JP6561598B2 - Rotation transmission device with torque measuring device - Google Patents

Description

  The present invention relates to an improvement in a rotation transmission device with a torque measuring device that is incorporated into, for example, an automatic transmission for an automobile, and transmits torque and is used to measure the magnitude of the transmitted torque.

  The rotational speed of the shaft that constitutes the automatic transmission for automobiles and the magnitude of torque transmitted by this shaft are measured, and the measurement results are used as information for performing shift control of the transmission or engine output control. It has been used conventionally. Conventionally, as an apparatus that can be used to measure the magnitude of torque, the amount of elastic torsional deformation of the shaft is converted into the phase difference between the output signals of a pair of sensors, and the torque is converted based on this phase difference. An apparatus for measuring the size is known (see, for example, Patent Documents 1 and 2). Such a conventional structure will be described with reference to FIG.

  In the case of the conventional structure shown in FIG. 6, a pair of encoders 2 and 2 are externally fitted and fixed at two positions in the axial direction of the torque transmission shaft 1 that transmits torque during operation. The magnetic characteristics of the detected surfaces, which are the outer peripheral surfaces of the encoders 2 and 2 that are the detected portions, change alternately and at equal pitches in the circumferential direction. Further, the pitches at which the magnetic characteristics of the two detection surfaces change in the circumferential direction are equal to each other on the two detection surfaces. The two sensors 3 and 3 are supported by a housing (not shown) in a state where the detection portions of the pair of sensors 3 and 3 are opposed to both the detection surfaces. These sensors 3 and 3 change their output signals in response to changes in the magnetic characteristics of the portions where their detection portions are opposed to each other.

  The output signals of the sensors 3 and 3 as described above periodically change as the encoders 2 and 2 rotate together with the torque transmission shaft 1. The frequency (and period) of this change takes a value commensurate with the rotational speed of the torque transmission shaft 1. For this reason, this rotational speed is calculated | required based on this frequency (or period). In addition, when the torque transmission shaft 1 is elastically twisted and deformed as the torque is transmitted by the torque transmission shaft 1, the encoders 2 and 2 are relatively displaced in the rotational direction. As a result, the phase difference ratio (= phase difference / 1 period) between the output signals of the sensors 3, 3 changes. The phase difference ratio takes a value commensurate with the torque (the elastic torsional deformation amount of the torque transmission shaft 1). Therefore, the torque can be obtained based on this phase difference ratio.

However, in the case of the rotation transmission device with the torque measuring device having the conventional structure as described above, the two sensors 3 and 3 need to be attached to the housing with a relative positional relationship with high accuracy in a state of being separated in the axial direction. There is. For this reason, the mounting work of both the sensors 3 and 3 becomes troublesome. Further, since two harnesses 4 and 4 are required in total, the wiring work of these harnesses 4 and 4 becomes troublesome (the handling property becomes worse), and the cost and the weight increase.
In order to increase the resolution of the torque measurement, it is preferable that the phase difference ratio between the output signals of the sensors 3 and 3 is large. For this reason, the torque transmission shaft 1 is elastically twisted. It is required to secure a large amount of relative displacement in the rotational direction between the encoders 2 and 2 based on the deformation amount.
As other prior art documents related to the present invention, there are inventions described in Patent Documents 3 to 5 in addition to Patent Documents 1 and 2 described above.

JP-A-1-254826 Japanese Unexamined Patent Publication No. 63-82330 Japanese Patent Application Laid-Open No. 60-213569 Japanese Patent Publication No. 7-18767 JP 2013-19828 A

  In view of the circumstances as described above, the present invention can improve the attachment workability of the sensor, simplify the wiring work of the harness, reduce the cost and weight, and further reduce the torque. The invention was invented to realize a structure capable of improving the resolution of measurement.

The rotation transmission device with a torque measuring device of the present invention includes a torque transmission shaft, an inner shaft, a first characteristic change member, a second characteristic change member, an amplification link member, and a sensor device.
Of these, the torque transmission shaft transmits torque during use.
The inner shaft is connected to the inner diameter side of the torque transmission shaft, and one end portion in the axial direction is directly or indirectly connected to the one end portion in the axial direction of the torque transmission shaft so as not to rotate relative to the torque transmission shaft. Is arranged in.
The first characteristic changing member is fixed directly or indirectly to the other axial end portion of the torque transmission shaft in a state where the central axis is coaxial with the central axis of the torque transmission shaft. Such a first characteristic changing member has a first detected part whose characteristics are alternately changed in the circumferential direction.
The second characteristic change member has a central axis at a center portion of the inner shaft at a portion of the other end portion in the axial direction of the inner shaft that protrudes from the other end side opening of the torque transmission shaft toward the other side in the axial direction. It is located coaxially with the shaft and is supported in a state allowing relative rotation with respect to the inner shaft. Such a second characteristic changing member has a second detected portion whose characteristics are alternately changed in the circumferential direction.
The amplification link member is provided between the inner shaft and the second characteristic change member in a state in which the rotation of the inner shaft can be transmitted to the second characteristic change member. The second characteristic change member is rotated at an angle equal to or greater than the torsion angle of the torque transmission shaft at the position where the inner shaft is connected.
The sensor device has a detection unit of the pair, the support to the one said first and respective detector of the pair, does not rotate even during use while being paired toward the second double-be-detected portions Has been. Such a sensor device can detect a phase change in the circumferential direction between portions of the first and second detected portions facing the pair of detection portions.

  In the case of implementing the torque transmission device-equipped rotation transmission device of the present example as described above, the amplification link member additionally has an engagement portion with the inner shaft as in the invention described in claim 2. Based on the displacement of the inner shaft input to the force point portion, the rocking is performed around the fulcrum portion that is the engaging portion with the first characteristic changing member or the member that rotates in synchronization with the first characteristic changing member. The second characteristic change member can be configured to rotate at an angle equal to or greater than the torsion angle of the inner shaft via an action point that is an engagement part with the second characteristic change member.

  When the rotation transmission device with a torque measuring device of the present example as described above is implemented, the distance between the action point portion and the force point portion is additionally set as in the invention described in claim 3. A configuration that is larger than the distance between the fulcrum part and the force point part can be adopted.

According to the rotation transmission device with a torque measuring device of the present invention configured as described above, the sensor mounting workability can be improved, and the wiring work of the harness can be simplified to reduce the cost and weight. .
That is, in the case of the present invention, the first and second characteristic change members used for detecting the magnitude of the torque transmitted by the torque transmission shaft are arranged on the other side in the axial direction of the torque transmission shaft. Adopted. For this reason, compared with the structure which arrange | positions said 2nd characteristic change member in the axial direction one end side of the said torque transmission shaft, the attachment workability | operativity of a sensor apparatus can be improved. In addition, since the first and second characteristic changing members can be arranged close to each other, the wiring work of the harness can be simplified and the cost and weight can be reduced.

Moreover, according to the rotation transmission device with a torque measuring device of the present invention, the resolution of torque measurement can be improved.
That is, in the case of the present invention, the second characteristic is obtained by amplifying the torsion angle (torsional deformation amount) of the torque transmission shaft at a position where the inner shaft is connected between the inner shaft and the second characteristic changing member. An amplification link member that can be transmitted to the change member is provided. For this reason, the amount of elastic torsional deformation of the torque transmission shaft transmitted from the inner shaft to the second characteristic changing member is made larger than that in the case of directly transmitting from the torque transmission shaft to the second characteristic changing member. Can do. As a result, the phase change (phase difference ratio) between the first and second characteristic change members detected by the sensor device is increased, and the resolution of torque measurement can be improved.

Sectional drawing of the rotation transmission apparatus with a torque measuring device which shows one example of embodiment of this invention. Similarly, it is the figure seen from the left side of Drawing 1 in the state where the 2nd encoder was omitted, and is the state (a) which is not transmitting torque, and the state (b) which is transmitting torque. Similarly, an exploded perspective view of a rotation transmission device with a torque measuring device, omitting the sensor device. Similarly, the exploded perspective view of the rotation transmission device with a torque measuring device in which the sensor device viewed from an angle different from that in FIG. 3 is omitted. Similarly, the top view which takes out and shows only an amplification link member. The schematic side view which shows an example of the rotation transmission apparatus with a torque measuring device of a conventional structure.

[Example of Embodiment]
An example of an embodiment of the present invention will be described with reference to FIGS. The rotation transmission device with torque measuring device 5 of this example is used by being incorporated in an automatic transmission for an automobile, for example. Such a rotation transmission device 5 with a torque measuring device includes a housing (mission case) (not shown) and a hollow (hollow cylindrical) torque transmission shaft 6 that functions as an input shaft (or countershaft) such as a belt type CVT. A pair of rolling bearings 7a and 7b, an input gear 8 , an output gear 9, an inner shaft 10, a first encoder 11, a second encoder 12, an amplification link member 13, and a sensor device 14 are provided. .

  The torque transmission shaft 6 is made in a hollow cylindrical shape by alloy steel such as carbon steel. Of the outer peripheral surface of the torque transmission shaft 6, the outer diameter dimension of the portion extending from the portion closer to one end in the axial direction (the right end in FIG. 1) to the one end edge in the axial direction is on the other axial side of the portion. One end side small diameter cylindrical portion 15 smaller than the outer diameter size of the adjacent portion is formed. In the present specification and claims as a whole, the axial direction, the radial direction, and the circumferential direction refer to directions of the torque transmission shaft unless otherwise specified.

  A locking groove 16 is formed over the entire circumference of the outer peripheral surface of the torque transmission shaft 6 adjacent to the other axial side of the one end side small diameter cylindrical portion 15. A male spline portion 17 serving as a torque input portion is formed on a portion of the outer peripheral surface of the torque transmission shaft 6 adjacent to the other axial side of the locking groove 16. Note that a female spline portion 28 of the input gear 8 to be described later is spline-engaged with the male spline portion 17 and is connected to the rotational shaft of the power source that is not coaxial with the torque transmission shaft 6. However, instead of the input gear 8, a power coupling such as a clutch, a cylindrical shaft coupling, a flange-type shaft coupling, a fluid coupling (including a torque converter) (not shown) is spline-engaged and is coaxial with the torque transmission shaft 6. It is also possible to adopt a configuration that connects to a rotating shaft of a power source such as an engine or motor arranged above.

  A positioning convex portion 18 is formed on the outer peripheral surface of the torque transmission shaft 6 adjacent to the other axial side of the male spline portion 17 so as to protrude radially outward over the entire circumference. Has been. In addition, the outer diameter of the outer peripheral surface of the torque transmission shaft 6 extends from the portion closer to the other end in the axial direction (the left end in FIG. 1) to the other end in the axial direction. A small-diameter cylindrical portion 19 on the other end side smaller than the outer diameter dimension of the portion adjacent to the side is formed. The inner peripheral surface of the torque transmission shaft 6 is formed in a cylindrical surface shape whose inner diameter does not change over the entire length. Such a torque transmission shaft 6 is rotatably supported by the rolling bearings 7a and 7b with respect to the housing. In the case of this example, the torque transmission shaft 6 is subjected to heat treatment such as quenching and tempering so that the surface hardness of the torque transmission shaft 6 is HV400 or more and the surface carbon concentration is 0.2%. That's it.

  One of the rolling bearings 7a and 7b (the right side in FIG. 1) is a tapered roller bearing, and includes an annular outer ring 20a and an inner ring 21a, a cage 22a, and a plurality of rolling elements. (Cone rollers) 23a, 23a. Of these, the outer ring 20a is fitted and fixed to the housing, and the inner ring 21a is fitted and fixed to the small-diameter cylindrical portion 15 at one end of the torque transmission shaft 6. The rolling elements 23a, 23a are held by the cage 22a between an outer ring raceway 24a formed on the inner peripheral surface of the outer ring 20a and an inner ring raceway 25a formed on the outer peripheral surface of the inner ring 21a. In such a state, it is provided to be able to roll freely.

On the other hand, of the two rolling bearings 7a and 7b, the other (left side in FIG. 1) rolling bearing 7b is a tapered roller bearing, and includes an annular outer ring 20b and an inner ring 21b, a cage 22b, and a plurality of rolling bearings. It is comprised from rolling elements (cone rollers) 23b, 23b. Of these, the outer ring 20 b is fitted and fixed to the housing, and the inner ring 21 b is fitted and fixed to the small diameter cylindrical portion 19 on the other end side of the torque transmission shaft 6. The rolling elements 23b, 23b are held by the cage 22b between an outer ring raceway 24b formed on the inner peripheral surface of the outer ring 20b and an inner ring raceway 25b formed on the outer peripheral surface of the inner ring 21b. In such a state, it is provided to be able to roll freely.
In addition to the tapered roller bearings as described above, for example, deep groove type and angular type ball bearings, cylindrical roller bearings, radial needle bearings, self-aligning roller bearings and the like are adopted as the double rolling bearings 7a and 7b. You can also do things.

  The input gear 8 is a helical gear or spur gear made of an alloy steel such as carbon steel, and includes a cylindrical portion 26 and an annular gear body 27. Of these, the cylindrical portion 26 has a female spline portion 28 formed on the inner peripheral surface thereof. The gear body 27 is formed on the outer peripheral surface of the cylindrical portion 26 so as to protrude radially outward from a portion extending from the axially intermediate portion to the other axial end edge. An input side tooth portion 29 is formed on the outer peripheral surface of the gear body 27. Such an input gear 8 is provided in a state where the female spline portion 28 of the cylindrical portion 26 is spline-engaged with the male spline portion 17 of the torque transmission shaft 6. In this state, one end surface in the axial direction of the cylindrical portion 26 is in contact with the other side surface in the axial direction of the retaining ring 30 locked in the locking groove 16 of the torque transmission shaft 6, and the cylindrical portion 26. The other end surface in the axial direction is in contact with one side surface in the axial direction of the positioning convex portion 18 of the torque transmission shaft 6. In this way, the input gear 8 is positioned in the axial direction with respect to the torque transmission shaft 6. As a structure for preventing relative rotation while achieving coaxiality between the input gear 8 and the torque transmission shaft 6, a fitting portion between the input gear 8 and the torque transmission shaft 6 is made coaxial. A cylindrical surface fitting portion for securing and an involute spline engaging portion for preventing relative rotation may be arranged adjacent to each other in the axial direction.

  The output gear 9 is a helical gear or a spur gear made of alloy steel such as raw steel, and is formed integrally with a portion closer to the other end in the axial direction in the axially intermediate portion of the outer peripheral surface of the torque transmission shaft 6. (Fixed). The output gear can be separately fitted from the torque transmission shaft and can be externally fitted (splined) to the outer peripheral surface of the intermediate portion in the axial direction of the torque transmission shaft. In this case, it is possible to adopt a configuration in which the fitting portion has a cylindrical surface fitting portion for ensuring concentricity and an involute spline engaging portion for preventing relative rotation arranged adjacent to each other in the axial direction. .

The inner shaft 10 is made in a substantially cylindrical shape (or a circular tube shape) from an alloy steel such as carbon steel or a synthetic resin. Such an inner shaft 10 has an outer diameter dimension of a portion (axial intermediate portion) adjacent to the other side in the axial direction of the portion extending from one axial end portion to one axial end edge. A fitting surface portion 31 larger than the size is formed. In addition, the outer diameter of the inner shaft 10 near the other end in the axial direction is larger than the portion adjacent to one side in the axial direction of the portion (the intermediate portion in the axial direction). A guide surface portion 32 slightly smaller than the size is formed. Further, of the outer peripheral surface of the inner shaft 10, a portion adjacent to the other axial side of the guide surface portion 32, and a portion protruding from the other axial end opening of the torque transmission shaft 6 to the other axial side. A ring-shaped inner shaft side flange portion 33 provided as a separate body is externally fitted and fixed. The outer diameter dimension of the inner shaft side flange portion 33 is larger than the inner diameter size of the torque transmission shaft 6 and smaller than the outer diameter size of the other end side small diameter cylindrical portion 19 of the torque transmission shaft 6. Further, at one position in the circumferential direction near the radially outer end of the other axial side surface of the inner shaft side flange portion 33, a cylindrical force point convex portion 34 protrudes to the other side in the axial direction. Is formed.
A stepped shaft portion 35 is formed at the other axial end portion of the inner shaft 10 (a portion adjacent to the other axial direction side of the inner shaft side flange portion 33). Specifically, the stepped shaft portion 35 includes a medium-diameter shaft portion 36 provided in one half of the axial direction, a small-diameter shaft portion 37 provided in the other half of the axial direction, and the medium-diameter shaft. The portion 36 and the small diameter shaft portion 37 are composed of a stepped portion 38 that is continuous. A locking groove 39 is formed on the outer circumferential surface of the intermediate portion in the axial direction of the small-diameter shaft portion 37 over the entire circumference.

The inner shaft 10 having such a configuration is disposed coaxially with the torque transmission shaft 6 on the inner diameter side of the torque transmission shaft 6. In this state, the fitting surface portion 31 of the inner shaft 10 is internally fitted and fixed to the inner peripheral surface of one axial end portion of the torque transmission shaft 6 by press fitting. In this way, the inner shaft 10 and the torque transmission shaft 6 are connected in a state in which they can rotate together (a state in which relative rotation is impossible). Further, the guide surface portion 32 of the inner shaft 10 is in close proximity to the inner peripheral surface of the other axial end portion of the torque transmission shaft 6. For this reason, it is possible to improve the torque detection accuracy by suppressing the vibration (vibration) of the inner shaft 10 during torque transmission. Further, in the state of being arranged as described above, one axial side surface of the inner shaft side flange portion 33 of the inner shaft 10 is in close proximity to the other axial end surface of the torque transmission shaft 6. Therefore, in the inner shaft 10, the other axial side portion (the inner shaft side flange portion 33 and the stepped shaft portion 35) than the guide surface portion 32 extends axially from the other axial opening of the torque transmission shaft 6. Projects to the other side.

  In the case of the structure of this example, in order to connect the inner shaft 10 and the torque transmission shaft 6 so as not to be relatively rotatable, the fitting surface portion 31 (one axial end portion) of the inner shaft 10 The torque transmission shaft 6 is fitted and fixed to the inner peripheral surface of one axial end portion by an interference fit. In addition to such a structure, as a structure for connecting the inner shaft 10 and the torque transmission shaft 6 so as not to be relatively rotatable, a structure in which, for example, an involute spline or a key is engaged may be employed. In the case of the illustrated structure, the fitting surface portion 31 (one axial end portion) of the inner shaft 10 and the inner circumferential surface of the one axial end portion of the torque transmission shaft 6 are fitted and fixed by an interference fit. For reasons of the assembly process, a configuration is adopted in which the inner shaft side flange portion 33 provided separately is fitted and fixed to the inner shaft 10. However, in the case where, for example, a structure in which the inner shaft 10 and the torque transmission shaft 6 are connected to each other so as not to rotate relative to each other is employed by, for example, an involute spline or a key, the inner shaft and the inner shaft 10 are connected. It is also possible to adopt a configuration in which the shaft side flange portion is formed integrally.

  The first encoder 11 includes a first fitting cylinder portion 40 and a first encoder body 41. Of these, the first encoder body 41 has an annular shape, and is provided in a state in which the radially inner end portion on one side surface in the axial direction is continuous with the other side surface in the axial direction of the first fitting tube portion 40. A first detected portion 42 is formed on the outer peripheral surface of such a first encoder body 41. In the first detected portion 42, the S poles and the N poles are alternately arranged at equal pitches in the circumferential direction, and the magnetic characteristics are alternately changed at equal pitches in the circumferential direction. In addition, a cylindrical fulcrum convex portion 43 is formed at one position in the circumferential direction of the radially inner end of the other side surface of the first encoder body 41 in a state of protruding to the other side in the axial direction. ing.

  The first encoder 11 having the above-described configuration configures the other rolling bearing 7b of the inner peripheral surface of the first fitting tube portion 40 in the other end side small diameter cylindrical portion 19 of the torque transmission shaft 6. The inner ring 21b to be rotated is fitted and fixed to the other side in the axial direction from the portion to which the inner ring 21b is fitted and fixed so that the inner ring 21b can rotate in synchronization with the torque transmission shaft 6. In this fixed state, the central axis of the first detected portion 42 of the first encoder 11 is coaxial with the central axes of the torque transmission shaft 6 and the inner shaft 10. In addition, the structure which attaches a 1st encoder via a support ring etc. can also be employ | adopted as well as the structure directly fixed with respect to an inner ring | wheel with a fitting cylinder part.

The second encoder 12 includes an annular portion 44 and a second encoder body 45.
Among these, the inner diameter dimension of the annular ring portion 44 is slightly larger than the outer diameter dimension of the small diameter shaft portion 37 of the torque transmission shaft 6. In addition, a cylindrical working point convex portion 46 is formed at one position in the circumferential direction near the radially outer end of one side surface in the axial direction of the annular portion 44 in a state of protruding to one side in the axial direction. ing.
The second encoder body 45 has a cylindrical shape, and is provided in a state in which the inner peripheral surface of the other end portion in the axial direction is continuous with the radially outer end edge of the annular portion 44. A second detected portion 47 is formed on the outer peripheral surface of the second encoder body 45. In the second detected portion 47, the S poles and the N poles are alternately arranged at equal pitches in the circumferential direction, and the magnetic characteristics are alternately changed at equal pitches in the circumferential direction. The pitch and the outer diameter of the change in the magnetic characteristics of the second detected portion 47 are the same as those of the first detected portion 42 of the first encoder 11.

In the second encoder 12 having the above-described configuration, the inner peripheral surface of the annular portion 44 is in a state in which the outer peripheral surface of the small-diameter shaft portion 37 of the inner shaft 10 can rotate relative to the inner shaft 10. It is loosely fitted. In this state, the central axis of the second detected portion 47 of the second encoder 12 is coaxial with the central axes of the torque transmission shaft 6 and the inner shaft 10. A radially inner end of one side surface in the axial direction of the annular portion 44 is in contact with a step portion 38 constituting the stepped shaft portion 35 of the inner shaft 10, and the axial direction of the annular portion 44 is The radially inner end portion of the other side surface is in contact with one axial side surface of a retaining ring 48 that is locked in a locking groove 39 formed in the small-diameter shaft portion 37. In this way, the second encoder 12 is positioned in the axial direction with respect to the inner shaft 10.
Further, in the assembled state as described above, the first detected portion 42 of the first encoder 11 and the second detected portion 47 of the second encoder 12 are close to each other in an axially adjacent state ( For example, they are arranged in the axial direction within 10 mm, preferably within 5 mm.

The amplification link member 13 is made, for example, by punching a metal plate, and includes an annular portion 49, a first projecting piece 50, and a second projecting piece 51.
Of these, the annular portion 49 has an inner diameter larger than the outer diameter of the medium-diameter shaft portion 36 constituting the stepped shaft portion 35 of the inner shaft 10. As will be described later, the inner diameter of the annular portion 49 is such that when the amplification link member 13 is swung, the inner peripheral surface of the annular portion 49 and the outer peripheral surface of the medium-diameter shaft portion 36 are as follows. Is restricted to a size that does not interfere.

The first projecting piece 50 is formed in a state of projecting radially outward from one circumferential position on the outer circumferential surface of the annular portion 49. A fulcrum through hole 52 that is a circular hole is formed in a portion near the radially outer end of the first projecting piece 50 in such a manner that the first projecting piece 50 penetrates in the axial direction. The inner diameter dimension of the fulcrum through hole 52 is slightly larger than the outer diameter dimension of the fulcrum convex portion 43 of the first encoder 11.
Further, a state in which the first projecting piece 50 and the annular portion 49 are penetrated in the axial direction in a portion extending from the radially intermediate portion of the first projecting piece 50 to the radially outer end portion of the annular portion 49. A long hole 53 for a power point that is long in the radial direction is formed.

The second projecting piece 51 is formed on the outer peripheral surface of the annular ring portion 49 so as to project radially outward from a portion opposite to the first projecting piece 50 in the radial direction. At the radially outer end of the second projecting piece 51, both axial end portions and radially outer end portions are opened, and the shape viewed from the axial direction is for a substantially semi-elliptical working point. A notch 54 is formed. In addition, this notch 54 for action points can also be formed in a long hole, for example.
In the case of this example, as shown in FIG. 5, the center O ₅₂ of the fulcrum through hole 52, the center O 53 of the force application slot _53, and the center O ₅₄ of the working point notch ₅₄ (circle) (Center position in the circumferential direction) is located on the same straight line X passing through the center of the annular portion 49. Further, on the straight line X, the distance _{L 1} between the center _{O 53} of the center _{O 54} and the force point long hole 53 of the action point notch 54, the force point and the center _{O 52} of the fulcrum hole 52 It is set to be about 7 times the distance L ₂ between the center O ₅₃ of use long hole 53. The ratio of the distance L ₁ and the distance L ₂ may be appropriately determined.

  The amplification link member 13 having the above-described configuration is configured so that the annular portion 49 is loosely inserted through the medium-diameter shaft portion 36 constituting the stepped shaft portion 35 of the inner shaft 10 with respect to the axial direction. It is arranged between the first encoder 11 and the second encoder 12. Further, the fulcrum convex portion 43 of the first encoder 11 is inserted (engaged) without being rattled inside the fulcrum through hole 52 of the amplification link member 13. In this state, the amplification link member 13 can swing (rotate) with respect to the first encoder 11 around the fulcrum through hole 52 (fulcrum convex portion 43). The engaging portion between the fulcrum through hole 52 of the amplification link member 13 and the fulcrum convex portion 43 of the first encoder 11 corresponds to the fulcrum described in the claims.

  Further, a force point convex portion 34 of the inner shaft 10 is inserted (engaged) inside the force point long hole 53 of the amplification link member 13 so as to be displaceable in the long axis direction of the force point long hole 53. ing). In this state, the rotation of the inner shaft 10 can be transmitted to the amplification link member 13. In addition, the engaging part of the long hole 53 for power points of the said amplification link member 13 and the convex part 34 for power points of the said inner shaft 10 is equivalent to the power point part described in the claim.

  Further, the working point projection 46 of the second encoder 12 is inserted (engaged) inside the working point notch 54 of the amplification link member 13. In this state, the swing (rotation) of the amplification link member 13 can be transmitted to the second encoder 12. The engaging portion between the action point notch 54 of the amplification link member 13 and the action point convex portion 46 of the second encoder 12 corresponds to the action point portion described in the claims.

  The sensor device 14 includes a holder 55 made of synthetic resin, first and second sensors 56 and 57 embedded (held) in a state adjacent to the tip of the holder 55 in the axial direction, and one sensor device 14. The harness 58 is provided. The detection units (first detection unit and second detection unit) of each of the first and second sensors 56 and 57 include a Hall element, a Hall IC, and an MR element (including a GMR element, a TMR element, and an AMR element). In the state where the holder 55 is supported and fixed to the outer ring 20b constituting the other rolling bearing 7b, the first detection unit of the first sensor 56 is connected to the first encoder 11. The second detection part of the second sensor 57 is made to face the second detection part 47 of the second encoder 12 in close proximity to the first detection part 42. For this reason, the first sensor 56 changes the output signal in response to a change in the magnetic characteristic of the first detected portion 42, and the second sensor 57 is a magnetic characteristic of the second detected portion 47. The output signal is changed in response to the change. In the case of this example, the output signals of the first and second sensors 56 and 57 are transmitted through the harness 58 to a calculator (not shown).

  In the case of the rotation transmission device 5 with the torque measuring device having the above-described configuration, the output signals of both the first and second sensors 56 and 57 constituting the sensor device 14 are output together with the torque transmission shaft 6. As both the first and second encoders 11 and 12 rotate, they change periodically. In the case of this example, the first encoder 11 rotates when the rotation of the torque transmission shaft 6 is directly transmitted. On the other hand, the second encoder 12 rotates when the rotation of the torque transmission shaft 6 is transmitted through the inner shaft 10 and the amplification link member 13. Here, the change frequency (and period) of the output signal takes a value corresponding to the rotational speed of the torque transmission shaft 6. Therefore, if the relationship between these frequencies (or periods) and the rotational speed is examined in advance, the rotational speed can be obtained based on the frequencies (or periods).

In particular, according to the rotation transmission device 5 with the torque measuring device of the present example, the work of attaching the sensor can be improved, the wiring work of the harness can be simplified, and the cost and weight can be reduced.
That is, in the case of this example, the phase of one end portion in the axial direction of the torque transmission shaft 6 is arranged on the inner diameter side of the torque transmission shaft 6, and the other end portion in the axial direction is the axial direction of the torque transmission shaft 6. Transmission to the inner shaft 10 protruding from the other end opening is possible. Therefore, the first encoder 11 for detecting the phase of the other end in the axial direction of the torque transmission shaft 6, and the second encoder 12 for detecting the phase of the one end of the torque transmission shaft 6 in the axial direction, Can be disposed adjacent to the other end portion in the axial direction of the torque transmission shaft 6 (collectively disposed). Therefore, in the case of this example, since one sensor device 14 holding both the first and second sensors 56 and 57 in the holder 55 can be used, the sensor mounting workability can be improved. Specifically, the first and second sensors 56 and 57 can be positioned with high accuracy by performing the operation of attaching the holder 55 to the outer ring 20b constituting the rolling bearing 7b only once. Further, since the number of harnesses can be reduced from two to one, the wiring work of the harness can be simplified (the handling property can be improved), and the cost and weight can be reduced.

  Further, when torque is transmitted by the torque transmission shaft 6, both ends of the torque transmission shaft 6 in the axial direction are elastically torsionally deformed between the input gear 8 and the output gear 9. The two (first and second encoders 11, 12) are relatively displaced in the rotational direction. As a result of the relative displacement of the first and second encoders 11 and 12 in the rotational direction in this way, the phase difference ratio between the output signals of the first and second sensors 56 and 57 (= phase difference). / 1 period) changes. Here, this phase difference ratio takes a value commensurate with the torque. Therefore, if the relationship between the phase difference ratio and the torque is examined in advance, the torque can be obtained based on the phase difference ratio.

Furthermore, according to the rotation transmission device 5 with the torque measuring device of this example, it is possible to improve the resolution of the torque measurement as described above.
That is, in this example, when the torque transmission shaft 6 is torsionally deformed, the relative displacement amount in the rotational direction of the second encoder 12 with respect to the first encoder 11 based on the torsional deformation is calculated as the amplification link member 13. Can be amplified using Specifically, when the torque transmission shaft 6 is torsionally deformed, the torsional deformation is transmitted to the amplification link member 13 from the force point portion of the force point convex portion 34 of the inner shaft 10 and the force point long hole 53. The Then, as shown in FIG. 2B, the amplification link member 13 is an engaging portion between the fulcrum through hole 52 and the fulcrum convex portion 43 of the first encoder 11 in the direction of the torsional deformation. Swing around the fulcrum. Then, the second encoder 12 is rotated in the twisting direction through an action point portion that is an engagement portion between the action point notch 54 and the action point projection 46. Here, in the case of a structure in which the amplification link member 13 is not provided, the displacement amount in the rotational direction of the force point convex portion 34 of the inner shaft 10 is transmitted to the second encoder 12. On the other hand, in the case of the structure in which the amplification link member 13 is provided as in the present example, the center O of the action point notch 54 with respect to the displacement amount of the force point convex portion 34 of the inner shaft 10 in the rotational direction. ₅₄ and the distance _{L 1} between the center _{O 53} of the force point long hole 53, the ratio between the distance _{L 2} between the center _{O 52} before Ki支 point for hole 52 and the center _{O 53} of the force point long hole 53 A displacement amount in the rotational direction amplified by (L ₁ / L ₂ ) (in this example, amplified by about 7 times) is transmitted to the second encoder 12. Based on the amount of displacement in the rotational direction thus amplified, the second encoder 12 has a torsion angle amplified by the ratio (L ₁ / L ₂ ) rather than the torsion angle of the inner shaft 10. Rotate. Therefore, in this example, even when the torque transmitted by the torque transmission shaft 6 is small, a large amount of relative displacement in the rotational direction of the encoders 11 and 12 based on the elastic torsional deformation amount of the torque transmission shaft 6 is ensured. I can do it. As a result, it is possible to improve the resolution of torque measurement.

The torque transmission shaft that constitutes the rotation transmission device with the torque measuring device of the present invention is not limited to the rotation shaft that constitutes the power train of the automobile, but, for example, the rotation shaft of the windmill (main shaft, rotation shaft of the speed increasing device), rolling mill Roll neck, rolling shaft of rolling stock (axle, rotating shaft of speed reducer), rotating shaft of machine tool (main shaft, rotating shaft of feed system), construction machinery / agricultural machinery / home appliance / motor rotating shaft, etc. The rotation shafts of various mechanical devices can be targeted. Further, when configuring a power train of an automobile, for example, an input shaft (turbine shaft) to which torque is input from a torque converter or a countershaft can be targeted. Further, the form of the transmission in the case of constituting the transmission by incorporating the rotation transmission device with the torque measuring device of the present invention is not particularly limited, and various continuously variable transmissions such as an automatic transmission (AT), a belt type and a toroidal type. It is possible to adopt a transmission that changes gears under the control of the vehicle, such as a machine (CVT), an automated manual transmission (AMT), a dual clutch transmission (DCT), and a transfer. The relationship between the installation position of the transmission and the drive wheels is not particularly limited, and there are front engine front wheel drive vehicles (FF vehicles), front engine rear wheel drive vehicles (FR vehicles), four wheel drive vehicles, and the like. It becomes a target. Further, the measured rotational speed and torque may be used for vehicle control other than shift control and engine output control. Further, the power source placed on the upstream side of the transmission does not necessarily need to be an internal combustion engine such as a gasoline engine or a diesel engine, and may be an electric motor used for a hybrid vehicle or an electric vehicle, for example. Further, when implementing the present invention, it is essential to measure the torque, but it is not essential to measure the rotational speed. Even if rotation speed is required, it can be measured by a separate simple structure.
Moreover, when implementing this invention, the structure of an amplification link member is not limited to the structure of one example of embodiment mentioned above.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Encoder 3 Sensor 4 Harness 5 Rotation transmitting device with torque measuring device 6 Torque transmitting shaft 7a, 7b Rolling bearing 8 Input gear 9 Output gear 10 Inner shaft 11 First encoder 12 Second encoder 13 Amplifying link member 14 Sensor device DESCRIPTION OF SYMBOLS 15 One end side small diameter cylindrical part 16 Locking groove 17 Male spline part 18 Positioning convex part 19 Other end side small diameter cylindrical part 20a, 20b Outer ring 21a, 21b Inner ring 22a, 22b Cage 23a, 23b Rolling element 24a, 24b Outer ring track 25a 25b Inner ring raceway 26 Tubular part 27 Gear body 28 Female spline part 29 Input side tooth part 30 Retaining ring 31 Fitting surface part 32 Guide surface part 33 Inner shaft side flange part 34 Force point convex part 35 Stepped shaft part 36 Medium diameter shaft part 37 Small-diameter shaft portion 38 Step portion 39 Locking groove 40 First fitting tube portion 41 First encoder Main body 42 first detected portion 43 fulcrum convex portion 44 annular portion 45 second encoder main body 46 acting point convex portion 47 second detected portion 48 retaining ring 49 annular portion 50 first projecting piece 51 second projection 53 fulcrum hole 53 force point slot 54 working point notch 55 holder 56 first sensor 57 second sensor 58 harness

Claims (3)

A torque transmission shaft that is hollow and transmits torque during use;
An inner end of the torque transmission shaft is disposed with one axial end portion thereof directly or indirectly coupled to the torque transmission shaft so as not to rotate relative to the torque transmission shaft. The axis,
The other end in the axial direction of the torque transmission shaft is directly or indirectly fixed with the central axis coaxially positioned with the central axis of the torque transmission shaft, and the characteristics change alternately in the circumferential direction. A first characteristic changing member having a first detected part,
The central axis is located coaxially with the central axis of the inner shaft at a portion protruding from the other end side opening of the torque transmission shaft to the other axial side of the axially other end portion of the inner shaft. A second characteristic changing member having a second detected part that is supported in a state capable of relative rotation with respect to the inner shaft and whose characteristics are alternately changed in the circumferential direction;
The rotation of the inner shaft is provided between the inner shaft and the second characteristic changing member in a state where the rotation of the inner shaft can be transmitted to the second characteristic changing member. An amplification link member capable of rotating the change member at an angle equal to or greater than the torsion angle of the torque transmission shaft at a position where the inner shaft is coupled;
Has a detection unit of the pair, said pair of detecting portions of the respective first, is supported in a portion which does not rotate even during use while being paired toward the second double-detected portions, these first, A rotation transmission device with a torque measuring device , comprising: a sensor device capable of detecting a phase change in a circumferential direction between portions of the two detected portions facing the pair of detection portions.   The amplification link member is a member that rotates in synchronization with the first characteristic changing member or the first characteristic changing member based on the displacement of the inner shaft that is input to a force point portion that is an engaging portion with the inner shaft. The second characteristic change member is swung around the fulcrum part that is an engagement part with the second characteristic change member via the action point part that is the engagement part with the second characteristic change member. The rotation transmission device with a torque measuring device according to claim 1, wherein the rotation transmission device is rotated at the above angle.   The rotation transmission device with a torque measuring device according to claim 2, wherein a distance between the action point portion and the force point portion is larger than a distance between the fulcrum portion and the force point portion.

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