JP6554938B2 - 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 for a long time. 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. 20, a pair of encoders 2 and 2 are 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 both encoders 2 and 2, 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. In the case of the structure shown in the figure, the output signals of the sensors 3 and 3 are transmitted to the computing unit (not shown) through the harnesses 4 and 4, respectively, and the computing unit determines the rotational speed of the torque transmission shaft 1 and the torque to be transmitted. Calculated.

  By the way, for example, Patent Document 3 relates to a structure for detecting the rotational speed of a shaft, and among the rolling bearings for rotatably supporting the shaft, there is a structure for supporting the sensor on the outer ring and supporting the encoder on the inner ring. It is disclosed. According to such a structure, since the encoder can be fixed to the inner ring that is smaller than the shaft, the mounting work of the encoder can be improved, and a mounting hole for fixing the sensor to the housing is formed. Since there is no need, the mounting workability of the sensor can be improved.

However, when the support structure related to the encoder and sensor described in Patent Document 3 as described above is applied to the torque detection structure shown in FIG. 20, the following problem may occur.
For example, with respect to the structure shown in FIG. 20, a structure in which both end portions in the axial direction of the torque transmission shaft 1 are rotatably supported with respect to the housing by respective rolling bearings is adopted, and the inner rings constituting the respective rolling bearings are respectively employed. It is assumed that the encoders 2 and 2 are supported and the sensors 3 and 3 are supported on the outer rings constituting the respective rolling bearings. In such a case, if any one of the inner rings and the torque transmission shaft 1 to which the inner ring is fitted and fixed are relatively rotated, even though the torque transmission shaft 1 is not twisted, both A phase difference is produced between the output signals of the sensors 3 and 3. In addition, even when any one of the outer rings and the housing in which the outer ring is fitted and fixed are relatively rotated, the two sensors 3, although the torque transmission shaft 1 is not twisted. 3 produces a phase difference between the three output signals. As described above, when relative rotation (creep) occurs in the portion between the inner ring and the torque transmission shaft 1 or in the portion between the outer ring and the housing, there arises a problem that the measurement accuracy of the torque is lowered. .
As other prior art related to the present invention, there are inventions described in Patent Documents 4 to 6 in addition to Patent Documents 1 to 3 described above.

JP-A-1-254826 Japanese Unexamined Patent Publication No. 63-82330 Special table 2012-529646 gazette 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 was invented to realize a structure of a rotation transmission device with a torque measuring device that can improve assembly workability and can improve torque measurement accuracy.

  Each of the rotation transmission devices with a torque measuring device according to the present invention includes a torque transmission shaft, one or more rolling bearings, a pair of encoders, and a pair of sensors.

In the case of the invention described in claim 1, the following configuration is provided.
The torque transmission shaft transmits torque during use.
The rolling bearing includes an outer ring, an inner ring, and a plurality of rolling elements, and rotatably supports the torque transmission shaft with respect to a portion that does not rotate during use (for example, a housing or a transmission case). It is.
Both the encoders alternately change the characteristics of the respective detection surfaces in the circumferential direction, and are supported by a member that rotates directly on the torque transmission shaft or in synchronization with the torque transmission shaft when in use.
The two sensors are supported by a portion that does not rotate even when used (for example, an outer ring that constitutes a rolling bearing or a housing that supports the outer ring, etc.) in a state where the respective detection portions are opposed to the detection surfaces of the encoders. ing.
The torque transmitted by the torque transmission shaft during use can be measured using output signals of the two sensors (for example, phase difference between the output signals, phase difference ratio).
In the case of the invention described in claim 1 , the inner ring and the torque transmission shaft are relatively rotated between the inner ring, which is a rotating wheel constituting the rolling bearing, and the torque transmission shaft to which the inner ring is fitted and fixed. An internal detent mechanism is provided to prevent this from happening.
Further, at least one of the encoders is fitted and fixed to a portion of the inner peripheral surface of the inner ring that is axially disengaged from the inner detent mechanism.

On the other hand, the invention described in claim 2 has the following configuration.
The torque transmission shaft transmits torque during use.
The rolling bearing includes an outer ring, an inner ring, and a plurality of rolling elements, and rotatably supports the torque transmission shaft with respect to a portion that does not rotate during use (for example, a housing or a transmission case). It is.
The two encoders alternately change the characteristics of the respective detection surfaces in the circumferential direction, and directly or another member (for example, a rolling bearing) is formed at two positions separated in the axial direction of the torque transmission shaft. Indirectly supported via an inner ring or the like).
The two sensors are supported by a portion that does not rotate during use, with each detection unit facing the detection surface of each encoder.
The torque transmitted by the torque transmission shaft during use can be measured using output signals of the two sensors (for example, phase difference between the output signals, phase difference ratio).
In the case of the invention described in claim 2, prior between Kigairin and fixed the rotating parts not fitted in the outer ring, for preventing that the part which does not rotate with the outer ring are relatively rotated, An outer detent mechanism comprising a key groove and a key press-fitted into the key groove is provided.
Further, at least one of the two sensors is supported by the outer ring and is disposed adjacent to the outer ring, and the detection portion thereof is an inner ring that is a rotating wheel constituting the rolling bearing. It is fitted and fixed to the peripheral surface, and is opposed to the detected surface of the encoder disposed adjacent to the inner ring.

Moreover, when implementing the rotation transmission device with a torque measuring device of the present invention, for example, the invention described in claim 1 and the invention described in claim 2 can be simultaneously performed.
Further, when performing the rotation transmission device with a torque measuring device of the present invention, for example, as a said inner detent Organization, for example key engagement, fitting engagement (non-circular non-circular each having a flat surface portion ), Bolting structure, serration engagement, spline engagement, etc. can be adopted.

Further, when the present invention described in claim 1 is carried out, for example, the encoder and the sensor are combined on one end side (or the other end side in the axial direction) of the torque transmission shaft ( (Adjacent).
In order to employ such a configuration, for example, the torque transmission shaft is hollow, and an inner shaft is disposed on the inner diameter side of the torque transmission shaft. And the axial direction one end side part of this inner shaft is connected to the axial direction one end side part of this torque transmission shaft directly or indirectly (through another member) so as not to be relatively rotatable.
In addition, of the two encoders, one encoder is supported and fixed to an inner ring constituting a rolling bearing that rotatably supports the other axial end of the torque transmission shaft, and the other encoder is connected to the shaft of the inner shaft. The other end portion in the direction (the portion protruding from the other end portion in the axial direction of the torque transmission shaft) is supported and fixed in a state adjacent to the one encoder.
Further, as described above, when the configuration in which the inner shaft is disposed on the inner diameter side of the torque transmission shaft is adopted, the inner shaft is formed into a hollow shape (hollow cylindrical shape, hollow tubular shape). In addition, the inner space of the inner shaft can be used as a flow path for supplying lubricating oil to each part.
Further, it is possible to adopt a configuration in which the outer peripheral surface in the axial direction of the inner shaft is guided and supported by the inner peripheral surface of the torque transmission shaft. In this case, a surface treatment for preventing wear can be applied to the outer circumferential surface in the axial direction of the inner shaft (the surface guided by the inner circumferential surface of the torque transmission shaft).

Alternatively, when carrying out the present invention described in claim 1, for example, the two encoders and the two sensors are respectively positioned at two positions (for example, both end portions) separated from each other in the axial direction of the torque transmission shaft. Can be placed.
When such a configuration is adopted, at least one of the encoders (preferably both encoders) is supported by an inner ring constituting a rolling bearing for rotatably supporting the torque transmission shaft. Fix it.

  When the invention described in claim 1 is carried out, a rolling bearing for rotatably supporting the torque transmission shaft is provided for at least one of the two sensors (preferably both sensors). It can be supported and fixed to the outer ring.

In contrast, when carrying out the invention described in claim 2, a good Mashiku both encoder, supporting and fixing the inner ring constituting the rolling bearing for rotatably supporting the torque transmitting shaft I can do things.

Also, as in the present invention, an encoder that supports fixed to the inner ring, the case you inner fitting fixed (press-fitted) to the inner peripheral surface of the inner ring, furthermore, the axial end portion of the inner ring, the shaft An attachment stepped portion having an inner diameter dimension larger than that of the portion other than the direction end portion can be formed. And the part by which the thickness dimension of the radial direction became small compared with the depth dimension of the radial direction of this attachment step part among the said encoder to this attachment step part can be internally fitted and fixed.

  Further, when the present invention is carried out, for example, the encoder is made of a permanent magnet, and a portion magnetized to the S pole and a portion magnetized to the N pole on the detected surface of the encoder in the circumferential direction. In addition to adopting a configuration in which the magnetic characteristics are alternately arranged (alternatingly changing the magnetic characteristics in the circumferential direction at an equal pitch), the encoder is made of a simple magnetic metal, and a through-hole (or recess) and a column are formed on the detection surface of the encoder A configuration in which the portions (or convex portions) are alternately provided in the circumferential direction can be employed. Also, if the encoder is made of magnetic metal and has a structure in which a through hole (or recess) and a column (or protrusion) are provided on the surface to be detected, a permanent magnet is installed on the sensor side combined with such an encoder. Include.

  Furthermore, when implementing the rotation transmission device with a torque measuring device of the present invention, for example, the surface hardness of the torque transmission shaft may be HV400 or more and the surface carbon concentration may be 0.2% or more. it can.

Further, when implementing the present invention, the position (formation position, installation position) of the input part for inputting torque to the torque transmission shaft is not particularly limited, and for example, it can be provided at one end part in the axial direction, It can also be provided in the axially intermediate portion or the other axial end portion. As the input portion, for example, a spline portion (male spline portion or female spline portion), a key engagement portion, a fitting surface portion, and a screw portion are directly formed on the outer peripheral surface or inner peripheral surface of the torque transmission shaft. In addition, a configuration in which an input gear, an input pulley, an input sprocket, and the like are provided integrally with the torque transmission shaft or coupled and fixed separately can be employed.
Similarly, the position (formation position, installation position) of the output part for outputting torque from the torque transmission shaft is not particularly limited, and can be provided at one end part in the axial direction, Or it can also provide in an axial direction other end part. As the output portion, for example, a spline portion (male spline portion or female spline portion), a key engagement portion, a fitting surface portion, and a screw portion are directly formed on the outer peripheral surface or inner peripheral surface of the torque transmission shaft. In addition, a configuration in which an output gear, an output pulley, an output sprocket, and the like are provided integrally with the torque transmission shaft or coupled and fixed separately can be employed. The torque transmission shaft may be provided with a plurality of output portions. In this case, for example, a plurality of output gears having different numbers of teeth may be provided, or different types of output portions (for example, an output pulley and an output). Gears, etc.) can be provided.

When the present invention is carried out, the torque transmission shaft can be freely rotated by using one or more bearings (including at least one rolling bearing) with respect to a portion that does not rotate even when a housing or the like is used. To support. As bearings used in this case, for example, deep groove type and angular type ball bearings, tapered roller bearings, cylindrical roller bearings, radial needle bearings, self-aligning roller bearings, sliding bearings and the like can be used. When a plurality of bearings are used, for example, a portion between the torque input portion and the output portion of the intermediate portion in the axial direction of the torque transmission shaft can be rotatably supported.
When the present invention is carried out, for example, the rotation shaft of a power source that inputs torque to the torque transmission shaft can be arranged coaxially, parallel, or at a right angle to the torque transmission shaft.
In addition, in this specification, the axial direction one end side of a shaft means a portion (including one end portion) that is closer to one end in the axial direction than the center portion of the shaft. Means a portion (including the other end portion) present on the side closer to the other end in the axial direction than the central portion of the shaft.

According to the rotation transmission device with a torque measuring device of the present invention configured as described above, the assembly workability can be improved and the torque measurement accuracy can be improved.
That is, in the case of the invention described in claim 1 of the present invention, at least one encoder of the pair of encoders is supported by the inner ring constituting the rolling bearing, and the invention described in claim 2 In this case, at least one of the pair of sensors is supported by the outer ring constituting the rolling bearing. For this reason, according to the first aspect of the invention, it is possible to improve the mounting workability of the encoder, and according to the second aspect, the mounting workability of the sensor can be improved. Therefore, in any case, it is possible to improve the assembly workability of the rotation transmission device with a torque measuring device.
In the invention described in claim 1 of the present invention, an inner detent mechanism is provided between the inner ring supporting the encoder and the torque transmission shaft to which the inner ring is fitted and fixed. In the second aspect of the invention, an outer detent mechanism is provided between the outer ring that supports the sensor and the portion that does not rotate when the outer ring is fitted and fixed. Therefore, according to the invention described in claim 1, it is possible to prevent the inner ring supporting the encoder and the torque transmission shaft from rotating relative to each other. According to the invention described in claim 2, the Relative rotation between the outer ring supporting the sensor and the non-rotating portion can be prevented. Therefore, in any case, it is possible to prevent a phase difference from occurring between the output signals of the pair of sensors based on the relative rotation. As a result, according to the present invention, torque measurement accuracy can be improved.

Sectional drawing of the rotation transmission apparatus with a torque measuring device which shows the 1st example of embodiment of this invention. The A section enlarged view of FIG. 1 similarly. The schematic diagram corresponding to the BB cross section of FIG. The disassembled perspective view of the member similarly shown in FIG. The perspective view which shows the sensor of the state before similarly bend | folding in a substantially U shape. The C section enlarged view of FIG. 2 similarly. The figure equivalent to the upper half part of FIG. 2 which shows the other example (reference example) of the attachment aspect of a 1st encoder similarly. The figure equivalent to FIG. 3 which shows the 2nd example of embodiment of this invention. The figure corresponding to FIG. 3 which shows a 3rd example similarly. The figure equivalent to FIG. 1 which shows a 4th example similarly. The figure equivalent to FIG. 1 which shows a 5th example similarly. The figure equivalent to FIG. 1 which shows the 6th example similarly. The figure equivalent to FIG. 1 which shows a 7th example similarly. The figure which corresponds to FIG. 3 similarly. The figure equivalent to FIG. 3 which shows the 8th example of embodiment of this invention. The figure equivalent to FIG. 3 which shows the 9th example similarly. The figure equivalent to FIG. 3 which shows the 1st example of the reference example regarding this invention . The figure equivalent to FIG. 1 which shows the 2nd example of a reference example similarly . The figure which corresponds to FIG. 3 similarly. The schematic side view which shows an example of the rotation transmission apparatus with a torque measuring device of a conventional structure.

[First example of embodiment]
A first example of the 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 hollow (hollow cylindrical) torque transmission shaft 6 that functions as an input shaft (or counter shaft) such as a belt type CVT, and a pair of rolling bearings 7a and 7b. And an input gear 8, an output gear 9, an inner shaft 10, a first encoder 11, a second encoder 12, one sensor unit 13, and a housing (mission case) 14.

  The torque transmission shaft 6 is made of an alloy steel such as carbon steel in a hollow cylindrical shape, and 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. At the same time, the surface carbon concentration is set to 0.2% or more. In the case of this example, the input gear 8 for inputting torque to the torque transmission shaft 6 is provided at an intermediate portion in the axial direction of the torque transmission shaft 6 and separately from the torque transmission shaft 6. The output gear 9 for outputting torque is provided at a portion closer to one end in the axial direction of the torque transmission shaft 6 (a portion closer to the right end in FIG. 1) separately from the torque transmission shaft 6. In addition, both side portions (the other end portion in the axial direction and the one end portion in the axial direction) of the torque transmission shaft 6 sandwiching the portion where the input gear 8 and the output gear 9 are installed are connected to the pair of rolling bearings 7a. , 7b so as to be rotatable with respect to the housing 14.

  The input gear 8 and the output gear 9 are helical gears or spur gears made of alloy steel such as carbon steel, and are provided separately from the torque transmission shaft 6. For this reason, with respect to the fitting portion of the input gear 8 and the output gear 9, a cylindrical surface fitting portion for ensuring concentricity and an involute spline engaging portion for preventing relative rotation are provided in the axial direction. Adopted a configuration adjacent to.

  The double rolling bearings 7a (7b) are, for example, deep groove type, angular type ball bearings, tapered roller bearings, cylindrical roller bearings, radial needle bearings, self-aligning roller bearings, etc. (in the illustrated example, ball bearings), Each of them is composed of an annular outer ring 15a (15b) and an inner ring 16a (16b), and a plurality of rolling elements 17,17. Of these, the outer ring 15a (15b) is a stationary ring that does not rotate during use, and is fitted and fixed to the housing 14. The inner ring 16a (16b) is a rotating wheel that rotates when in use, and is externally fixed to the torque transmission shaft 6. Each of the rolling elements 17, 17 includes an outer ring raceway formed on the inner circumferential surface of the intermediate portion in the axial direction of the outer ring 15a (15b), and an inner ring raceway formed on the outer peripheral surface of the inner ring 16a (16b) in the axial direction intermediate portion. In between, it is provided to be able to roll while being held by a cage. In the case of this example, the two rolling bearings 7a and 7b have opposite contact angles.

  Particularly in the case of this example, in order to prevent relative rotation between the inner ring 16a constituting the rolling bearing 7a and the torque transmission shaft 6 to which the inner ring 16a is externally fitted and fixed, the inner ring 16a and the torque transmission shaft 6 are A key engaging portion 18 corresponding to the inner detent mechanism described in the claims is provided in the portion. More specifically, as shown in FIGS. 1 and 3, the inner ring 16 a has a radial direction in a part of the inner circumferential surface of the inner ring 16 a in the circumferential direction of one half of the axial direction (the right half of FIG. 1). An inner ring side keyway 19 that is recessed outward is formed. Further, a shaft-side key groove 20 that is recessed radially inward is formed in a part of the outer peripheral surface of the torque transmission shaft 6 in the circumferential direction at a portion near the other end in the axial direction (portion near the left end in FIG. 1). ing. A rectangular plate-like key member 21 is press-fitted into both the grooves 19 and 20 in a state of straddling the inner ring side key groove 19 and the shaft side key groove 20 in the radial direction. This mechanically prevents relative rotation between the inner ring 16a and the torque transmission shaft 6. Further, in the case of this example, the width dimension of the key member 21 in the free state is slightly larger than the width dimension of the inner ring side key groove 19 and the shaft side key groove 20 in the free state, The inner ring 16a and the torque transmission shaft 6 are prevented from rattling in the circumferential direction.

  The inner shaft 10 is made of an alloy steel such as carbon steel or a synthetic resin in a substantially cylindrical shape (or a circular tube), and is concentric with the torque transmission shaft 6 on the inner diameter side of the torque transmission shaft 6. Is arranged. The inner shaft 10 has one axial end (the right end in FIG. 1) connected to one axial end of the torque transmission shaft 6 in a relatively non-rotatable manner and the other axial end (FIG. 1). The left end portion of the torque transmission shaft 6 protrudes from the other axial opening of the torque transmission shaft 6 to the other axial side. In the case of the illustrated structure, one axial end portion of the inner shaft 10 is provided at one axial end portion of the inner shaft 10 so as not to be relatively rotatable with the one axial end portion of the torque transmission shaft 6. The outer peripheral surface of the large-diameter portion 22 and the inner peripheral surface of one axial end portion of the torque transmission shaft 6 are fitted and fixed by an interference fit so as not to be relatively rotatable. In addition, in order to connect these both peripheral surfaces so that relative rotation is impossible, the engagement by an involute spline or a key can also be employ | adopted, for example. In the case of this example, a portion of the inner shaft 10 between the outer peripheral surface of the portion that is axially disengaged from the large diameter portion 22 and the inner peripheral surface of the torque transmission shaft 6 is a shaft. A gap (a minute gap) is provided over the entire length and the entire circumference. The portion between these can be filled with lubricating oil and function as a film damper.

  The first encoder 11 is supported and fixed to an inner ring 16a constituting the rolling bearing 7a. In other words, the first encoder 11 is indirectly attached to a portion near the other end in the axial direction of the torque transmission shaft 6 via the inner ring 16a constituting the rolling bearing 7a. For this reason, the first encoder 11 can rotate (synchronously) with a portion closer to the other axial end of the torque transmission shaft 6. On the other hand, the second encoder 12 is externally fixed to a portion of the inner shaft 10 that protrudes from the other axial opening of the torque transmission shaft 6 to the other axial side (the other axial end). Has been. In other words, the second encoder 12 is indirectly attached to one axial end portion of the torque transmission shaft 6 via the inner shaft 10. For this reason, the second encoder 12 can rotate (synchronously) together with one end of the torque transmission shaft 6 in the axial direction.

  The first and second encoders 11 and 12 are cross-sectional cranks made of a magnetic metal plate supported and fixed to the inner ring 16a constituting the rolling bearing 7a or the other axial end of the inner shaft 10. In the form of an annular support ring 23, 24, and magnetic powder is dispersed in a polymer material such as rubber or synthetic resin fixed to the outer peripheral surface of each of the support rings 23, 24 to form a cylindrical shape as a whole. Encoder bodies 25 and 26 made of permanent magnets such as rubber magnets and plastic magnets. Examples of the magnetic powder contained in the encoder bodies 25 and 26 include ferrite-based magnetic powder such as strontium ferrite and barium ferrite, and rare earth elements such as samarium-iron, samarium-cobalt, and neodymium-iron-boron. Magnetic powder can be used. The outer peripheral surface of the encoder body 25 constituting the first encoder 11 is defined as a first detected surface 27, and the outer peripheral surface of the encoder body 26 constituting the second encoder 12 is defined as a second detected surface 28. It is said. These first and second detected surfaces 27 and 28 have the same diameter, are concentric with each other, and are adjacent to each other in the axial direction (for example, within 10 mm in the axial direction, preferably within 5 mm). Open). The first and second detected surfaces 27 and 28 have S poles and N poles arranged alternately and at equal pitches in the circumferential direction, respectively, and the magnetic characteristics are alternated in the circumferential direction. And at an equal pitch. The total number of magnetic poles (S pole and N pole) of the first and second detected surfaces 27 and 28 is the same. Although not shown, the first encoder (encoder main body) may be directly attached to the inner ring without a support ring. Although not shown, a female thread is formed on the inner peripheral surface of the support ring constituting the second encoder, and this female thread is screwed into a male thread formed on the other axial end of the inner shaft. Two encoders may be attached to the other axial end of the inner shaft. Further, in the case of this example, the sensor unit 13 including the first sensor 29 and the second sensor 30 is supported and fixed to an outer ring 15a that constitutes the rolling bearing 7a.

  A specific support structure of the first encoder 11 will be described with reference to FIGS. 1 and 2. As described above, the first encoder 11 includes the support ring 23 and the encoder body 25 fixed to the outer peripheral surface of the support ring 23. Of these, the support ring 23 is made by pressing a rolled steel plate such as SPCC having a plate thickness of about 0.5 to 1.3 mm, and is formed into a crank shape in cross section. A small-diameter cylindrical portion 31 for internal fitting and fixing, a large-diameter cylindrical portion 32 in which the encoder body 25 is fixed to the outer peripheral surface thereof, the other axial end of the small-diameter cylindrical portion 31 and the shaft of the large-diameter cylindrical portion 32. An annular portion 33 that is continuous with one end portion in the direction is provided. Of the support ring 23, a bent portion 34a that connects the small-diameter cylindrical portion 31 and the annular portion 33, and a bent portion 34b that continues the large-diameter cylindrical portion 32 and the annular portion 33. The respective curvature radii (bending R) are regulated in the range of 0.2 to 1.3 mm.

  Further, in the case of this example, the inner peripheral surface of the inner ring 16a is compared with one end part in the axial direction to the intermediate part (excluding the part where the inner ring side keyway 19 is formed) on the other end part in the axial direction. An attachment step 35 having a larger inner diameter is formed, and the small-diameter cylindrical portion 31 is press-fitted and fixed to the attachment step 35 in a range in which the press-fit tightening margin is about 20 to 400 μm. In the case of this example, by keeping the value of the press-fit tightening margin within the above range, the first encoder 11 is prevented from falling off, and damage during press-fitting is prevented. The inner diameter dimension of the mounting step portion 35 is a value obtained by doubling the plate thickness of the support ring 23 to the inner diameter dimension of the inner circumferential surface of the inner ring 16a that is off the mounting step portion 35 in the axial direction. It is larger than the total value added. In other words, the radial depth dimension of the mounting step 35 is made smaller than the plate thickness (diameter thickness) of the support ring 23 (small-diameter cylindrical portion 31). Thus, in a state where the small diameter cylindrical portion 31 is press-fitted and fixed to the mounting stepped portion 35, the inner peripheral surface of the small diameter cylindrical portion 31 is prevented from projecting radially inward from the inner peripheral surface of the inner ring 16a. The inner peripheral surface of the small diameter cylindrical portion 31 is prevented from contacting the outer peripheral surface of the torque transmission shaft 6. Further, in the case of this example, as described above, by restricting the curvature radius of each of the bent portions 34a and 34b to a small value, the contact area of the annular portion 33 with respect to the axial end surface of the inner ring 16a. The large-diameter cylindrical portion 32, and thus the encoder main body 25 fixed to the large-diameter cylindrical portion 32 is concentric with the inner ring 16a.

Although not included in the technical scope of the present invention, as shown in FIG. 7, the first encoder 11 is externally fitted to the other axial end (groove shoulder) of the outer peripheral surface of the inner ring 16a by an interference fit. A fixed configuration can also be adopted. In the case of the illustrated structure, the support ring 23 constituting the first encoder 11 includes a small-diameter cylinder portion 31a for fixing the encoder body 25 and a large-diameter cylinder for externally fixing to the outer peripheral surface of the inner ring 16a. It includes a portion 32a, and an annular portion 33a that is continuous with one axial end of the small diameter cylindrical portion 31a and the other axial end of the large diameter cylindrical portion 32a, and is configured in a crank shape in cross section. Even when such a support structure for the first encoder 11 is adopted, the value of the press-fitting allowance of the large-diameter cylindrical portion 32a is restricted to 20 to 400 μm, or the large-diameter cylindrical portion 32a and the small-diameter cylindrical portion 31a It is preferable to regulate the value of the radius of curvature of the bent portions 34a and 34b between the ring portion 33a and the range of 0.2 to 1.3 mm.

Next, the structure and specific support structure of the sensor unit 13 will be described with reference to FIGS. 4 to 6 in addition to FIGS.
In the case of this example, the sensor unit 13 includes the first sensor 29, the second sensor 30, a first substrate 36, a second substrate 37, a sensor support block 38, and a sensor cap 39. doing. Among these, the first sensor 29 (second sensor 30) includes a magnetic detection element such as a Hall element, Hall IC, and MR element (including GMR element, TMR element, and AMR element) as shown in FIG. The detection unit 40a (40b), a pair of terminals 41a, 41a (41b, 41b) drawn from the detection unit 40a (40b), and the length directions of both terminals 41a, 41a (41b, 41b) And a connecting member 42a (42b) that connects the intermediate portions without conducting them. In the case of this example, the terminals 41a and 41a (41b and 41b) are bent into a substantially U shape and used to support the first sensor 29 (second sensor 30).

  The sensor support block 38 is made of synthetic resin and is configured in a partial annular shape (arc plate shape), and the pair of mounting portions 43a and 43b are shifted in the axial position in a portion adjacent in the circumferential direction ( Provided in an offset state. In the case of this example, the first and second sensors 29 and 30 are attached to such attachment portions 43a and 43b. Specifically, the tip portions of the terminals 41a and 41a constituting the first sensor 29 and the tip portions of the terminals 41b and 41b constituting the second sensor 30 are opposite to each other in the axial direction (facing direction). Deploy. The first sensor 29 is supported by the mounting portion 43a so as to surround the mounting portion 43a from both sides in the radial direction and one axial side (the other end side) by the terminals 41a and 41a bent in a U-shape. To do. Similarly, the second sensor 30 is attached to the mounting portion 43b so that the mounting portion 43b is surrounded from both sides in the radial direction and one side (one end side) in the radial direction by the terminals 41b and 41b bent in a U-shape. Attach to. In addition, with the first and second sensors 29 and 30 attached in this manner, the attachment portions 43a and 43b are arranged in the radial direction between the detection portions 40a and 40b and the connection members 42a and 42b. It is clamped elastically from both sides. In addition, with the first and second sensors 29 and 30 attached to the sensor support block 38, the leading ends of the terminals 41a, 41a, 41b and 41b are connected to the first and second substrates 36, 37 are electrically connected to each other.

  The first and second substrates 36 and 37 are formed in a substantially circular arc plate shape, and are supported on both axial sides of the sensor support block 38. Specifically, the first and second substrates 36 and 37 are fixed to engagement holes 44 and 44 formed at a plurality of positions in a fixing pin (engagement) formed on the side surface in the axial direction of the sensor support block 38. By engaging (press-fitting) the convex portions 45, 45, the sensor support block 38 is supported on the side surface in the axial direction. In the case of this example, the first and second substrates 36 and 37 are electrically connected at one end in the circumferential direction, and a harness 46 is electrically connected to the first substrate 36 among them. doing.

  In this example, the first and second sensors 29 and 30 are attached to the sensor support block 38 and the first and second substrates 36 and 37 are supported. 29, 30, 36, 37 and 38 are accommodated in the sensor cap 39. The sensor cap 39 is manufactured by pressing a rolled steel plate such as SPCC having a plate thickness of about 0.5 to 1.3 mm, and has a substantially annular shape as a whole. Specifically, the sensor cap 39 includes a ring-shaped bottom portion 47, an outer cylindrical portion 48 provided in a state of being bent at a right angle from the outer diameter side end portion of the bottom portion 47 toward one end side in the axial direction, An abutment ring portion 49 provided in a state of being bent at a right angle from one axial end portion of the outer cylindrical portion 48 toward the radially inward direction, and one axial end side from the radial intermediate portion of the abutment ring portion 49 And a supporting cylinder portion 50 provided so as to protrude toward the surface.

  In the case of this example, the sensor cap 39 having the above-described configuration is supported and fixed to an outer ring 15a that constitutes the rolling bearing 7a. For this reason, the inner diameter of the inner peripheral surface of the outer ring 15a is larger at the other axial end of the shoulder 52 provided on the other axial side of the outer ring raceway 51 formed at the axial center. The formed fitting step part 53 is formed. And the support cylinder part 50 is press-fitted and fixed to the fitting step part 53 in a range in which the press-fitting allowance is about 20 to 400 μm. This prevents the sensor cap 39 from falling off and prevents damage during press-fitting. Further, the rolling element (ball) 17 constituting the rolling bearing 7 a rides on the shoulder 52 while keeping the inner diameter dimension of the shoulder 52 adjacent to the outer ring raceway 51 in the axial direction small. Is preventing.

  Further, the first and second sensors 29 and 30, the first and second substrates 36 and 37, and the sensor support block 38, which are combined with each other as described above, are connected to the first substrate 36. One end of the harness 46 is sealed with a resin adhesive (not shown) such as an epoxy adhesive or a silicon adhesive (embedded in the resin member), and the inside of the sensor cap 39 The fixing pins 45 and 45 are used for holding and fixing. In this state, the remaining portion of the harness 46 is pulled out in the axial direction through a harness lead-out hole 54 formed in a part of the bottom portion 47. In the case of this example, the detection part 40a constituting the first sensor 29 installed on the inner side in the state where the sensor cap 39 is press-fitted and fixed to the fitting step part 53 of the outer ring 15a, While facing the outer peripheral surface (first detected surface 27) of one encoder 11 through a minute gap in the radial direction, the detection unit 40b constituting the second sensor 30 is placed on the outer peripheral surface ( It is opposed to the second detected surface 28) via a minute gap in the radial direction. For this reason, the first sensor 29 changes the output signal in response to the change in magnetic characteristics of the first encoder 11, and the second sensor 30 outputs in response to the change in magnetic characteristics of the second encoder 12. Change the signal. Then, the output signals of the first and second sensors 29 and 30 are transmitted to a calculator (not shown) through one harness 46 drawn in the axial direction. In addition, power is supplied to the first and second sensors 29 and 30 through the harness 46.

  In the case of the rotation transmission device 5 with the torque measuring device of the present example having the above-described configuration, the output signals of both the first and second sensors 29 and 30 constituting the sensor unit 13 together with the torque transmission shaft 6 are described above. As both the first and second encoders 11 and 12 rotate, they change periodically. Here, the frequency (and period) of this change takes a value commensurate with 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). 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 at the portion between the input gear 8 and the output gear 9. The two (first and second two encoders 11 and 12) are relatively displaced in the rotational direction. As a result of the relative displacement of the first and second two encoders 11 and 11 in the rotational direction in this way, the phase difference ratio between the output signals of the first and second sensors 29 and 30 (= 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 calculated based on the phase difference ratio. This calculation process is performed by the calculator. For this reason, in this computing unit, the relationship between the phase difference ratio and the torque, which has been examined in advance by theoretical calculation or experiment, is incorporated in a model such as a calculation formula or a map.

Further, according to the rotation transmission device 5 with the torque measuring device of this example, the assembly workability can be improved.
That is, in the case of this example, the first encoder 11 is attached to the inner ring 16a constituting the rolling bearing 7a which is smaller in size and lighter in weight than the torque transmission shaft 6. Compared with the case where the first encoder 11 is directly attached to the torque transmission shaft 6, the workability of attaching the first encoder 11 can be improved. Further, since the first sensor 29 and the second sensor 30 are supported and fixed to the outer ring 15a constituting the rolling bearing 7a via the sensor support block 38 and the sensor cap 39, the first, Compared with the case where the second sensors 29 and 30 are directly supported by the housing 14, the workability of attaching the first and second sensors 29 and 30 can be improved. Therefore, in the case of this example, the assembly workability of the rotation transmission device 5 with the torque measuring device can be improved.

  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. Since it can transmit to the inner shaft 10 protruding from the other end opening, the first encoder 11 for detecting the phase of the other axial end portion of the torque transmission shaft 6 and one axial end portion of the torque transmission shaft 6 The second encoder 12 for detecting the phase of the torque transmission shaft 6 can be disposed adjacent to the other end portion in the axial direction of the torque transmission shaft 6 (collectively disposed). Therefore, one sensor unit 13 in which the first and second sensors 29 and 30 are held by the sensor support block 38 can be used. From this aspect, the sensor mounting workability can be improved. Specifically, the first and second sensors 29 and 30 can be positioned with high accuracy by performing the operation of attaching the sensor cap 39 to the outer ring 15a constituting the rolling bearing 7a only once. . Moreover, since the number of harnesses can be reduced from two {harness 4, 4 (see FIG. 20)} to one {harness 46 (see FIGS. 1-2, 4)}, the wiring work of the harness can be simplified. In addition to being able to achieve good handling performance, cost and weight can be reduced.

In addition, since the sensor cap 39 supporting the first and second sensors 29 and 30 is supported and fixed to the outer ring 15a constituting the rolling bearing 7a, the rolling bearing 7a is used to perform the rolling. the positioning of the first sensor 29 can be easily achieved for the first encoder 11, which is supported by and fixed to the inner race 16a constituting the bearing 7a. For this reason, the positional relationship between the first encoder 11 and the first sensor 29 can be easily and strictly regulated. In the case of this example, the second sensor 30 can be positioned using the rolling bearing 7a. Therefore, the detection surfaces (first and second) of the detection parts of the first and second sensors 29 and 30 and the first and second encoders 11 and 12 (especially the first encoder 11 supported by the inner ring). The gap in the radial direction between the two detected surfaces 27 and 28) can be easily and strictly managed.

  Furthermore, in the case of this example, the key engaging portion 18 is provided between the inner ring 16a that supports the first encoder 11 and the torque transmission shaft 6 that is fitted and fixed to the inner ring 16a. . For this reason, relative rotation of the inner ring 16a supporting the first encoder 11 and the torque transmission shaft 6 can be prevented. Therefore, it is possible to prevent a phase difference from occurring between the output signals of the first and second sensors 29 and 30 based on the relative rotation between the inner ring 16a and the torque transmission shaft 6. As a result, according to the rotation transmission device 5 with the torque measuring device of this example, it is possible to improve the measurement accuracy of the torque.

  Further, the terminals 41a and 41b constituting the first and second sensors 29 and 30 are bent in a substantially U-shape from the detection portions 40a and 40b constituting the first and second sensors 29 and 30, respectively. The first and second sensors 29 and 30 are supported by the sensor support block 38 so as to surround the sensor support block 38 from both sides in the radial direction and one side in the axial direction by these terminals 41a and 41b. doing. For this reason, compared with the case where the structure which arrange | positions a linear terminal in radial direction (radial direction) or an axial direction is employ | adopted, the dimension regarding the radial direction and axial direction of both said 1st, 2nd sensors 29 and 30 is adopted. Can be kept small. Therefore, according to the structure of this example, the first and second sensors 29 and 30 can be downsized. As a result, it is possible to prevent the sensor cap 39 supporting both the first and second sensors 29 and 30 from projecting radially outward from the outer ring 15a constituting the rolling bearing 7a. The outer ring 15a can be disposed on the inner diameter side of the housing 14 in which the inner ring 15a is fitted and fixed.

  Further, since the small-diameter cylindrical portion 31 of the support ring 23 constituting the first encoder 11 is press-fitted and fixed to the mounting step portion 35 formed at the other axial end portion of the inner peripheral surface of the inner ring 16a, It becomes possible to keep the outer diameter dimension of the first detected surface 27 of the first encoder 11 small. For this reason, the outer diameter of the sensor cap 39 supporting the first and second sensors 29 and 30 can be kept small.

  Further, since the first and second sensors 29 and 30 are arranged in opposite directions with respect to the axial direction in a state where the phase (position) in the circumferential direction is shifted, the axial dimension of the sensor unit 13 is determined. Can be shortened. Further, since the harness 46 is pulled out in the axial direction, the harness 46 is not obstructed when the rolling bearing 7a to which the sensor unit 13 is attached is fitted and fixed to the housing 14. It is possible to prevent the workability from being lowered.

  Furthermore, since the surface hardness of the torque transmission shaft 6 is HV400 or more and the surface carbon concentration is 0.2% or more, the durability of the torque transmission shaft 6 can be improved. Therefore, the rotation transmission device 5 with the torque measuring device of the present example can be preferably applied to applications such as automobiles and wind power generators that require particularly durability. In addition, since the torque transmission shaft 6 is rotatably supported by the both rolling bearings 7a and 7b, the friction torque acting on the torque transmission shaft 6 can be reduced as compared with the case where the structure is supported by the sliding bearing. Can be kept small. Therefore, it is possible to secure a large torque transmitted by the torque transmission shaft 6 and to improve the measurement accuracy of the torque obtained from the output signals of the first and second sensors 29 and 30.

[Second Example of Embodiment]
A second example of the embodiment of the present invention will be described with reference to FIG. The feature of this example lies in the structure of a key engaging portion 18a provided between the inner ring 16a constituting the rolling bearing 7a and the torque transmission shaft 6 to which the inner ring 16a is externally fitted and fixed. That is, in this example, an inner ring side key groove 19 that is recessed radially outward is formed in a part of the inner circumferential surface of the inner ring 16a in the circumferential direction, and the torque transmission shaft 6 A shaft-side convex portion 55 having a rectangular cross section protruding outward in the radial direction is formed on a part of the outer circumferential surface in the circumferential direction. The key engagement portion 18a is configured by press-fitting the shaft-side convex portion 55 into the inner ring-side key groove 19 without a gap. With such a configuration, in the case of this example, the cost can be reduced by reducing the number of parts compared to the case of the first example of the embodiment.
Also in the case of this example, the width dimension in the free state of the shaft-side convex portion 55 is slightly larger than the dimension in the width direction in the free state of the inner ring-side key groove 19, and the inner ring 16a and The torque transmission shaft 6 is prevented from rattling in the circumferential direction.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Third example of embodiment]
A third example of the embodiment of the present invention will be described with reference to FIG. The feature of this example lies in the structure of a key engaging portion 18b provided in a portion between the inner ring 16a constituting the rolling bearing 7a and the torque transmission shaft 6 to which the inner ring 16a is externally fitted and fixed. That is, in the case of this example, an inner ring-side convex portion 56 having a rectangular cross section protruding radially inward is formed on a part of the inner circumferential surface of the inner ring 16a in the circumferential direction, and the torque A shaft-side keyway 20 that is recessed radially inward is formed in a part of the outer peripheral surface of the transmission shaft 6 in the circumferential direction. The key engagement portion 18b is configured by press-fitting the inner ring side convex portion 56 into the shaft side key groove 20 without a gap. With such a configuration, in the case of this example, the cost can be reduced by reducing the number of parts compared to the case of the first example of the embodiment.
Also in the case of this example, the width dimension in the free state of the inner ring side convex portion 56 is slightly larger than the width direction dimension in the free state of the shaft side key groove 20, and the inner ring 16a and The torque transmission shaft 6 is prevented from rattling in the circumferential direction.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Fourth Example of Embodiment]
A fourth example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is that the sensor cap 39a constituting the sensor unit 13a is replaced with an outer ring 15a constituting a rolling bearing 7a that rotatably supports the portion near the other axial end of the torque transmission shaft 6 with respect to the housing 14. Thus, a configuration in which it is supported and fixed (fixed by internal fitting) is employed. In the case of this example having such a configuration, the degree of freedom regarding the attachment structure of the sensor cap 39a can be increased as compared with the case of the first example of the embodiment (when attaching to the outer ring 15a). In addition, since the first and second sensors 29 and 30 are displaced in the same direction with respect to the first and second encoders 11 and 12 when the housing 14 is deformed, the deformation of the housing 14 is caused by torque. The influence on detection accuracy can be reduced.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Fifth Example of Embodiment]
A fifth example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is that the inner shaft is omitted from the structure of the first example of the embodiment, and the set of the first encoder 11 and the first sensor 29 and the set of the second encoder 12 and the second sensor 30 are The torque transmission shaft 6 is disposed on both sides in the axial direction in a state of being separated in the axial direction. Since the configuration and operational effects of other parts are the same as in the case of the first example of the embodiment, the characteristic parts of this example will be described below.

  Also in this example, both axial ends of the torque transmission shaft 6 are rotatably supported by the housing 14 by a pair of rolling bearings 7a and 7b. Of the first and second encoders 11 and 12, the first encoder 11 is supported and fixed to an inner ring 16a that constitutes the rolling bearing 7a. In other words, the first encoder 11 is indirectly attached to the other axial end portion of the torque transmission shaft 6 via the inner ring 16a constituting the rolling bearing 7a. For this reason, the first encoder 11 can rotate (synchronously) with the other axial end of the torque transmission shaft 6. On the other hand, the second encoder 12 is supported and fixed to an inner ring 16b that constitutes the rolling bearing 7b. In other words, the second encoder 12 is indirectly attached to one end portion in the axial direction of the torque transmission shaft 6 via the inner ring 16b constituting the rolling bearing 7b. For this reason, the second encoder 12 can rotate (synchronously) together with one end of the torque transmission shaft 6 in the axial direction. The support structure for the first and second encoders 11 and 12 with respect to the inner rings 16a and 16b is the same as in the first example of the embodiment.

  In the case of this example, in order to prevent relative rotation between the inner ring 16a constituting the rolling bearing 7a and the torque transmission shaft 6 to which the inner ring 16a is externally fitted and fixed, a portion between the inner ring 16a and the torque transmission shaft 6 is provided. In addition, a key engaging portion 18 is provided. More specifically, the inner ring-side keyway 19 that is recessed radially outwardly in a part of the inner circumferential surface of the inner ring 16a in the circumferential direction of one axial half (the right half in FIG. 11). Is forming. A shaft-side key groove 20 that is recessed radially inward is formed in a part of the outer peripheral surface of the torque transmission shaft 6 in the circumferential direction at a portion near the other end in the axial direction (portion near the left end in FIG. 11). ing. A key member 21 is press-fitted into both the grooves 19 and 20 in a state of straddling the inner ring side key groove 19 and the shaft side key groove 20 in the radial direction. This mechanically prevents relative rotation between the inner ring 16a and the torque transmission shaft 6. Further, in the case of this example, in order to prevent relative rotation between the inner ring 16b constituting the rolling bearing 7b and the torque transmission shaft 6 to which the inner ring 16b is fitted and fixed, the inner ring 16b and the torque transmission shaft 6 are prevented. A key engaging portion 18c is provided in a portion between the two. More specifically, an inner ring-side keyway that is recessed radially outward in a part of the inner circumferential surface of the inner ring 16b in the circumferential direction of the other half in the axial direction (the left half in FIG. 11). 19a is formed. Further, on the outer peripheral surface of the torque transmission shaft 6, a shaft-side key groove 20 a that is recessed inward in the radial direction is formed in a part in the circumferential direction of a portion near one end in the axial direction (portion near the right end in FIG. 11). Yes. The key member 21a is press-fitted into both the grooves 19a and 20a in a state straddling the inner ring side key groove 19a and the shaft side key groove 20a in the radial direction. Thereby, relative rotation between the inner ring 16b and the torque transmission shaft 6 is mechanically prevented.

  In the case of this example, of the first and second sensors 29, 30, the first sensor 29 is supported and fixed to the outer ring 15a constituting the rolling bearing 7a, and the second sensor 30 is It is supported and fixed to the outer ring 15b constituting the rolling bearing 7b. More specifically, the first sensor 29 is combined with a first substrate 36, a sensor holding block 38a, and a sensor cap 39b to constitute a sensor unit 13b, which is supported and fixed to the outer ring 15a. Similarly, for the second sensor 30, the sensor unit 13c is configured in combination with the second substrate 37, the sensor holding block 38b, and the sensor cap 39c, and is supported and fixed to the outer ring 15b.

  In the case of this example, each of the sensor support blocks 38a and 38b is made of synthetic resin, is configured in a partial annular shape, and has a mounting portion only at one place in the circumferential direction. The first and second sensors 29 and 30 are attached to the attachment portion, respectively. Specifically, the first and second sensors 29 and 30 are configured by the substantially U-shaped terminals 41a and 41b so as to surround the mounting portions from both sides in the radial direction and one side in the axial direction. The first and second sensors 29 and 30 are attached to the attachment portions.

  The first and second substrates are respectively supported by the tip portions of the terminals 41a and 41b constituting the first and second sensors 29 and 30 on the axial side surfaces of the sensor support blocks 38a and 38b, respectively. 36 and 37 are electrically connected to each other. In addition, harnesses 46 and 46 are electrically connected to the first and second substrates 36 and 37, respectively.

  In this example, the first and second sensors 29 and 30 are attached to the sensor support blocks 38a and 38b, and the first and second substrates 36 and 37 are supported. Thus, the members 29, 36, and 38a are accommodated in the sensor cap 39b, and the members 30, 37, and 38b are accommodated in the sensor cap 39c. Of these sensor caps 39b and 39c, one sensor cap 39b is supported and fixed (internally fixed) to the outer ring 15a constituting the rolling bearing 7a, and the other sensor cap 39c is fixed to the rolling bearing 7b. It is supported and fixed (fixed by internal fitting) to the outer ring 15b that constitutes it. Note that the support structure for both the sensor caps 39b and 39c is basically the same as in the first example of the above embodiment.

With the configuration as described above, the detection unit 40a configuring the first sensor 29 installed inside the sensor cap 39b is arranged in the radial direction with respect to the outer peripheral surface (first detected surface 27) of the first encoder 11. The detection portion 40b that constitutes the second sensor 30 disposed inside the sensor cap 39c is opposed to the outer peripheral surface (second detected surface 28) of the second encoder 12 with a small gap between them. On the other hand, they are opposed to each other through a minute gap in the radial direction. For this reason, the first sensor 29 changes the output signal in response to the change in magnetic characteristics of the first encoder 11, and the second sensor 30 outputs in response to the change in magnetic characteristics of the second encoder 12. Change the signal. Then, the output signals of the first and second sensors 29 and 30 are transmitted to a calculator (not shown) through the two harnesses 46 and 46 drawn in the axial direction. Further, electric power is supplied to the first and second sensors 29 and 30 through the harnesses 46 and 46.
In carrying out the present invention, only one of the first and second encoders 11 and 12 is supported and fixed to the inner ring, and the other encoder is attached to the end of the torque transmission shaft. A structure of directly supporting and fixing may be employed. In this case, a key engagement portion (inner detent mechanism) can be provided between the inner ring that supports and fixes the one encoder and the torque transmission shaft 6.

  In the case of the rotation transmission device 5 with the torque measuring device of the present example having the above-described configuration, the output signals of the first and second sensors 29 and 30 together with the torque transmission shaft 6 are the first and second encoders. As 11 and 12 rotate, each changes periodically. Here, the frequency (and period) of this change takes a value commensurate with 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). Further, when torque is transmitted by the torque transmission shaft 6, both ends in the axial direction of the torque transmission shaft 6 are elastically deformed as the portion between the input gear 8 and the output gear 9 is elastically twisted and deformed ( The first and second encoders 11 and 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 (= phase difference) between the output signals of the first and second sensors 29 and 30 is obtained. / 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.

Further, in the case of the rotation transmission device 5 with the torque measuring device of this example, the first and second encoders 11 among the pair of rolling bearings 7a and 7b that rotatably support the torque transmission shaft 6; 12, key engagement portions 18 and 18c are respectively provided between the inner rings 16a and 16b that support 12 and the torque transmission shaft 6. For this reason, relative rotation of the inner rings 16a and 16b and the torque transmission shaft 6 can be prevented. Accordingly, also in this example, a phase difference is generated between the output signals of the first and second sensors 29 and 30 based on the relative rotation between the inner rings 16a and 16b and the torque transmission shaft 6. You can prevent things. As a result, according to the rotation transmission device 5 with the torque measuring device of this example, it is possible to improve the measurement accuracy of the torque.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment.

[Sixth Example of Embodiment]
A sixth example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is that the sensor cap 39b constituting the sensor unit 13b is replaced with an outer ring 15a constituting a rolling bearing 7a that rotatably supports a portion near the other axial end of the torque transmission shaft 6 with respect to the housing 14. The sensor cap 39c that constitutes the sensor unit 13c is supported and fixed (internally fitted), in place of the outer ring 15b that constitutes the rolling bearing 7b that rotatably supports a portion near the one end of the torque transmission shaft 6 in the axial direction. The point is that the housing 14 is supported and fixed (fixed by internal fitting). In the case of this example having such a configuration, the degree of freedom regarding the mounting structure of the sensor caps 39b and 39c can be increased as compared with the case of the fifth example of the embodiment. In addition, since the first and second sensors 29 and 30 are displaced in the same direction with respect to the first and second encoders 11 and 12 when the housing 14 is deformed, the deformation of the housing 14 is caused by torque. The influence on detection accuracy can be reduced.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment, and a 5th example.

[Seventh example of embodiment]
A seventh example of the embodiment of the present invention will be described with reference to FIGS. In the first to sixth examples of the above-described embodiment, an inner detent mechanism (key engagement) is provided between the inner ring constituting the rolling bearing with the encoder fixed and the torque transmission shaft to which the inner ring is fitted and fixed. The structure provided with the joint part) was explained. On the other hand, in the case of this example, the basic configuration is the same as in the case of the fifth example of the above-described embodiment, and instead of the inner detent mechanism, a rolling bearing 7a to which the first sensor 29 is fixed is provided. A portion between the outer ring 15a constituting the housing 14 to which the outer ring 15a is fitted and fixed, an outer ring 15b constituting the rolling bearing 7b to which the second sensor 30 is fixed, and the housing to which the outer ring 15b is fitted and fixed. 14 is provided with key engaging portions 57 and 57a, which are outer detent mechanisms, respectively.

More specifically, of the outer peripheral surface of the outer ring 15a constituting the rolling bearing 7a, the outer circumferential surface of the outer ring 15a is recessed inward in the radial direction at a part in the circumferential direction of one axial half (right half in FIG. 13). An outer ring side keyway 58 is formed. In addition, a housing-side key groove 59 that is recessed radially outward is formed in a part of the housing 14 in the circumferential direction of the portion where the outer ring 15a is fitted and fixed. The key member 60 is press-fitted into both the grooves 58 and 59 in a state of straddling the outer ring side key groove 58 and the housing side key groove 59 in the radial direction. Thereby, the relative rotation of the outer ring 15a and the housing 14 is mechanically prevented. Similarly, on the outer ring side of the outer ring 15b constituting the rolling bearing 7b, the outer ring side is recessed radially inward at a part in the circumferential direction of the other half in the axial direction (the left half in FIG. 13). A key groove 58a is formed. In addition, a housing-side key groove 59a that is recessed outward in the radial direction is formed in a part of the housing 14 in the circumferential direction of the portion where the outer ring 15b is fitted and fixed. Then, in a state straddling the outer ring side key groove 58a and the housing side key groove 59a in the radial direction, a key member 60a corresponding to the key described in the claims is press-fitted into both the grooves 58a, 59a. ing. Thereby, relative rotation between the outer ring 15b and the housing 14 is mechanically prevented. Also in this example, the width dimension of the key member 60 in the free state is slightly larger than the width dimension of the outer ring side key groove 58 and the housing side key groove 59 in the free state, The outer ring 15a and the housing 14 are prevented from rattling in the circumferential direction, and the width dimension of the key member 60a is slightly larger than the width dimension of the outer ring side key groove 58a and the housing side key groove 59a. Thus, the outer ring 15b and the housing 14 are prevented from rattling in the circumferential direction.

In the case of this example having the above-described configuration, the key engaging portion 57 is provided between the outer ring 15a that supports the first sensor 29 and the housing 14 that is fitted and fixed to the outer ring 15a. At the same time, the key engaging portion 57a is provided in a portion between the outer ring 15b that supports the second sensor 30 and the housing 14 in which the outer ring 15b is fitted and fixed. Therefore, the outer ring 15a supporting the first sensor 29 and the housing 14 can be prevented from rotating relative to each other, and the outer ring 15b supporting the second sensor 30 and the housing 14 can be rotated relative to each other. Can be prevented. Therefore, it is possible to prevent a phase difference from occurring between the output signals of the first and second sensors 29 and 30 based on the relative rotation between the outer rings 15a and 15b and the housing 14. As a result, according to the rotation transmission device 5 with the torque measuring device of this example, it is possible to improve the measurement accuracy of the torque.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment, and a 5th example.

[Eighth Example of Embodiment]
An eighth example of the embodiment of the present invention will be described with reference to FIG. The feature of this example is the structure of the key engagement portion 57b provided in the portion between the outer ring 15a (15b) constituting the rolling bearing 7a (7b) and the housing 14 in which the outer ring 15a (15b) is fitted and fixed. is there. In other words, in the case of this example, a part of the outer peripheral surface of the outer ring 15a (15b) in the circumferential direction has a rectangular cross-section projecting radially outward corresponding to the key recited in the claims. The outer ring side convex portion 61 is formed, and a housing side key groove 59 (59a) that is recessed radially outward is formed in a part of the inner circumferential surface of the housing 14 in the circumferential direction. The key engagement portion 57b is configured by press-fitting the outer ring side convex portion 61 into the housing side key groove 59 (59a) without a gap. With such a configuration, in the case of this example, the cost can be reduced by reducing the number of parts compared to the case of the seventh example of the above embodiment.
Also in the case of this example, the width dimension in the free state of the outer ring side convex portion 61 is slightly larger than the dimension in the width direction in the free state of the housing side key groove 59 (59a). The outer ring 15a (15b) and the housing 14 are prevented from rattling in the circumferential direction.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment, and a 5th example.

[Ninth Embodiment]
A ninth example of the embodiment of the invention will be described with reference to FIG. The feature of this example is the structure of the key engagement portion 57c provided in the portion between the outer ring 15a (15b) constituting the rolling bearing 7a (7b) and the housing 14 in which the outer ring 15a (15b) is fitted and fixed. is there. That is, in the case of this example, an outer ring side key groove 58 (58a) that is recessed radially inward is formed in a part of the outer circumferential surface of the outer ring 15a (15b) in the circumferential direction. A part of the inner circumferential surface of the housing 14 in the circumferential direction is formed with a housing-side convex portion 62 having a rectangular cross-section projecting radially inward , corresponding to the key described in the claims . The key engagement portion 57c is configured by press-fitting the housing-side convex portion 62 into the outer ring-side key groove 58 (58a) without a gap. With such a configuration, in the case of this example, the cost can be reduced by reducing the number of parts compared to the case of the seventh example of the above embodiment.
Also in the case of this example, the width dimension in the free state of the housing side convex portion 62 is slightly larger than the width direction dimension in the free state of the outer ring side key groove 58 (58a), The outer ring 15a (15b) and the housing 14 are prevented from rattling in the circumferential direction.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment, and a 5th example.

[ First example of reference example ]
A first example of a reference example relating to the present invention will be described with reference to FIG. The feature of this reference example is an outer detent mechanism (non-circular) provided between the outer ring 15a (15b) constituting the rolling bearing 7a (7b) and the housing 14 in which the outer ring 15a (15b) is fitted and fixed. (Fitting) structure. That is, in the case of this reference example, the outer ring side flat surface portion 63 having a linear cross section is formed on a part of the outer circumferential surface of the outer ring 15a (15b) in the circumferential direction. A housing-side flat surface portion 64 having a linear cross-sectional shape is formed on a portion of the inner peripheral surface in the circumferential direction. Then, with the outer ring 15a (15b) fitted and fixed inside the housing 14, the outer ring side flat surface portion 63 and the housing side flat surface portion 64 are brought into contact with each other to be non-circularly fitted. With such a configuration, in the case of the present reference example, the cost can be reduced by reducing the number of parts as compared with the case of the seventh example of the embodiment.
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment, and a 5th example.

[ Second example of reference example ]
A second example of the reference example related to the present invention will be described with reference to FIGS. The feature of this reference example is that an outer detent mechanism (bolt) provided between the outer rings 15a and 15b constituting the rolling bearings 7a and 7b and the housing 14 in which the outer rings 15a and 15b are fitted and fixed. In the structure. That is, in the case of this reference example, screw holes 65a and 65b penetrating in the diametrical direction are formed in portions of the housing 14 where the outer rings 15a and 15b are fitted and fixed, respectively. The fixing screws 66a and 66b are screwed into the screw holes 65a and 65b from the outside in the radial direction. And the outer peripheral surface of each said outer ring | wheel 15a, 15b fixed to the said housing 14 is hold | suppressed toward the radial inside by the front-end | tip part (inner diameter side edge part) of each of these fixing screws 66a, 66b. .
About another structure and an effect, it is the same as that of the case of the 1st example of the said embodiment, and a 5th example.

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. Further, in the above-described embodiment, the encoder is made of a permanent magnet, and a structure that adopts a configuration in which N poles and S poles are alternately arranged in the circumferential direction on the detected surface of the encoder has been described as an example. However, the encoder is made of a simple magnetic material, and the detection surface of the encoder is provided with a solid portion such as a convex portion, a tongue piece, or a column portion, and a thinned portion such as a concave portion, a notch, or a through hole, A configuration in which they are alternately arranged in the circumferential direction can also be adopted. When such a configuration is adopted, a permanent magnet is incorporated on the sensor side. Furthermore, the structures of the above-described embodiments and reference examples can be implemented in appropriate combination. For example, the structures of the fifth and sixth examples of the embodiment, the structures of the seventh to ninth examples of the embodiment, and the structures of the first and second examples of the reference example can be implemented in combination. Further, in each example of the embodiment, the case where the ball bearing is used as the rolling bearing for rotatably supporting the torque transmission shaft has been described. However, when the present invention is implemented, the deep groove ball bearing, Conventionally known rolling bearings having various structures such as a tapered roller bearing, a needle bearing, a cylindrical roller bearing, and an angular ball bearing can be used.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Encoder 3 Sensor 4 Harness 5 Rotational transmission 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, 13a Sensor unit 14 Housing 15a, 15b Outer ring 16a, 16b Inner ring 17 Rolling element 18, 18a, 18b, 18c Key engagement part 19, 19a Inner ring side keyway 20, 20a Shaft side keyway 21 Key member 22 Large diameter part 23 Support ring 24 Support ring 25 Encoder body 26 Encoder body 27 First detected surface 28 Second detected surface 29 First sensor 30 Second sensor 31, 31a Small diameter cylindrical portion 32, 32a Large diameter cylindrical portion 33, 33 Annular portion 34a, 34b Bent portion 35 Mounting step 36 First substrate 37 Second substrate 38, 38a, 38b Sensor support Block 39, 39a, 39b, 39c Sensor cap 40a, 40b Detection part 41a, 41b Terminal 42a, 42b Connection member 43a, 43b Mounting part 44 Engagement hole 45 Fixing pin 46 Harness 47 Bottom part 48 Outer cylinder part 49 Annular part 50 Supporting cylinder part 51 Outer ring raceway 52 Shoulder part 53 Fitting step part 54 Harness drawing hole 55 Shaft side convex part 56 Inner ring side convex part 57, 57a, 57b, 57c Key engaging part 58, 58a Outer ring side keyway 59, 59a Housing Side keyway 60, 60a Key member 61 Outer ring side convex part 62 Housing side convex part 63 Outer ring side flat surface part 64 Housing side flat surface part 65a, 65b Screw hole 66a, 66b Fixing screw

Claims (2)

A torque transmission shaft that transmits torque during use;
A rolling bearing for supporting the torque transmission shaft in a rotatable manner with respect to a portion that does not rotate during use,
A pair of encoders that alternately change the characteristics of each detected surface in the circumferential direction and are supported by a member that rotates directly on the torque transmission shaft or in synchronization with the torque transmission shaft when in use;
A pair of sensors supported by a portion that does not rotate even when used in a state in which each detection unit is opposed to the detection surface of each encoder.
A rotation transmission device with a torque measuring device ,
Between the front Symbol fitted to the inner ring and wheel among a rotating ring constituting the rolling bearing fixed the torque transmission shaft, inner detent for preventing that the inner ring and the torque transmission shaft rotates relatively mechanism is provided with,
Of the two encoders, at least one encoder is internally fitted and fixed to a portion of the inner peripheral surface of the inner ring that is axially disengaged from the inner detent mechanism.
A rotation transmission device with a torque measuring device characterized by the above. A torque transmission shaft that transmits torque during use;
A rolling bearing for supporting the torque transmission shaft in a rotatable manner with respect to a portion that does not rotate during use,
A pair of encoders that alternately change the characteristics of each detected surface in the circumferential direction and are respectively supported directly or indirectly via other members at two positions separated in the axial direction of the torque transmission shaft When,
A pair of sensors supported by a portion that does not rotate even when used in a state in which each detection unit is opposed to the detection surface of each encoder.
A rotation transmission device with a torque measuring device ,
Between the front Symbol stationary ring in which the outer ring and the fixed the rotating parts not fitted in the outer ring which constitutes the rolling bearing, for preventing that the part which does not rotate with the outer ring are relatively rotated, keyways and said key is constituted by a key which is pressed into the groove, is provided with an outer detent mechanism,
Of the two sensors, at least one of the sensors is supported by the outer ring and disposed adjacent to the outer ring, and the detection unit is a rotating wheel that constitutes the rolling bearing of the two encoders. It is fitted and fixed to the inner peripheral surface of the inner ring and is opposed to the detected surface of the encoder disposed adjacent to the inner ring.
A rotation transmission device with a torque measuring device characterized by the above.

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