JP2015090340A - Rotary transmission device attached with torque measurement device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable sufficient improvement of resolving power of measurement by a structure in which torque of a rotary shaft is measured on the basis of measurement of a torsional amount of the rotary shaft by a pair of encoders and a pair of sensors, and to further attain a structure capable of supporting both of the sensors at one part.SOLUTION: A target rotary shaft is determined to be a rotary shaft unit 6 that is formed by coupling a hollow input shaft 13 having an input gear 7 fixed and a hollow output shaft 14 having an output gear 8 fixed with a torsion bar 15 arranged on an inner diameter side of both shafts 13 and 14. Further, a first encoder 10 supportedly fixed at a part which is rotated together with the input shaft 13 and a second encoder 11 supportedly fixed at a part which is rotated together with the output shaft 14 are arranged in close proximity to each other. In a state where detection parts of a pair of sensors 42a and 42b held in one sensor unit 12 are directed to detected parts of both of the encoders 10 and 11, the sensor unit 12 is supported by a housing.

Description

  The present invention relates to an improvement in a rotation transmission device with a torque measuring device that is incorporated in, for example, an automatic transmission for automobiles, transmits torque by a rotating shaft, and is used for measuring torque transmitted by the rotating shaft.

  Conventionally, in order to appropriately perform the shift control of the automobile automatic transmission, the rotational speed of the rotating shaft constituting the automotive automatic transmission and the torque transmitted by the rotating shaft are measured, and the measurement result Is used as information for performing the shift control. On the other hand, as a device that can be used for measuring the torque, the amount of elastic torsional deformation of the rotating shaft transmitting torque is converted into a phase difference between the output signals of a pair of sensors. An apparatus for measuring the torque based on the above is known (for example, see Patent Document 1). Such a conventional structure will be briefly described below with reference to FIG.

  In the first example of the conventional structure shown in FIG. 53, a pair of encoders 2 and 2 are externally fitted and fixed at two positions in the axial direction of the target rotating shaft 1. The magnetic characteristics of 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. In addition, the pitches at which the magnetic properties of the outer peripheral surfaces change in the circumferential direction are equal to each other on the outer peripheral surfaces. In addition, the 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 outer peripheral 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 rotating shaft 1. The frequency (and period) of this change takes a value commensurate with the rotational speed of the rotary shaft 1. For this reason, the said rotational speed is calculated | required based on this frequency (or period). When the rotary shaft 1 is elastically twisted and deformed as torque is transmitted by the rotary 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 (elastic torsional deformation amount of the rotating shaft 1). Therefore, the torque can be obtained based on this phase difference ratio.

  However, when the first example of the conventional structure as described above is incorporated and used in an automatic transmission for an automobile, the torsional rigidity of the rotating shaft 1 to be measured is high. There is a problem that it is difficult to ensure a sufficient amount of torsional deformation and the resolution of torque measurement is lowered. Further, since the two sensors 3 and 3 that are spaced apart in the axial direction are used, there is a problem that it is difficult to dispose the two harnesses 4 and 4 drawn from both the sensors 3 and 3. . Further, since it is necessary to provide support and fixing portions for each of the sensors 3 and 3 in the housing in a highly accurate relative positional relationship, there is a problem that processing of the housing becomes difficult.

  On the other hand, in Patent Document 1, as shown in FIG. 54, the detected portions of a pair of encoders 2a and 2a fixed at two positions in the axial direction of the rotating shaft 1 are extended toward the central portion in the axial direction. In addition, there is described a structure in which the detection portions of a pair of sensors constituting one sensor unit 5 arranged in the central portion in the axial direction are opposed to the detection portions of the encoders 2a and 2a. However, also in the case of this second example of the conventional structure, when it is incorporated in an automatic transmission for an automobile, the torsional rigidity of the target rotating shaft 1 is high, so that the torsional deformation of the rotating shaft 1 is elastic. It is difficult to secure a sufficient amount. Therefore, even with the above-described second example of the conventional structure, the problem that the resolution of torque measurement is low cannot be solved.

  In Patent Document 2, a pair of rotating shafts each having an encoder fixed to each outer peripheral surface are arranged on the same straight line, and the ends of both rotating shafts are more elastic than the two rotating shafts. A structure in which both ends of a torsion bar that is easily twisted is connected is described. In the case of the third example of the conventional structure described in Patent Document 2, the relative displacement amount in the rotational direction of both encoders can be increased based on the elastic torsional deformation of the torsion bar that occurs during torque transmission. . For this reason, the resolution of torque measurement can be improved accordingly. However, when the third example of such a conventional structure is applied to a counter shaft of an automobile automatic transmission, it is difficult to sufficiently improve the resolution of torque measurement. That is, the input gear and the output gear are fixed at two positions in the axial direction of the counter shaft, and the portion of the counter shaft that is elastically torsionally deformed when torque is transmitted is between the two gears. Only the part between. For this reason, when the third example of the conventional structure as described above is applied to such a countershaft, the torsion bar needs to be installed between the two gears. Therefore, the axial dimension of the torsion bar is equal to or smaller than the axial distance between the two gears. However, in the case of the countershaft, since the axial distance between these two gears is narrow, the axial dimension of the torsion bar cannot be made sufficiently long. Therefore, it is not possible to secure a sufficient amount of elastic torsional deformation of the torsion bar that occurs when torque is transmitted. As a result, it is difficult to sufficiently improve the resolution of torque measurement.

JP-A-1-254826 Japanese Utility Model Publication No. 217311

  In view of the circumstances as described above, the present invention can measure the transmission torque using a pair of encoders and a sensor unit, and regardless of whether the axial distance between the pair of gears is wide or narrow. The invention was invented to realize a structure capable of increasing the resolution of torque measurement.

Each of the rotation transmission devices with a torque measuring device according to the present invention includes a housing, a rotary shaft unit, a first gear, a second gear, a first encoder, a second encoder, and one sensor unit. .
Among these, the rotating shaft unit includes both hollow first and second rotating shafts and a torsion bar. Of these, the first and second rotating shafts are arranged concentrically with each other, and are rotatably supported by the housing in a state where their one end portions are combined so as to be relatively rotatable. The torsion bar is arranged on the inner diameter side of the first and second rotary shafts, concentrically with the first and second rotary shafts, and one end portion of the first and second rotary shafts is used as the first rotary shaft. The other end is connected to the second rotation shaft among them so that they cannot rotate relative to each other.
The first gear is fixed to an intermediate portion in the axial direction of the outer peripheral surface of the first rotating shaft.
The second gear is fixed to an intermediate portion in the axial direction of the outer peripheral surface of the second rotating shaft.
The first and second gears, which are made separately from the first and second rotary shafts, may be coupled and fixed to the axial intermediate portion of the outer peripheral surface of each rotary shaft. Alternatively, they may be integrally formed in the axially intermediate portion of the outer peripheral surface of each of these rotary shafts.
The first encoder is fixed to a portion that rotates together with either one of the first and second rotating shafts, and is concentric with the one rotating shaft and has an annular first shape. While having a to-be-detected part, the magnetic characteristic of this 1st to-be-detected part is changed by the equal pitch alternately with respect to the circumferential direction.
In addition, the second encoder is fixed to a portion that rotates together with the other rotary shaft of the two rotary shafts, and has an annular second detected portion that is concentric with the other rotary shaft, The magnetic characteristics of the second detected portion are changed alternately and at equal pitches in the circumferential direction.
Each of the first and second encoders may be supported and fixed to these parts separately from the parts that rotate together with the rotary shafts, or may be formed integrally with these parts. You may do it.
The first and second detected parts are arranged close to each other (for example, arranged with an interval of 10 mm or less, more preferably 5 mm or less).
The sensor unit is supported by the housing in a state where a part of the sensor unit is opposed to the first and second detected parts, and of the first and second detected parts. The output signal is changed in response to the change in the magnetic characteristics of the part facing itself.

  Particularly, in the case of the rotation transmitting device with a torque measuring device according to claim 1, the torsion bar is hollow. In addition, a connecting shaft is provided separately from each member described above. The connecting shaft is disposed on the inner diameter side of the torsion bar, concentrically with the torsion bar, and has one end portion which is not rotatable relative to one of the first and second rotating shafts. In the connected state, the other end is projected in the axial direction from the other rotating shaft and the end of the torsion bar. The first encoder is fixed to the other end of the connecting shaft, and the first detected portion is concentric with the connecting shaft. The second encoder is fixed to the other end of the other rotating shaft, and the second detected portion is concentric with the other rotating shaft.

  On the other hand, in the case of the rotation transmission device with a torque measuring device according to claim 2, the first encoder is disposed at a position sandwiched between the first and second gears in the axial direction. The first rotation axis is fixed, and the first detected portion is concentric with the first rotation axis. The second encoder is disposed at a position sandwiched between the first and second gears in the axial direction and supported and fixed to the second rotating shaft. The detected part is concentric with the second rotation axis.

  When the rotation transmission device with a torque measuring device of the present invention as described above is implemented, preferably, as shown in the third aspect of the present invention, it is shown by the arrow in FIG. 55 at the axially intermediate portion of the torsion bar. A portion that is elastically twisted and deformed when torque is transmitted through a transmission path (a portion of the torsion bar that is sandwiched between both ends connected to the first and second rotating shafts so as not to rotate relative to each other. ) Is made larger than the axial distance between the two gears. Further, the transmission path is longer than the conventional one, and the torque resolution is improved.

Further, when carrying out the present invention, for example, it can be employed the following configuration C _1. This case of employing the configuration C _1, the first, the end portions of the second double rotary shaft, combined while preventing the direction of displacement of mutually approach each other in the axial direction. Each of the first and second gears is a helical gear. Further, the direction of inclination of the teeth of both gears is determined when the two gears are rotated forward (when rotating in the rotational direction that is frequently performed during use, for example, when the vehicle is moving forward). The axial reaction force acting on these two gears is regulated so as to be in the direction in which they face each other (press each other).

Further, when carrying out the present invention, for example, it can be employed the following configuration C _2. When employing this configuration C ₂ has a first combined cylindrical portion provided at one end portion of the first rotation axis, of the second combined cylindrical portion provided at one end portion of the second rotary shaft Any one of the combination cylinder portions is inserted into the inner diameter side of the other combination cylinder portion. Further, a radial bearing (radial rolling bearing or radial sliding bearing) is installed between the circumferential surfaces facing each other of the combination cylinder portions, and the base end of the outer peripheral surface of the one combination cylinder portion. A thrust bearing (a thrust rolling bearing or a thrust sliding bearing) is installed between the step surface provided in the portion and the tip surface of the other combination cylinder portion.
In this case, for example, an annular thrust washer sandwiched between the step surface and the tip surface can be used as the thrust sliding bearing. In this case, for example, it can be employed the following configuration C _3. When employing this configuration C _3, the (preferably equally spaced plural locations) circumferentially 1 or a plurality of locations of the thrust washer, the radial direction on both sides between part of said stepped surface and the tip surface A thinning portion is formed which communicates a pair of spaces existing at the sandwiched positions. As the thinning portion, for example, a slit or a through hole provided in a state where both side surfaces of the thrust washer communicate with each other, a concave groove provided on at least one side surface of the thrust washer, or the like can be employed.
Further, as the thrust sliding bearing, when using a thrust washer, such as described above, for example, can be employed the following configuration C _4. This case of employing the configuration C _4, the outer peripheral edge of the thrust washer, to protrude radially outward from between portions of said stepped surface and the tip surface. At the same time, a reinforcing cylindrical portion is provided around the entire outer periphery.

Further, when carrying out the present invention, for example, it can be employed the following configuration C _5. When employing this configuration C ₅ is at one end an outer circumferential surface of the torsion bar, the first male spline portion having a first plating layer on the surface portion, the inner peripheral surface of the first rotation axis, the A first female spline portion that can be engaged with the first male spline portion is provided. Among these, the metal which comprises the 1st plating layer shall be a softer metal than each metal which comprises the said torsion bar and said 1st rotating shaft. Then, the first male spline portion is press-fitted into the first female spline portion with a tightening margin smaller than a thickness dimension in a free state (a state where no external force is applied) of the first plating layer. , Engage with each other without rattling in the circumferential direction. At the same time, a second male spline portion having a second plating layer on the outer surface of the other end portion of the torsion bar is associated with the second male spline portion on the inner peripheral surface of the second rotating shaft. A second female spline portion that can be combined is provided. Among these, the metal which comprises the 2nd plating layer shall be a softer metal than each metal which comprises the said torsion bar and said 2nd rotating shaft. Then, the second male spline part is pressed into the second female spline part with a tightening margin smaller than the thickness dimension in the free state of the second plating layer, thereby preventing looseness in the circumferential direction. Combine.
Further, in this case, for example, it can be employed the following configuration C _6. When employing this configuration C _6, the first, the metal constituting the second double-plating layer, a copper or nickel.

Further, when carrying out the present invention, for example, it can be employed the following configuration C _7. This case of employing the configuration C ₇ is an end portion of the connecting shaft, the first, fitted to fix the inner by interference fit on the inner peripheral surface of one of the rotation axis of the second double rotary shaft.

  In carrying out the present invention, for example, as in the fourth aspect of the present invention, the rotary shaft unit is rotatably supported on the housing by a plurality of rolling bearings. In this case, an inner ring constituting at least one of the rolling bearings can be integrally formed with the first rotating shaft or the second rotating shaft.

  Further, when carrying out the present invention, for example, as in the invention described in claim 5, the sensor unit includes a first sensor opposed to the first detected part and a second detected part. A device provided with a second sensor facing each other is used. These first and second sensors generate output signals that change in response to changes in the magnetic characteristics of the portions of the first and second detected parts facing each other.

  Moreover, when implementing this invention, the structure of the invention described in Claim 6 can be employ | adopted, for example. When this configuration is employed, the first and second encoders are each made of a magnetic material. Further, it is assumed that the first and second detected parts are arranged such that the thinned parts and the full parts are alternately arranged at equal pitches in the circumferential direction. And these both to-be-detected parts are piled up in the radial direction or the axial direction in a state in which they are close to each other. In addition, as a combination of the said thinning part and a full part, the combination of a recessed part and a convex part, the combination of a notch and a tongue piece, the combination of a through-hole and a column part, etc. are employable. The sensor unit includes a stator made of a magnetic material and a plurality of coils made of one conductor, and outputs an output current or output voltage of the conductor in a state where a drive voltage is applied to the conductor. The signal used is used. Each of the stators is long in the overlapping direction of the two detected parts, and the respective front ends thereof are opposed to the two detected parts from one side in the overlapping direction of the two detected parts. A plurality of core portions arranged at equal pitches with respect to the direction, and an annular rim portion that connects the base end portions of these core portions. In addition, the coils are fitted (wound) one by one to the cores, and the winding directions of the coils adjacent in the circumferential direction are opposite to each other.

  Moreover, when implementing this invention, the structure of the invention described, for example in Claim 7 is employable. When this configuration is employed, the first and second encoders are each made of a magnetic material. Further, it is assumed that the first and second detected parts are arranged such that the thinned parts and the full parts are alternately arranged at equal pitches in the circumferential direction. Then, the solid portion constituting the first detected portion and the solid portion constituting the second detected portion are alternately arranged in the circumferential direction with a circumferential gap interposed therebetween. In addition, as a combination of the said thinning part and a full part, the combination of a recessed part and a convex part, the combination of a notch and a tongue piece, the combination of a through-hole and a column part, etc. are employable. In addition, as the sensor unit, a sensor unit having one sensor facing the portions where the solid portions of the detected portions are alternately arranged is used. This sensor generates an output signal that changes in response to a change in the magnetic characteristics of a portion of the portion where the enhancement portions of the detected portions are alternately arranged.

  Moreover, when implementing this invention, the structure of the invention described, for example in Claim 8 is employable. When adopting this configuration, the first and second detected parts are a pair of cylindrical surfaces opposed to each other in the radial direction or a pair of annular surfaces opposed to each other in the axial direction. Suppose that the S pole and the N pole are alternately arranged at equal pitches in the circumferential direction. Further, as the sensor unit, a sensor unit provided with a magnetic detection element or a coil disposed between the detected parts is used. The output voltage or output current of the magnetic detection element or the output voltage or output current of the coil is used as an output signal.

  In the case of the rotation transmission device with a torque measuring device of the present invention configured as described above, the output signal of the sensor unit is output together with the first and second encoders (first and second rotation shafts) together with the rotation shaft unit (first and second rotation shafts). The second both detected parts) change corresponding to the rotational speed based on the rotation. Therefore, if necessary, the rotation speed can be measured based on the output signal of the sensor unit. In addition, when the torque is transmitted between the first and second gears by the rotary shaft unit, the first, The second gears (the first and second rotating shafts, the first and second encoders) are relatively displaced in the rotational direction. As a result of the relative displacement of the first and second encoders in the rotational direction in this way, the output signal of the sensor unit changes corresponding to the amount of relative displacement (the magnitude of the torque). Therefore, the torque can be measured based on the output signal of the sensor unit.

  In particular, in the case of the present invention, the first rotation shaft having the first gear fixed to the axial intermediate portion of the outer peripheral surface and the second rotation having the second gear fixed to the axial intermediate portion of the outer peripheral surface. Each of the shafts is formed in a hollow shape, and the torsion bar whose both ends are connected to the two rotation shafts so as not to rotate relative to the two rotation shafts is disposed on the inner diameter side of the two rotation shafts. For this reason, the axial direction dimension of the axial direction intermediate part of this torsion bar can be made larger than the axial direction space | interval of said both gears like the invention described in Claim 3, for example. Therefore, it is possible to sufficiently secure the amount of elastic torsional deformation of the intermediate portion in the axial direction of the torsion bar that occurs when torque is transmitted. As a result, in the case of the present invention, unlike the structure in which the rotary shaft unit is an integral rotary shaft, both the gears are generated when the torque is transmitted, regardless of whether the axial distance between the two gears is wide or narrow. The relative displacement amount in the rotation direction between the two rotation shafts and the two encoders can be sufficiently increased. Therefore, the resolution of torque measurement can be sufficiently increased.

  In the case of the present invention, the torsional rigidity of the axially intermediate portion can be easily adjusted by adjusting the diameter and axial dimensions of the axially intermediate portion of the torsion bar at the design stage. For this reason, the relationship (gain) between the torque and the relative displacement in the rotational direction between the first and second encoders is designed in a systematic manner compared to a structure in which the rotary shaft unit is an integral rotary shaft. Easy to do.

  In the case of the present invention, since one sensor unit can be used, the number of harnesses drawn from the sensor unit can be reduced to one, and the harness can be easily arranged. In addition, the sensor unit provided in the housing needs only one support and fixing portion, so that the processing of the housing can be facilitated.

Further, when practicing the present invention, when adopting the configuration C _1, the first, during forward rotation of the second double gear, the axial direction of the gear reaction force acting on the both gears, at least a portion Can be offset. For this reason, during the forward rotation of the two gears, the axial load applied to the rolling bearings supporting the first and second rotating shafts can be suppressed, and the friction loss of these rolling bearings can be suppressed accordingly.

Further, when the configuration C ₂ is adopted and the configuration C ₃ is adopted, a space sandwiched between a pair of peripheral surfaces, which is a space where a radial bearing is installed, and a thrust washer are provided. Lubricating oil can be circulated efficiently in the space between the stepped surface and the tip surface, which is the installed space.
That is, since the space where the radial bearing is installed and the space where the thrust washer is installed are connected to each other, the lubricating oil can be supplied to both the spaces from either side. However, even when lubricating oil is supplied from any space side, if both side surfaces of the thrust washer are in contact with the entire circumference of the step surface and the tip surface, the lubricating oil is It becomes difficult to pass through the space where the washer is installed. As a result, the lubricating oil cannot be efficiently circulated through both the spaces.
In contrast, in the case of the invention employing the configuration C _3, the spatial between the pair at the position sandwiching the space that installing the thrust washer from both sides in the radial direction is circumferentially 1 of the thrust washer Or it communicates through the thinning part formed in several places. For this reason, the lubricating oil can easily pass through the space where the thrust washer is installed through the thinning portion. As a result, even when lubricating oil is supplied from any one of the space in which the radial bearing is installed and the space in which the thrust washer is installed, the lubricating oil can be efficiently circulated through these two spaces. Accordingly, the lubrication state of the radial bearing and the thrust washer installed in both the spaces can be improved.
Further, when adopting the structure C _3, by adopting the configuration C _4, it is possible to enhance the strength of the outer peripheral portion of the thrust washer.

Further, by adopting the configuration C _5, the engaging portion between the first male spline section and the first female spline portion, and the engagement portion of the second male spline section and the second female spline portion, the circumferential respectively It becomes an engaging part which does not produce shakiness of a direction. For this reason, when the rotation direction of the rotation shaft on the torque input side of the first and second rotation shafts is reversed, the both engagement portions have a gap in the circumferential direction that causes backlash. Relative rotation can be prevented. As a result, it is possible to prevent the inconvenience that the minute torque cannot be accurately measured based on the occurrence of such relative rotation.
Further, in the case of employing the configuration C _5, wherein the first, the second two great men spline portion first, when pressed into second double female spline portion, deformation of the interference content of the (elastic deformation or plastic deformation) Most of them occur in both the relatively soft first and second plating layers. For this reason, it is possible to efficiently fill (eliminate) the circumferential gap that causes the rattling of the both engaging portions with the first and second plating layers. At the same time, the deformation of the metal constituting the first and second plating layers is generated with a smaller force than the deformation of the metal constituting the main body portion of each involute spline part, so that the force required for press-fitting can be reduced. .
Further, when adopting the configuration C _5, wherein by employing a configuration C _6, the first, can be appropriately the values of hardness and crush resistance of the second double-plating layer.

Further, by adopting the configuration C _7, one end of the first connecting shaft, can simplify the structure of a portion for relatively non-rotatably coupled on either one of the rotation axis of the second double rotary shaft, its The manufacturing cost can be reduced.

  Further, if the configuration of the invention described in claim 4 is adopted, the structure can be simplified and the cost can be reduced along with the reduction of the number of parts.

The perspective view which abbreviate | omits a housing and a sensor and shows the 1st example of embodiment of this invention. The side view which abbreviate | omits a housing and shows. The figure which abbreviate | omitted the sensor unit and was seen from the left side of FIG. The figure seen from the right side of FIG. The disassembled perspective view which abbreviate | omits and shows a housing and a sensor. FIG. 4 is a cross-sectional view taken along the line aa in FIG. 3. The left end part enlarged view of FIG. The b section enlarged view of FIG. The figure which looked at the circumference direction part of the 1st, 2nd to-be-detected part from the outer diameter side. The expanded sectional view of the opposing part of a sensor unit and both 1st, 2nd encoders. The perspective view which shows three examples of a thrust washer. The figure similar to FIG. 9 which shows the 2nd example of embodiment of this invention. Similarly, the same figure as FIG. The figure which shows the 3rd example of embodiment of this invention which looked at the 1st encoder from the left side of FIG. 6 (A), and the figure which looked at the 2nd encoder from the left side of FIG. 6 (B). The fragmentary sectional view shown in the state which couple | bonded the 1st, 2nd encoder with the pin. The perspective view of both the 1st and 2nd encoder which shows the 4th example of embodiment of this invention. The figure which shows the 5th example from the left side of FIG. 6 and the 2nd encoder which looked at the 1st encoder from the left side of FIG. 6 (B). The expanded sectional view of the circumferential direction part of the involute spline engaging part of a torsion bar and an input shaft (or output shaft) showing the sixth example. The same figure as FIG. 18 shown in the state before providing a plating layer in the surface layer part of a male involute spline part. The diagram which shows the relationship between a sensor output and transmission torque. The expanded sectional view equivalent to the right end part of Drawing 6 showing the 7th example of an embodiment of the invention. The expansion perspective view of the one end part of a connecting shaft. The figure similar to FIG. 6 which shows the 8th example of embodiment of this invention. The partial expanded sectional view similar to FIG. 7 which shows the 9th example. The figure seen from the left of FIG. Cc sectional drawing of FIG. The disassembled perspective view of both a 1st, 2nd encoder and a sensor unit. FIG. 25 shows a part in the circumferential direction in a state (A) when torque is not transmitted and a state (B) when torque is transmitted, and a diagram (C) showing the output signal of the sensor unit in each of these states ). The partial expanded sectional view similar to FIG. 7 which shows the 10th example of embodiment of this invention. The figure which took out only the 1st and 2nd both encoders, and was seen from the outer diameter side. The figure which abbreviate | omitted the sensor unit and was seen from the left side of FIG. FIG. 3 is an exploded perspective view of both first and second encoders. The diagram which shows the output signal of a sensor unit with the state (A) at the time of non-transmission of torque, and the state (B) at the time of transmission. The diagram which shows the relationship between duty ratio (epsilon) of an output signal of a sensor, and torque. The partial expanded sectional view similar to FIG. 7 which shows the 11th example of embodiment of this invention. The figure seen from the left of FIG. FIG. 3 is an exploded perspective view of both first and second encoders. The partial expanded sectional view similar to FIG. 7 which shows the 12th example of embodiment of this invention. The figure seen from the left side of FIG. The schematic diagram which shows the positional relationship of the magnetic pole of a 1st and 2nd to-be-detected part and the detection part of a sensor with the state (A) at the time of non-transmission of a torque, and the state (B) at the time of transmission. The diagram which shows the output signal of a sensor unit. FIG. 14 is a schematic cross-sectional view showing a thirteenth example of embodiment of the present invention. A schematic sectional view showing the 14th example. A schematic sectional view showing the 15th example. A schematic sectional view showing the 16th example. A schematic sectional view showing the 17th example. The side view which shows the 18th example. FIG. 48 is a sectional view taken along line dd in FIG. 47. Ee sectional drawing. Ff sectional drawing of FIG. The figure similar to FIG. 8 which shows the 19th example of embodiment of this invention. The figure similar to FIG. 8 which shows the 20th example. The schematic side view which shows the 1st example of a conventional structure. The schematic side view which cuts a part and shows the 2nd example. The figure which simplified FIG. 6 and showed the torque transmission path | route.

[First example of embodiment]
FIGS. 1-11 has shown the 1st example of embodiment of this invention corresponding to Claim 1,3,5. The rotation transmission device with a torque measuring device of this example is equipped with a so-called transverse engine (transverse engine) such as a front wheel drive vehicle or a four wheel drive vehicle adopting a prime mover and transmission arrangement similar to the front wheel drive vehicle. Used in the counter shaft and counter gear portion of an automatic transmission for automobiles. Such a rotation transmission device with a torque measuring device of this example includes a housing (mission case) (not shown), a rotary shaft unit 6 that functions as a counter shaft, and an input gear that is a first gear that functions as a counter gear. 7 and an output gear 8 that is a second gear, a connecting shaft 9, a first encoder 10, a second encoder 11, and one sensor unit 12.

  Among these, the rotating shaft unit 6 includes an input shaft 13 that is a hollow first rotating shaft, an output shaft 14 that is a hollow second rotating shaft, and a hollow torsion bar 15. Of these, the input shaft 13 and the output shaft 14 are each made of steel in a cylindrical shape, are arranged concentrically with each other, and are combined with each other so as to be relatively rotatable. In addition, regarding each of the input shaft 13 and the output shaft 14, one end portion refers to an end portion on a side close to each other, and the other end portion refers to an end portion on a side far from each other. In the case of this example, in order to combine the end portions of the input shaft 13 and the output shaft 14 so that they can rotate relative to each other, one end portion of the input shaft 13 is a first combination cylinder portion. A small-diameter input-side combination cylinder portion 16 is provided, and a relatively large-diameter output-side combination cylinder portion 17, which is a second combination cylinder portion, is provided at one end portion of the output shaft 14. The input side combination cylinder part 16 is inserted into the inner diameter side of the output side combination cylinder part 17. In this state, a radial needle bearing 18 is installed between the cylindrical peripheral surfaces of the combination cylinder portions 16 and 17 facing each other. At the same time, a circular slide bearing is provided between the stepped surface 19 provided at the base end portion of the outer peripheral surface of the input side combination cylinder portion 16 and the distal end surface 20 of the output side combination cylinder portion 17. An annular thrust washer 21 is sandwiched. Further, by adopting such a configuration, the one end portions of the input shaft 13 and the output shaft 14 are combined in a state in which relative displacement is possible and displacement in a direction approaching each other in the axial direction is prevented. ing.

  In the case of this example, the thrust washer 21 is, as shown in detail in FIG. 11 (A), a plurality of parts at equal intervals in the circumferential direction of the annular body part, each of which is a thinning part. The slits 22 and 22 which are long in the radial direction are formed so as to open at the inner peripheral edge of the main body portion. At the same time, a reinforcing cylindrical portion 23 bent at a right angle in the axial direction from the outer peripheral edge is provided around the entire outer periphery of the main body portion. Such a thrust washer 21 is large in the radial direction at the proximal end portion of the input side combination cylinder portion 16 with the distal end edge of the cylindrical portion for reinforcement 23 facing the other end side of the input shaft 13. It is fitted externally without rattling. At the same time, the intermediate portion in the radial direction of the main body is sandwiched between the step surface 19 and the tip surface 20. Further, in this state, each of the slits 22 and 22 communicates with a pair of spaces existing at positions sandwiching the portion between the step surface 19 and the tip surface 20 from both radial sides. That is, in order to realize such a communication state, the diameter of the inscribed circle of each of the slits 22 and 22 (inner diameter of the main body portion) is made smaller than the diameter of the inner peripheral edge of the tip surface 20, and The diameter of the circumscribed circle of the slits 22 and 22 is made larger than the diameter of the outer peripheral edge of the distal end surface 20.

  The torsion bar 15 is made of an alloy steel such as carbon steel in a circular tube shape, and is arranged concentrically with the input shaft 13 and the output shaft 14 on the inner diameter side of the input shaft 13 and the output shaft 14. ing. In this state, the torsion bar 15 has one end (the right end in FIGS. 5 to 6) on the input shaft 13 and the other end (the left end in FIGS. 5 to 6) on the output shaft 14. They are connected so that they cannot rotate relative to each other. In order to realize such a connected state, in the case of this example, the outer diameter of the torsion bar 15 is slightly increased at both ends compared to the intermediate portion, and the outer peripheral surfaces of these both ends are Each of them is engaged with a portion near the other end of the inner peripheral surface of the input shaft 13 and a portion near the other end of the inner peripheral surface of the output shaft 14 so as not to be relatively rotatable. Specifically, these both engaging portions are involute spline engaging portions 24a and 24b (engaging portions formed by engaging both male and female involute spline portions without rattling in the circumferential direction). That is, the first female involute spline portion 62 which is the first male spline portion provided on the outer peripheral surface of the one end portion of the torsion bar 15 is the first female spline portion provided on the inner peripheral surface of the other half portion of the input shaft 13. The involute spline engaging portion 24a is configured by engaging the first female involute spline portion 63 without rattling in the circumferential direction. At the same time, a second male involute spline portion 64, which is a second male spline portion provided on the outer peripheral surface of the other end portion of the torsion bar 15, is provided on the inner peripheral surface of the other end portion of the output shaft 14. The involute spline engaging portion 24b is configured by engaging with the second female involute spline portion 65, which is, without rattling in the circumferential direction. Note that an engaging portion having another rotation preventing structure such as a key engaging portion can be adopted as both engaging portions. In this state, the torsion bar 15 is clamped from both sides in the axial direction by a pair of retaining rings 25a and 25b locked to the inner peripheral surfaces of the input shaft 13 and the output shaft 14. The axial displacement of is prevented. In the case of this example, a portion that is elastically twisted and deformed when torque is transmitted at the intermediate portion in the axial direction of the torsion bar 15 (a portion sandwiched between the involute spline engaging portions 24a and 24b). ) Is larger than the axial distance W between the input gear 7 and the output gear 8 described below (L> W) (in the example shown, L is slightly larger than four times W). )

  The input gear 7 is a helical gear made of alloy steel such as carbon steel, and is externally fixed to the intermediate portion of the input shaft 13. The fitting portion between the inner peripheral surface of the input gear 7 and the outer peripheral surface of the input shaft 13 is a cylindrical surface fitting portion 26a for ensuring concentricity (both outer diameter side and inner diameter side cylindrical surfaces are press-fitted together. And an involute spline engaging portion 24c for preventing relative rotation are disposed adjacent to each other in the axial direction. Further, the positioning of the input gear 7 in the axial direction with respect to the input shaft 13 is performed on one side surface of the input gear 7 (FIG. 1, FIG. 1) on a stepped surface 27 formed near the one end of the intermediate portion of the outer peripheral surface of the input shaft 13. This is achieved by bringing the inner peripheral portion of the left side surface of 2, 5, 6 into contact with each other. In the case of this example, a parking lock gear 28 is integrally formed on the inner peripheral portion of one side surface of the input gear 7. At the time of parking lock, the rotation shaft unit 6 cannot be rotated by engaging a tip portion of a lock member (not shown) with a part of the outer peripheral surface of the parking lock gear 28 in the circumferential direction. The output gear 8 is a helical gear made of alloy steel such as carbon steel, and is formed (fixed) integrally with the output shaft 14 at a portion near one end of the intermediate portion of the outer peripheral surface of the output shaft 14. ing. In the case of this example, when the rotary shaft unit 6 is rotated forward (when the automobile is moving forward), the torque input from the input gear 7 to the input shaft 13 is applied to the torsion bar 15. To the output shaft 14 and output from the output gear 8. At this time, the axially intermediate portion of the torsion bar 15 is elastically twisted and deformed by an amount corresponding to the magnitude of the torque.

  The rotary shaft unit 6 is rotatably supported with respect to the housing by a pair of tapered roller bearings 29a and 29b arranged so that their contact angles are opposite to each other. In the case of this example, in order to assemble these tapered roller bearings 29 a and 29 b to the rotary shaft unit 6, an inner ring 30 a constituting one tapered roller bearing 29 a is attached to a portion near the other end of the input shaft 13. It is fitted. At the same time, a spacer 31 is sandwiched between the large-diameter side end surface of the inner ring 30 a and the other side surface of the input gear 7. In this state, the inner ring 30a is pressed against the input shaft 13 by pressing the small-diameter side end surface of the inner ring 30a with a nut 32a that is screwed into the other end portion of the outer peripheral surface of the input shaft 13 and further tightened. 30a and the input gear 7 are coupled and fixed. Further, the inner ring 30b constituting the other tapered roller bearing 29b is externally fitted to the portion near the other end of the output shaft 14, and the large-diameter side end surface of the inner ring 30b is connected to the outer peripheral surface of the output shaft 14. It is made to contact | abut on the level | step difference surface 33 formed in the edge side part. In this state, the nut 32b screwed to the other end portion of the outer peripheral surface of the output shaft 14 and further tightened presses the end surface on the small diameter side of the inner ring 30b, and the inner ring 30b is supported and fixed to the output shaft 14. doing.

  Further, in the case of this example, the tooth inclination directions of the input gear 7 and the output gear 8 are helical gears, respectively. In the forward rotation), the axial gear reaction forces acting on the gears 7 and 8 are regulated so as to face each other (press each other). Thereby, at the time of forward rotation of the two gears 7 and 8, at least a part of the axial reaction force acting on the two gears 7 and 8 can be canceled. As a result, the axial load applied to the tapered roller bearings 29a and 29b during the forward rotation of the gears 7 and 8 is suppressed, and the friction loss (dynamic torque) of the bearings 29a and 29b is correspondingly reduced. I try to suppress it.

  The connecting shaft 9 is arranged on the inner diameter side of the torsion bar 15 concentrically with the torsion bar 15. At the same time, the connecting shaft 9 has one end portion (the right end portion in FIG. 6) connected to the input shaft 13 in a relatively non-rotatable manner and the other end portion (the left end portion in FIG. 6) connected to the output shaft 14. It protrudes from the other end opening. In the case of this example, in order to connect one end portion of the connecting shaft 9 to the input shaft 13 in such a manner that relative rotation is impossible, the one end portion of the connecting shaft 9 is projected from the one end opening of the torsion bar 15. At the same time, an outward flange-like flange 34 is formed on the outer peripheral surface of the protruding portion. And the outer peripheral surface of this collar part 34 and the inner peripheral surface of the said input shaft 13 are engaged so that relative rotation is impossible. Specifically, this engaging portion is an involute spline engaging portion 24d. In addition, as this engagement part, the engagement part with another rotation prevention structure, such as a key engagement part, can also be employ | adopted. Further, in this state, the collar 34 is clamped from both sides in the axial direction by the retaining ring 25a and another retaining ring 25c that are latched to the inner peripheral surface of the input shaft 13, and the shaft of the connecting shaft 9 Directional displacement is prevented. Note that both female involute spline portions constituting the both involute spline engaging portions 24a and 24d provided at one end portion of the torsion bar 15 and one end portion of the connecting shaft 9 are arranged on the inner periphery of the input shaft 13. It is the thing of the same specification provided mutually in the other half part of the surface. That is, in the case of this example, the first female involute spline portion 63 is shared as both the female involute spline portions.

  The first encoder 10 is fitted and fixed to the other end of the connecting shaft 9 concentrically with the connecting shaft 9. That is, the first encoder 10 is supported and fixed to the input shaft 13 through the connecting shaft 9. For this reason, the first encoder 10 can rotate (synchronously) with the input shaft 13. The second encoder 11 is externally fitted and fixed to the other end of the output shaft 14 concentrically with the output shaft 14. Therefore, the second encoder 11 can rotate (synchronously) with the output shaft 14.

  Further, the first and second encoders 10 and 11 are each made of a magnetic metal and made of an annular cored bar 35 that is externally fitted and fixed to the other end of the connecting shaft 9 or the other end of the output shaft 14. (36) and a cylindrical permanent magnet 37 (38) fixed to the outer peripheral surface of the cylindrical portion existing on the outer peripheral portion of the core bar 35 (36). The outer peripheral surface of the permanent magnet 37 constituting the first encoder 10 is defined as a first detected portion 39, and the outer peripheral surface of the permanent magnet 38 constituting the second encoder 11 is defined as a second detected portion 40. It is said. These first and second detected parts 39 and 40 are equal in diameter, are concentric with each other, and are adjacent to each other in the axial direction (for example, an interval within 10 mm, preferably within 5 mm in the axial direction). Open). Further, as shown in FIG. 9, the S poles and the N poles are alternately arranged at equal pitches in the circumferential direction in both of the detected parts 39 and 40. The total number of magnetic poles (S poles and N poles) of these detected parts 39 and 40 coincides with each other. In this example, the torque is not transmitted, that is, the torsion bar 15 is not elastically twisted and deformed, and the detected parts 39 and 40 are not relatively displaced in the rotational direction. Thus, the circumferential phases of the magnetic poles of the detected parts 39 and 40 coincide with each other as shown in FIG. That is, the same poles of the detected parts 39 and 40 are arranged adjacent to each other in the axial direction. In the case of this example, the cylindrical surface for ensuring concentricity between the inner peripheral surface of the core bar 35 constituting the first encoder 10 and the outer peripheral surface of the other end portion of the connecting shaft 9. The fitting portion 26b and the involute spline engaging portion 24e for preventing relative rotation are arranged adjacent to each other in the axial direction. At the same time, the metal core 35 is prevented from coming off by a retaining ring 25d locked to the outer peripheral surface of the other end of the connecting shaft 9. The core bar 36 constituting the second encoder 11 is externally fixed to the other end portion of the output shaft 14 by an interference fit.

  The sensor unit 12 includes a holder 41 made of synthetic resin, and first and second sensors 42 a and 42 b embedded in the tip of the holder 41. Magnetic detection elements such as a Hall element, a Hall IC, an MR element, and a GMR element are incorporated in the detection portions of both the sensors 42a and 42b. In such a sensor unit 12, the detection part of the first sensor 42a is in close proximity to the first detected part 39 and the detection part of the second sensor 42b is in close proximity to the second detected part 40. And supported by the housing. In particular, in the case of this example, as shown in FIG. 10, in a state where the sensors 42a and 42b are arranged in opposite directions, the detection parts of both the sensors 42a and 42b are used as the detection parts 39 and 40. Are opposed to the same position in the circumferential direction. Accordingly, the phase difference between the output signals of the two sensors 42a and 42b is 180 degrees (the phase difference ratio is 0.5) in a rotation state where the transmission torque is zero.

  In the case of this example, an oil introduction path 43 that opens only at one end surface of the connecting shaft 9 is provided in the central portion in the radial direction of the connecting shaft 9. The lubricating oil introduced into the oil introduction passage 43 is supplied into the tapered roller bearings 29a and 29b through the end opening of the oil introduction passage 43. For this purpose, oil passages 44a and 44b are provided in the portions near both ends of the connecting shaft 9, the torsion bar 15, and the input shaft 13 and the output shaft 14, respectively. And by these both oil paths 44a and 44b, the minute annular space which exists in the inner diameter side of the small diameter side edge part of the inner ring | wheels 30a and 30b of the both tapered roller bearings 29a and 29b of the both ends of the said oil introduction path 43, and the tapered roller bearings 29a and 29b. 45a and 45b are communicated. Further, oil grooves 46a and 46b extending in the radial direction are formed in one or a plurality of circumferential directions on the front end surfaces of the nuts 32a and 32b. As a result, the lubricating oil introduced into the oil introduction passage 43 from the end opening of the oil introduction passage 43 is transferred to the oil passages 44a and 44b, the annular spaces 45a and 45b, and the oil grooves 46a and 46b. And is supplied to the inside of the both tapered roller bearings 29a and 29b.

  Further, in the case of this example, a part of the lubricating oil fed into the both oil passages 44a and 44b is present in the both involute spline engaging portions 24a and 24b from the intermediate portion between the both oil passages 44a and 44b. Through the gap, the gas is fed into a cylindrical space 47 existing between the outer peripheral surface of the intermediate portion of the torsion bar 15 and the inner peripheral surfaces of the intermediate portions of the input shaft 13 and the output shaft 14. And the stepped surface which exists in the base end part of the front end surface 48 of the said input side combination cylinder part 16, and the inner peripheral surface of the said output side combination cylinder part 17 the lubricating oil sent in this cylindrical space 47 49 is supplied to the installation portion of the radial needle bearing 18 and the clamping portion of the thrust washer 21 through a gap existing between them, and the installation portion and the clamping portion are lubricated. At this time, the lubricating oil that has reached the clamping portion passes smoothly through the plurality of slits 22 and 22 provided in the thrust washer 21 while being used for lubrication of the clamping portion. As a result, the lubricating oil is efficiently supplied to the installation portion of the radial needle bearing 18 and the clamping portion of the thrust washer 21, and the lubrication state of the installation portion and the clamping portion is improved.

  In the case of carrying out the present invention, instead of the thrust washer 21 as shown in FIG. 11A, the reinforcing cylindrical portion of the outer peripheral portion as shown in FIG. 11B is omitted. It is also possible to use the thrust washer 21a or a simple annular thrust washer 21b in which the outer peripheral reinforcing cylindrical portion and the plurality of slits are omitted as shown in FIG. However, it is preferable to use the thrust washers 21 and 21a with the slits 22 and 22 shown in (A) and (B) from the viewpoint of improving the lubrication state of the installation part and the clamping part. Furthermore, from the viewpoint of securing the strength of the outer peripheral portion (particularly the vicinity of the base end portion of each of the slits 22 and 22), it is preferable to use the thrust washer 21 with the reinforcing cylindrical portion 23 shown in (A).

  Further, in the case of this example, the lubricating oil fed into the both oil passages 44a, 44b passes from the intermediate portion of both the oil passages 44a, 44b to the inner peripheral surface of the torsion bar 15 and the outer peripheral surface of the connecting shaft 9. Are also fed into a minute gap (cylindrical gap having a radial thickness of about 0.2 mm). In particular, in the case of this example, in order to smoothly feed the lubricating oil into such a minute gap, the both oil passages 44a, Concave grooves 66a and 66b extending around the entire circumference are provided in a portion aligned with 44b. During operation, the lubricating oil filled in the minute gap exhibits a function as a film damper that attenuates minute vibrations of the connecting shaft 9.

  In the case of the rotation transmission device with the torque measuring device of the present example configured as described above, the output signals of the first and second sensors 42a and 42b constituting the sensor unit 12 are output from the rotary shaft unit 6 (the input shaft). 13 and the output shaft 14), and the first and second encoders 10 and 11 rotate, respectively, change periodically. Here, the frequency (and period) of this change takes a value commensurate with the rotational speed of the rotary shaft unit 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 the case of this example, when torque is transmitted between the input gear 7 and the output gear 8 by the rotary shaft unit 6, the axial intermediate portion of the torsion bar 15 is elastically twisted and deformed. As a result, the gears 7 and 8 (the shafts 13 and 14 and the encoders 10 and 11) are relatively displaced in the rotational direction. As a result of the relative displacement of the encoders 10 and 11 in the rotational direction in this way, the phase difference ratio (= phase difference / 1 period) between the output signals of the first and second sensors 42a and 42b. Change. 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.

  In particular, in the case of this example, the input shaft 13 in which the input gear 7 is fixed to the axial intermediate portion of the outer peripheral surface, and the output shaft 14 in which the output gear 8 is fixed to the axial intermediate portion of the outer peripheral surface; The torsion bars 15 having both ends configured to be hollow and connected to the both shafts 13 and 14 so as not to rotate relative to the shafts 13 and 14 are disposed on the inner diameter side of the shafts 13 and 14. For this reason, the axial dimension L of the axially intermediate portion of the torsion bar 15 can be made larger than the axial interval W between the gears 7 and 8 (L> W). Therefore, the amount of elastic torsional deformation at the intermediate portion in the axial direction of the torsion bar 15 that occurs when torque is transmitted can be sufficiently secured. As a result, in the case of this example, unlike the structure in which the rotary shaft unit 6 is an integral rotary shaft, the torque is transmitted when the torque is transmitted regardless of the width W of the two gears 7 and 8 in the axial direction. The relative displacement amount in the rotational direction between the gears 7 and 8 (the shafts 13 and 14 and the encoders 10 and 11) can be sufficiently increased. Therefore, the resolution of torque measurement can be sufficiently increased. In the case of this example, the torsional rigidity of the axially intermediate portion can be easily adjusted by adjusting the radial dimension and axial dimension of the axially intermediate portion of the torsion bar 15 at the design stage. . For this reason, the relationship (gain) between the torque and the relative displacement amount in the rotational direction can be easily designed to a desired value as compared with a structure in which the rotational shaft unit 6 is an integral rotational shaft.

  In the case of this example, since only one sensor unit 12 is used, the number of harnesses (not shown) pulled out from the sensor unit 12 can be reduced to one, and the harness can be easily arranged. Further, since the sensor unit 12 provided on the housing has only one supporting and fixing portion, the processing of the housing can be facilitated.

  In the case of carrying out the present invention, in the first example of the embodiment described above, the detected portions of both the first and second encoders, and the detecting portions of a pair of sensors constituting the sensor unit, It is also possible to adopt a configuration in which the facing direction is changed from the radial direction to the axial direction. In this case, the detected parts of both the first and second encoders are a pair of annular-shaped detected parts having different diameters, and both the detected parts are set in the same direction with respect to the axial direction. In such a state, they are arranged concentrically with each other (superposed in the radial direction). And the detection part of a pair of sensor which comprises a sensor unit is made to oppose these both to-be-detected parts to an axial direction.

[Second Example of Embodiment]
FIGS. 12-13 has shown the 2nd example of embodiment of this invention corresponding to Claim 1,3,5. In the case of this example, the circumferential phase of the magnetic poles of the detected portions 39 and 40 of the first and second encoders 10 and 11 in the state when torque is not transmitted is 180, as shown in FIG. It is misaligned. That is, the different polarities of both the detected parts 39 and 40 are arranged adjacent to each other in the axial direction. Further, as shown in FIG. 13, in a state where a pair of sensors 42a and 42b constituting the sensor unit 12 are arranged in the same direction, the detection parts of both the sensors 42a and 42b are both the detected parts 39 and 40. Are opposed to the same position in the circumferential direction. Accordingly, the phase difference between the output signals of the sensors 42a and 42b is 180 degrees (the phase difference ratio is 0.5) in a rotation state where the transmission torque is zero.

In the case of the structure of the present example having the above-described configuration, the permanent magnets 37 and 38 constituting both the encoders 10 and 11 are in a state before the first and second encoders 10 and 11 are assembled to the use location. When the axial end surfaces facing each other are magnetically attracted, the circumferential phases of the magnetic poles of both encoders 10 and 11 are shifted from each other by 180 degrees as shown in FIG. For this reason, if the assembly work of the encoders 10 and 11 is performed in this state, it is easy to realize the magnetic pole arrangement relationship as shown in FIG. 12 in the state after the assembly.
Other configurations and operations are the same as in the case of the first example of the above-described embodiment, and thus illustrations and descriptions regarding equivalent parts are omitted.

  When the structures of the first and second examples of the above-described embodiment are implemented, the first and second encoders 10 and 11 are in a predetermined positional relationship as shown in FIG. 9 or FIG. Therefore, it is preferable that a part for defining the relative positional relationship of the magnetic poles in the circumferential direction is provided in a part of the encoders 10 and 11 respectively. Hereinafter, structural examples provided with such a defining portion will be described as third to fifth examples of the embodiment of the present invention.

[Third example of embodiment]
14 to 15 show a third example of the embodiment of the invention corresponding to claims 1, 3, and 5. FIG. In the case of this example, two through holes 67a and 67b, each of which is a defining portion, are provided in the core bar 35b constituting the first encoder 10f so as to be spaced apart in the circumferential direction. Along with this, one core hole 36b constituting the second encoder 11f is provided with one concave hole 68 as a defining portion. With the central axes of the encoders 10f and 11f aligned with each other, the radial positions of the through holes 67a and 67b and the concave hole 68 are equal to each other. The pitch between the two through holes 67a and 67b (the center-to-center distance in the circumferential direction) is equal to the one magnetization pitch of the encoders 10f and 11f (the circle between the S pole and the N pole adjacent in the circumferential direction). It is equal to the center-to-center distance in the circumferential direction.

  In the case of this example, when magnetizing the encoders 10f and 11f at the manufacturing stage, as shown in FIG. 15, the center axes of the encoders 10f and 11f are aligned with each other. A pin 69 as a defining member is inserted or inserted into the through hole 67a (or 67b) of either one of the through holes 67a and 67b and the concave hole 68 without rattling. Thereby, the positioning of the encoders 10f and 11f in the circumferential direction is achieved. In this state, the detected poles 39 and 40 of both encoders 10f and 11f are simultaneously magnetized with S and N poles in the same circumferential direction alternately and at equal pitches in the circumferential direction. Work to do.

  Thereafter, when assembling both the encoders 10f and 11f in the position of use in the positional relationship shown in FIG. 9, the circumference of the encoders 10f and 11f is set by the pin 69 in the same manner as in the above-described magnetization. The operation of assembling both the encoders 10f and 11f at the place of use is performed while positioning the direction. On the other hand, when assembling both the encoders 10f and 11f in the use location in the positional relationship shown in FIG. 12, the through hole through which the pin 69 is inserted is connected from the one through hole 67a (or 67b) to the other. In this state, the relative positional relationship between the encoders 10f and 11f in the circumferential direction is equal to one magnetization pitch with respect to the positional relationship at the time of magnetization described above. In the shifted state, the encoders 10f and 11f are assembled to the use location. In either case, after the encoders 10f and 11f are assembled (fixed) to the use location, the pin 69 is removed from the through hole 67a (or 67b) and the recessed hole 68.

If the encoders 10f and 11f are assembled in the above manner, the encoders 10f and 11f can be easily and accurately assembled to the use location in the positional relationship shown in FIG. 9 or FIG.
Instead of the concave hole 68, a through hole through which the pin 69 can be inserted without rattling may be provided.
Since other configurations and operations are the same as those in the first and second examples of the above-described embodiment, illustration and description regarding equivalent parts are omitted.

[Fourth Example of Embodiment]
FIG. 16 shows a fourth example of an embodiment of the present invention corresponding to claims 1, 3 and 5. In the case of this example, a pair of recesses 70a and 70b, each of which is a defining portion, are provided in the circumferential direction on one axial end surface (end surface on the second encoder 11g side) of the permanent magnet 37b constituting the first encoder 10g. Are provided apart from each other. Along with this, one convex portion 71 as a defining portion is provided on one end surface in the axial direction of the permanent magnet 38b constituting the second encoder 11g (the end surface on the first encoder 10g side). The pitch between the concave portions 70a and 70b is equal to one magnetization pitch of the encoders 10g and 11g.

  In the case of this example, when magnetizing both the encoders 10g and 11g in the manufacturing stage, from the state shown in FIG. 16A, the permanent magnets 37b constituting the encoders 10g and 11g, 38b, the one end surfaces of the encoders 10g and 11g in the circumferential direction of each of the encoders 10g and 11g in the circumferential direction are brought into contact with each other by engaging one of the concave portions 70a and 70b with the convex portion 71. Position it. And in this state, as shown in FIG. 16A, the S pole and the N pole are circularly rotated at the same circumferential phase as shown in FIG. Work to magnetize alternately and at equal pitches in the circumferential direction.

  Thereafter, when the encoders 10g and 11g are assembled to the use location in the positional relationship shown in FIG. 9, the encoders 10g and 11g are positioned in the circumferential direction in the same manner as the above-described magnetization. As shown, both encoders 10g and 11g are assembled to the place of use. On the other hand, when assembling both the encoders 10g and 11g in the use location in the positional relationship shown in FIG. 12, from the state shown in FIG. 16B, the permanent magnets constituting both the encoders 10g and 11g. 37b and 38b end each other in the axial direction, and by engaging the other concave portion 70b of the concave portions 70a and 70b with the convex portion 71, the circumference between the encoders 10g and 11g Orient the direction. And in this state, the operation | work which assembles these encoders 10g and 11g to a use location is performed.

If the encoders 10g and 11g are assembled in the manner as described above, the encoder 10g and 11g can be easily and accurately assembled to the use location in the positional relationship shown in FIG. 9 or FIG.
Since other configurations and operations are the same as those in the first and second examples of the above-described embodiment, illustration and description regarding equivalent parts are omitted.

[Fifth Example of Embodiment]
FIG. 17 shows a fifth example of the embodiment of the present invention corresponding to the first, third, and fifth aspects. In the case of this example, the other axial end surface of the permanent magnet 37c constituting the first encoder 10h (the end surface opposite to the second encoder 11h) and the same axial direction of the permanent magnet 38c constituting the second encoder 11h. A pair of mark portions 72a and 72b (73a and 73b) such as a concave portion and a convex portion, each of which is a defining portion, are separated from each other on the end surface (the end surface on the first encoder 10h side) in the circumferential direction. Provided. The circumferential positions of the mark portions 72a and 72b provided in the first encoder 10h are two adjacent magnetization boundaries (S poles) existing in the detected portion 39 of the first encoder 10h. And the position in the circumferential direction at the boundary between the N pole and the N pole. Further, the circumferential positions of the mark portions 73a and 73b provided on the second encoder 11h are the positions of two adjacent magnetized boundaries existing in the detected portion 40 of the second encoder 11h. It coincides with the circumferential position.

  In the case of this example, the work of assembling both the encoders 10h and 11h in the use location is the state after assembly in which the positions of both the mark portions 72a and 72b and the mark portions 73a and 73b are the same in the circumferential direction. The mark portions 72a and 72b (73a and 73b) are visually observed so that the circumferential positions of the mark portions 72a (or 72b) and the mark portions 73b (or 73a) coincide with each other. Check with confirmation.

If the encoders 10h and 11h are assembled in the manner as described above, the encoder 10h and 11h can be easily and accurately assembled in the use location in the positional relationship shown in FIG. 9 or FIG.
Since other configurations and operations are the same as those in the first and second examples of the above-described embodiment, illustration and description regarding equivalent parts are omitted.

[Sixth Example of Embodiment]
A sixth example of an embodiment of the present invention corresponding to claims 1, 3, and 5 will be described with reference to FIGS. In the case of this example, the first male involute spline portion 62a provided on the outer peripheral surface of one end of the torsion bar 15b (refer to “torsion bar 15” in FIG. 6 for the entire configuration) The second plating layer 75 is provided on the surface layer portion of the second male involute spline portion 64a provided with the one plating layer 74 on the outer peripheral surface of the other end. The metal constituting the first and second plated layers 74 and 75 is softer than an alloy steel such as carbon steel constituting the torsion bar 15b, the input shaft 13 and the output shaft 14 (see FIG. 6). , Copper, nickel and the like. The first male involute spline portion 62a (the second male involute spline portion 64a) is connected to the first female involute spline portion 63a (on the inner peripheral surface of the output shaft 14) provided on the inner peripheral surface of the input shaft 13. The second female involute spline portion 65a) is press-fitted with a tightening margin smaller than the thickness of the first plating layer 74 (second plating layer 75) in the free state. Thus, as shown in FIG. 18, the first male involute spline portion 62a (the second male involute spline portion 64a) and the first female involute spline portion 63a (the second female involute spline portion 65a) are connected. An involute spline engaging portion 24a1 (involute spline engaging portion 24b1) is configured by engaging with each other without rattling in the circumferential direction. In particular, in this example, the first male involute spline portion 62a (the second male involute spline portion 64a) and the first female involute spline portion 63a (the second female involute spline portion 65a) By crushing the first plating layer 74 (the second plating layer 75) between the tooth surfaces, the circumferential rattling of the involute spline engaging portion 24a1 (the involute spline engaging portion 24b1) is achieved. Is missing. On the other hand, the tooth tip and the tooth bottom of the first male involute spline portion 62a (the second male involute spline portion 64a) and the first female involute spline portion 63a (the second female involute spline portion 65a). A gap is left between the two and the gaps function as a lubricating oil passage.

  In the case of this example, in order to set the tightening margin as described above, the thickness dimension T in the free state of the first plating layer 74 (the second plating layer 75) is as shown in FIG. The spacing between the tooth surfaces before the first plating layer 74 (second plating layer 75) is formed on the first male involute spline portion 62a (second male involute spline portion 64a). It is larger than t (T> t). In the state shown in FIG. 19, the interval t is equal to the first male involute spline portion 62a (the second male involute spline portion 64a) and the first female involute spline portion 63a (the second female involute spline portion 65a. ) And 2d, which is a relative movable amount in the radial direction, can be obtained as t = d · sin θ (θ: angle of the tooth surface with respect to the radius line determined in the design). The distance t can be obtained by other methods. For example, the first male involute spline portion 62a (the second male layer) before the first plating layer 74 (the second plating layer 75) is formed. Based on measuring the dimension of each part of the involute spline part 64a) and the dimension of each part of the first female involute spline part 63a (second female involute spline part 65a) with a conventionally known measuring pin. Thus, the interval t can be obtained.

  Also in the case of the rotation transmission device with the torque measuring device of the present example having the above-described configuration, the both involute spline engaging portions 24a1 and 24b1 are engaging portions that do not cause rattling in the circumferential direction. . For this reason, when the rotational direction of the input shaft 13, which is the rotational shaft on the side where torque is input, is reversed, both the involute spline engaging portions 24a1, 24b1 have a clearance in the circumferential direction that causes backlash. It is possible to prevent the relative rotation of. As a result, it is possible to prevent the inconvenience that the minute torque cannot be accurately measured based on the occurrence of such relative rotation.

That is, when the rotation direction of the input shaft 13 is reversed, if the relative rotation of the circumferential clearance that causes rattling occurs in the involute spline engaging portions 24a1 and 24b1, Similar relative rotation occurs between the first and second encoders 10 and 11 (see, for example, FIG. 6). As a result, as shown by a broken line β in FIG. 20, the characteristic curve representing the relationship between the sensor output and the torque shows nonlinearity in a mode in which the torque changes suddenly at the torque = 0 and the vicinity thereof, and the measurement of the minute torque is performed. It becomes impossible to do accurately.
On the other hand, in the case of this example (and each example of the above-described embodiment), when the rotation direction of the input shaft 13 is reversed, the both involute spline engaging portions 24a1 and 24b1 have a backlash. Since it is possible to prevent the relative rotation corresponding to the circumferential clearance that causes the occurrence, it is possible to prevent the same relative rotation from occurring between the first and second encoders 10 and 11. As a result, as shown by the solid line α in FIG. 20, the linearity of the characteristic curve representing the relationship between the sensor output and the torque is maintained as a whole, so that the minute torque can be measured accurately.

In the case of this example, when the first and second male involute spline parts 62a and 64a are press-fitted into the first and second female involute spline parts 63a and 65a, deformation (elastic deformation or Most of the plastic deformation) occurs in the relatively soft first and second plated layers 74 and 75. For this reason, it is possible to efficiently fill (eliminate) the circumferential gap that causes the rattling of the involute spline engaging portions 24a1 and 24b1 by the first and second plated layers 74 and 75. At the same time, the deformation of copper and nickel constituting both the first and second plated layers 74 and 75 is smaller than the deformation of steel constituting the main body portion of each of the involute spline portions 62a, 64a, 63a and 65a. Because it is generated by force, the force required for press-fitting can be kept low. In the case of this example, as the metal constituting the first and second plating layers 74 and 75, a metal having appropriate crushing resistance and rigidity, such as copper and nickel, is used. Even when used over a long period of time, it is difficult to form a gap between the plated layers 74 and 75 and the tooth surfaces of the female involute spline portions 63a and 65a.
Since other configurations and operations are the same as those in the first to fifth examples of the above-described embodiment, illustration and description regarding equivalent parts are omitted.

In the sixth example of the above-described embodiment, only the both involute spline engaging portions 24a1 and 24b1 have a structure that eliminates rattling in the circumferential direction by a relatively soft plating layer. When implemented, the other involute spline engaging portions 24c to 24e (see FIG. 6) can appropriately employ a structure that eliminates rattling in the circumferential direction by a relatively soft plating layer.
Moreover, when implementing this invention, it can also be set as the engaging part which produces the slight shakiness of the circumferential direction regarding any involute spline engaging part 24a-24e (refer FIG. 6). If the pair of involute spline engagement portions 24a and 24b existing at both ends of the torsion bar 15b (see FIG. 6) are engagement portions that generate minute rattling in the circumferential direction, sensor output and torque The characteristic curve representing the relationship between the two values becomes as shown by the broken line β in FIG. 20, and the measurement of the minute torque cannot be performed accurately. However, since the torque can be accurately measured in other areas, even if such a configuration is adopted in applications that do not require measurement of minute torque, there is no particular problem.

[Seventh example of embodiment]
21 to 22 show a seventh example of the embodiment of the invention corresponding to claims 1, 3 and 5. In the case of this example, the flange portion 34a provided at one end portion of the connecting shaft 9b is internally fitted and fixed to the other end portion of the input shaft 13a. Specifically, the outer peripheral surface of the flange 34a is a cylindrical surface 76, and this cylindrical surface 76 is fitted into a cylindrical surface 77 provided on the inner peripheral surface of the other end of the input shaft 13a by an interference fit. . In the case of this example having such a configuration, it is possible to simplify the structure of the portion that connects one end of the connecting shaft 9b to the input shaft 13a so as not to rotate relative to the input shaft 13a, thereby reducing the manufacturing cost.
Since other configurations and operations are the same as those of the first to sixth examples of the above-described embodiment, illustration and description regarding equivalent parts are omitted.

[Eighth Example of Embodiment]
FIG. 23 shows an eighth example of the embodiment of the present invention corresponding to claims 1 and 3 to 5. In the case of this example, of the pair of tapered roller bearings 29c and 29d that rotatably support the rotating shaft unit 6b with respect to the housing, the inner ring 30c constituting one tapered roller bearing 29c is integrated with the input shaft 13b. The inner ring 30d constituting the other tapered roller bearing 29d is integrally formed with the output shaft 14a. Accordingly, in the case of this example, nuts 32a and 32b (for example, see FIG. 6) for preventing the inner rings 30c and 30d from being detached are omitted. In the case of this example, the inner diameter dimension of the input gear 7 that is externally fitted and fixed to the input shaft 13b is made larger than the outer diameter dimension of the inner ring 30c. Thus, when the input gear 7 is attached to and detached from the input shaft 13b, the input gear 7 can pass around the inner ring 30c in the axial direction.

In the case of this example configured as described above, both the inner rings 30c and 30d and the nuts 32a and 32b as single parts can be omitted, so that the number of parts and assembly man-hours can be reduced, the structure can be simplified, The size and weight can be reduced, and the manufacturing cost can be reduced, the strength of the large collar portions of the inner rings 30c and 30d can be improved, and the degree of freedom in the arrangement of the tapered roller bearings 29c and 29d can be improved.
Since other configurations and operations are the same as those of the first to seventh examples of the above-described embodiment, illustration and description regarding equivalent parts are omitted.

[Ninth Embodiment]
24 to 28 show a ninth example of the embodiment of the invention corresponding to claims 1, 3, and 6. FIG. In the case of this example, the first encoder 10a externally fitted and fixed to the other end portion of the connecting shaft 9 is made of a magnetic metal and has an L-shaped cross section as a whole, and the outer peripheral portion is a spur gear-like first. One detected portion 39a is used. That is, the first detected portion 39a is formed by arranging a plurality of convex portions 50, 50 that protrude from the portion near the outer periphery of the first encoder 10a toward the outer diameter side at an equal pitch in the circumferential direction. In the case of this example, among the first detected portions 39a, the convex portions 50 and 50 correspond to the solid portions described in claim 6, respectively, and the convex portions 50 adjacent to each other in the circumferential direction. , 50 portions correspond to the thinned portions described in claim 6 respectively.

  The second encoder 11a, which is externally fitted and fixed to the other end of the output shaft 14, is made of a magnetic metal plate in a cylindrical shape, and protrudes in the axial direction from the other end surface of the output shaft 14. The half portion is a comb-like second detected portion 40a. That is, the second detected portion 40a is arranged with a plurality of tongue pieces 51, 51 extending from the intermediate portion in the axial direction of the second encoder 11a toward the distal end side in the axial direction at an equal pitch in the circumferential direction. It consists of The total number of these tongue pieces 51, 51 coincides with the total number of the respective convex portions 50, 50. Further, the circumferential width represented by the central angle of each of the tongue pieces 51, 51 is equal to the circumferential width represented by the central angle of each of the convex portions 50, 50. In the case of this example, each of the tongue pieces 51, 51 of the second detected part 40 a corresponds to the solid part described in claim 6, and each of these tongue pieces 51 adjacent to each other in the circumferential direction. , 51 correspond to the thinned portion described in claim 6 respectively.

  In the case of this example, both the first and second detected parts 39a are arranged with the inner peripheral surface of the second detected part 40a being closely opposed to the outer peripheral surface of the first detected part 39a. , 40a are arranged concentrically with each other. That is, both the detected parts 39a and 40a are arranged to overlap in the radial direction while ensuring concentricity. Further, in the state when torque is not transmitted, that is, in the state where the torsion bar 15 is not elastically twisted and deformed and the detected portions 39a and 40a are not relatively displaced in the rotational direction, 50, 50 and the respective tongue pieces 51, 51 have the same circumferential phase.

  In the case of this example, the sensor unit 12a supported by a housing (not shown) is formed in an annular shape as a whole, and these sensor units 12a are arranged on the outer diameter side of the first and second detected portions 39a, 40a. It arrange | positions concentrically with both to-be-detected parts 39a and 40a. Such a sensor unit 12 a includes a stator 52 made of a magnetic material and a plurality of coils 54, 54 including a single conducting wire 53. Of these, the stator 52 is arranged at an equal pitch in the circumferential direction, and each has a plurality of core portions 55 and 55 that are long in the radial direction, and an outer diameter side that is a base end portion of each of the core portions 55 and 55. And an annular rim portion 56 that connects the end portions. The total number of the core portions 55 and 55 is the same as the total number of the tongue pieces 51 and 51 (the total number of the convex portions 50 and 50). Further, the circumferential width represented by the central angle of the inner diameter side end face which is the tip face of each of the core parts 55, 55 is the circumferential width of each tongue piece 51, 51 (each convex part 50, 50 circumferential width). In the case of this example, the end surfaces on the inner diameter side of each of the core portions 55 and 55 are made to face and face each other on the outer peripheral surface of the second detected portion 40a. The coils 54 and 54 are wound around the core portions 55 and 55, respectively, and are adjacent to each other in the circumferential direction, and the winding directions are opposite to each other. Therefore, the total number of the coils 54 and 54 (the core portions 55 and 55) is an even number (10 in the illustrated example). Therefore, in this example, the total number of the convex portions 50 and 50 and the total number of the tongue pieces 51 and 51 are even numbers.

  In the case of the rotation transmission device with a torque measuring device of the present example having the above-described configuration, each of the coils 54 and 54 has both functions for driving to generate a magnetic field and for detecting a change in the magnetic field. Yes. That is, in the case of this example, by applying a driving voltage to each of the coils 54, 54 (the conductive wire 53), when a driving current is passed through the coils 54, 54, the coils 54, 54 adjacent to each other in the circumferential direction. A loop-shaped magnetic flux as shown by thick arrow lines in FIG. 26 flows between the stators 52 and the first and second encoders 10a and 11a. In this state, when the first and second encoders 10a and 11a rotate together with the rotating shaft unit 6, the density of the loop-shaped magnetic flux periodically changes, and accordingly, the coils 54, A periodic induced current flows through 54. As a result, the output signal {voltage, current (when the drive voltage is AC, these peak values, effective values, etc.)}, which is an output signal of the sensor unit 12a, is the (C) of FIG. As shown, it changes periodically. Here, the frequency (and period) of this output takes a value commensurate with the rotational speed of the rotary shaft unit 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, in the case of this example, when the encoders 10a and 11a are relatively displaced in the rotational direction based on the fact that the torsion bar 15 is elastically twisted and deformed during torque transmission, (A) → (B ) In the circumferential direction of the convex portion 50 and the tongue piece 51 constituting the both detected portions 39a and 40a. Along with this, the circumferential width of the magnetic paths inside the encoders 10a and 11a, which are the portions where the convex portions 50 and the tongue pieces 51 overlap in the radial direction, are reduced. As a result, as shown in the order of broken line → solid line in FIG. Here, the phase shift (the amount of decrease in the circumferential width of the magnetic path) increases as the torque increases. Therefore, the magnitude of the output decreases greatly as the torque increases. However, the magnitude of this output varies not only with this torque but also with the rotational speed. That is, the magnitude of the induced current flowing through the coils 54 and 54 (the induced electromotive force of the coils 54 and 54) is proportional to the rate of change of the magnetic flux passing through the coils 54 and 54. The rate of change of the magnetic flux increases in proportion to the rotational speed. Accordingly, the magnitude (amplitude) of the output increases in proportion to the rotational speed. Therefore, in this example, the influence of the torque on the magnitude of the output and the influence of the rotational speed on the magnitude of the output are examined in advance. First, as described above, the rotational speed is obtained based on the frequency (or period) of the output. And the correction which returns the magnitude | size of the said output changed under the influence of this rotational speed to the original magnitude | size is performed. In this way, the torque can be accurately obtained based on the corrected output magnitude.
The drive voltage applied to the conducting wire 53 may be a direct current, but is preferably an alternating current in order to improve noise resistance.

In the case of this example, the sensor unit 12a is formed by combining the stator 52 and the coils 54 and 54, and is not provided with precision electronic components such as a magnetic detection element. Therefore, the sensor unit 12a has excellent heat resistance and vibration resistance. ing. In the case of this example, since only one output is used for measuring the rotation speed and torque, it is not necessary to perform complicated signal processing for the measurement. Therefore, an inexpensive arithmetic unit that does not have a high processing capability can be used as the arithmetic unit for performing this signal processing.
Other configurations and operations are the same as those in the respective examples of the above-described embodiments, and thus illustrations and descriptions regarding equivalent parts are omitted.

  In the case of carrying out the present invention, in the ninth example of the above-described embodiment, the detected portions of both the first and second encoders and the tip surfaces of the core portions constituting the sensor unit A configuration in which the facing direction is changed from the radial direction to the axial direction can also be adopted. In other words, in this case, the detected parts of both the first and second encoders are a pair of annular-shaped detected parts having the same radial dimension, and both the detected parts are overlapped in the axial direction. To do. Further, each core portion constituting the sensor unit is formed long in the axial direction. And the front end surface of each core part is made to oppose the said to-be-detected parts from the one side of the axial direction which is the superimposition direction of these to-be-detected parts.

[Tenth example of embodiment]
29 to 34 show a tenth example of the embodiment of the invention corresponding to claims 1, 3 and 7. In the case of this example, the first encoder 10b fitted and fixed to the other end of the connecting shaft 9 and the second encoder 11b fitted and fixed to the other end of the output shaft 14 are all made of magnetic metal. It is constructed in an annular shape, and has a comb-teeth cylindrical detected portion 39b (40b) on each outer peripheral portion. In other words, the first detected portion 39b constituting the first encoder 10b and the second detected portion 40b constituting the second encoder 11b are each provided with a plurality of tongue pieces 51a, 51a (51b, 51b) that are long in the axial direction. ) Are arranged at equal pitches in the circumferential direction, and the base ends of the tongue pieces 51a and 51a (51b and 51b) are connected to each other. In addition, the shapes and diameters of the detected portions 39b and 40b are equal to each other, but the arrangement directions are opposite to each other with respect to the axial direction. At the same time, the tongue pieces 51a, 51a constituting the first detected portion 39b and the tongue pieces 51b, 51b constituting the second detected portion 40b are provided with a circumferential gap therebetween. Thus, they are alternately arranged one by one in the circumferential direction. In particular, in the case of this example, in the state when torque is not transmitted, the circumferential widths of the portions between the tongue pieces 51a and 51b adjacent in the circumferential direction are all equal. Furthermore, in this state, the circumferential width of each of these portions is equal to the circumferential width of each of the tongue pieces 51a and 51b. This is because a duty ratio ε described later is set to 0.5 in a state where torque is not transmitted. In the case of this example, among the detected portions 39b (40b), the tongue pieces 51a, 51a (51b, 51b) correspond to the solid portions described in claim 7, respectively, and are adjacent in the circumferential direction. The portions between the matching tongue pieces 51a, 51a (51b, 51b) correspond to the thinned portions described in claim 7, respectively.

  In the case of this example, the sensor unit 12b supported by a housing (not shown) includes a synthetic resin holder 41a and a single sensor 42c embedded in the tip of the holder 41a. The detecting portion of the sensor 42c is made to face and face the outer peripheral surface of the detected portions 39b and 40b (portions where the tongue pieces 51a and 51b are alternately arranged in the circumferential direction). The sensor 42c includes a permanent magnet magnetized in a direction (radial direction in the illustrated example) in which the outer peripheral surfaces of the detected parts 39b and 40b face each other, and the magnetization direction of the permanent magnets. A magnetic detection element such as a Hall element, a Hall IC, an MR element, or a GMR element, which is disposed on an end face of the both end faces opposite to the outer peripheral faces of the detected portions 39b and 40b, is provided.

  In the case of the rotation transmission device with the torque measuring device of the present example having the above-described configuration, the output signal of the sensor 42c that constitutes the sensor unit 12b, together with the rotary shaft unit 6, the first and second encoders 10b, As 11b rotates, it changes periodically. Further, in the case of this example, when the torque is transmitted by the rotary shaft unit 6, when the first and second encoders 10 b and 11 b are relatively displaced in the rotational direction based on the elastic torsional deformation of the torsion bar 15. The circumferential width of the portion between the tongue pieces 51a and 51b adjacent in the circumferential direction changes. More specifically, the circumferential width of the portion between every other portion in the circumferential direction is widened, and the circumferential width of the remaining portion is narrowed. As a result, as shown in the order of (A) → (B) in FIG. 33, the duty ratio ε (= time ratio B / A) of the output signal of the sensor 42c changes. Here, since the amount of expansion (narrowing amount) of the circumferential width of each of the inter-portions has a size corresponding to the torque, the duty ratio ε also takes a value corresponding to the torque. Therefore, if the relationship between the duty ratio ε and the torque as shown in FIG. 34 is examined in advance, the torque can be obtained based on the duty ratio ε. Furthermore, in the case of this example, the two-pulse period A related to the output signal of the sensor 42c takes a value commensurate with the rotational speed of the rotary shaft unit 6. Accordingly, if the relationship between the two-pulse period A and the rotational speed is examined in advance, the rotational speed can be obtained based on the two-pulse period A.

In the case of this example, since the detected parts of the first and second encoders 10b and 11b are overlapped with each other in the circumferential direction, the axial dimension of the portion where these detected parts 39b and 40b are installed is set. It can be shortened and a space-saving structure can be obtained. Further, since only one magnetic detection element is required to be incorporated in the sensor unit 12b, the cost of the sensor unit 12b can be suppressed.
Other configurations and operations are the same as those in the first to eighth examples of the above-described embodiment, and thus descriptions of equivalent parts are omitted.

[Eleventh example of embodiment]
FIGS. 35 to 37 show an eleventh example of the embodiment of the invention corresponding to claims 1, 3 and 7. In the case of this example, the first detected portion 39c constituting the first encoder 10c fitted and fixed to the other end portion of the connecting shaft 9, and the second encoder 11c fitted and fixed to the other end portion of the output shaft 14. Are respectively formed in a comb-toothed ring shape. At the same time, the tongue pieces 51c, 51c (51d, 51d) constituting the detected parts 39c, 40c are circumferentially connected in a state where the axial positions of the detected parts 39c, 40c coincide with each other. They are alternately arranged in the circumferential direction with a gap in the direction interposed. And the detection part of the one sensor 42c which comprises the sensor unit 12b is made to oppose the axial direction at the side surface of the axial direction of the part which has arrange | positioned each said tongue piece 51c, 51d.
Other parts except that the shapes of the detected parts 39c and 40c are changed to an annular shape and the facing direction of the detected parts 39c and 40c and the detecting part of the sensor 42c is changed to the axial direction. Since the configuration and operation of are the same as in the case of the tenth example of the above-described embodiment, description of equivalent parts is omitted.

[Twelfth example of embodiment]
38 to 41 show a twelfth example of the embodiment of the invention corresponding to the first, third, and eighth aspects. In the case of this example, the first encoder 10d supported and fixed to the other end portion of the connecting shaft 9 is made of a magnetic material and fitted to the other end portion of the connecting shaft 9, and is made of an annular core bar 35a. And a cylindrical permanent magnet 37a fixed to the outer peripheral surface of the cylindrical portion existing on the outer peripheral portion of the cored bar 35a. In the first detected portion 39d, which is the outer peripheral surface of the permanent magnet 37a, S poles and N poles are alternately arranged at equal pitches in the circumferential direction. On the other hand, the second encoder 11d supported and fixed to the other end portion of the output shaft 14 is made of a magnetic metal plate and fitted to the other end portion of the output shaft 14 and is made of an annular core metal 36a. And a cylindrical permanent magnet 38a fixed to the inner peripheral surface of the cylindrical portion existing on the outer peripheral portion of 36a. The second detected portion 40d, which is the inner peripheral surface of the permanent magnet 38a, is in a state where a predetermined radial interval is provided on the outer diameter side of the first detected portion 39d. Are arranged concentrically. That is, the first and second detected portions 39d and 40d face each other with a predetermined radial interval therebetween. And also in this 2nd to-be-detected part 40d, the south pole and the north pole are arrange | positioned alternately with equal pitch regarding the circumferential direction. The total number of magnetic poles (S pole and N pole) arranged in the second detected part 40d and the total number of magnetic poles arranged in the first detected part 39d coincide with each other. Further, in the state when torque is not transmitted, the detected portions 39d and 40d are arranged so that the opposite poles are opposed to each other in the radial direction with their centers aligned.

  In the case of this example, the sensor unit 12c supported by a housing (not shown) includes a synthetic resin holder 41b and a single sensor 42d embedded in the tip of the holder 41b. The sensor 42d is disposed at the radial center position between the detected portions 39d and 40d. The detection part of the sensor 42d incorporates a magnetic detection element such as a Hall element, Hall IC, MR element, GMR element, etc. The sensitivity direction of the magnetic detection element is at the center of the magnetic detection element. The first and second detected portions 39d and 40d coincide with the radial direction.

  Here, regarding the rotation transmission device with a torque measuring device of the present example having the above-described configuration, as shown in FIG. 40 (A), when the torque is not transmitted, both the detected portions 39d, 40d is not relatively displaced in the rotational direction and when torque is transmitted, that is, as shown in FIG. 5B, the detected portions 39d and 40d are relatively displaced in the rotational direction. Think of it as a state. The sensitivity direction of the magnetic detection element is the vertical direction of (A) and (B), the magnetic flux density in the vertical direction, and the output (voltage, current) of the magnetic detection element, which is the output signal of the sensor unit 12c. Is proportional to the size of In the state when torque is not transmitted, as shown in (A), since the different polarities of the detected portions 39d and 40d are opposed to each other in the radial direction, the direction of the magnetic flux passing through the magnetic detection element is As a whole, it almost coincides with the sensitivity direction. That is, in this state, since the magnetic flux density in the sensitivity direction is maximized, the output of the magnetic detection element is also maximized. On the other hand, in the state at the time of torque transmission, as shown in (B), the positional relationship between the different poles of the detected parts 39d, 40d is shifted in the circumferential direction, so that it passes through the magnetic detecting element. The direction of the magnetic flux is generally inclined with respect to the sensitivity direction of the magnetic detection element. That is, in this state, the magnetic flux density in the sensitivity direction is reduced by this inclination, so that the output of the magnetic detection element is also reduced accordingly. Here, the magnitude of the inclination increases as the torque (the deviation in the circumferential direction) increases. Accordingly, the output of the magnetic detection element is maximized when the torque is zero, and decreases as the torque increases.

  By the way, at the time of transmission of the torque, the detected parts 39d and 40d rotate together with the rotary shaft unit 6. For this reason, the output of the magnetic detection element has a sine wave shape, for example, as shown in FIG. As described above, the magnitude (amplitude) of this output increases as the torque increases. Therefore, if the relationship between the magnitude of the output and the torque is examined in advance, the torque can be obtained based on the magnitude of the output. Further, the frequency (and period) of the output takes a value corresponding to the rotation speed of the rotary shaft unit 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 the case of carrying out this example, the magnetic pole arrangement between the detected parts 39d and 40d is shifted by 90 degrees in electrical angle with respect to the circumferential direction in a state where torque is not transmitted (one detected part). The magnetic pole center and the boundary between the magnetic poles of the other detected part can be opposed to each other in the radial direction). In this case, contrary to the case described above, the output of the magnetic detection element is minimized when torque is not transmitted, and increases as the transmitted torque increases.

  Moreover, when implementing this example, instead of using a magnetic detection element as a detection part of the sensor 42d which comprises the said sensor unit 12c, a coil can also be used. When a coil is used, the central axis of the coil is made to coincide with the radial direction of the first and second detected portions 39d and 40d. In the case of adopting such a configuration, when both of the detected portions 39d and 40d rotate together with the rotating shaft unit 6, the direction and magnitude of the magnetic flux passing through the coil periodically change. The output (voltage, current) of the coil, which is an output signal, periodically changes. Since the frequency (and period) of the output takes a value corresponding to the rotational speed, the rotational speed can be obtained based on the frequency (or period). Further, the magnetic flux density penetrating vertically through the coil changes in accordance with the magnitude of torque (the amount of displacement in the circumferential direction between the different poles of the detected parts 39d and 40d). For this reason, the magnitude | size of the output of the said coil changes according to the magnitude | size of the said torque. However, as in the case of the sensor unit 12a (see FIGS. 24 to 27) of the ninth example of the above-described embodiment, the magnitude of the output of the coil also changes depending on the rotational speed. Accordingly, as in the case of the ninth example of the above-described embodiment, first, as described above, the rotational speed is obtained based on the output frequency (or period) of the coil, and then changes under the influence of the rotational speed. The correction is performed to return the output size to the original size. In this way, the torque can be accurately obtained based on the corrected output magnitude.

Also in this example, since only one sensor 42d is incorporated in the sensor unit 12c, the cost of the sensor unit 12c can be reduced.
Since other configurations and operations are the same as those of the first to eighth examples of the above-described embodiment, illustration and description regarding equivalent parts are omitted.

  In the case of carrying out the present invention, in the twelfth example of the above-described embodiment, the detected parts of both the first and second encoders, the detecting part of one sensor constituting the sensor unit, It is also possible to adopt a configuration in which the facing direction is changed from the radial direction to the axial direction. That is, in this case, the detected portions of the first and second encoders are a pair of annular-shaped detected portions having the same diameter dimension, and both the detected portions are opposed in the axial direction. Arrange. And the detection part of one sensor which comprises a sensor unit is arrange | positioned between these to-be-detected parts.

[13th Embodiment]
FIG. 42 shows a thirteenth example of the embodiment of the present invention corresponding to the first, third, and fifth aspects. This example is a modification of the first example of the embodiment shown in FIGS. That is, in the case of the first example of the above-described embodiment, the first and second encoders 10 and 11 and the sensor unit 12 are concentrated around the other end of the output shaft 14. In the case of this example, the first and second encoders 10 and 11 and the sensor unit 12 are concentrated around the other end portion of the input shaft 13. For this reason, in this example, one end (left end in FIG. 42) outer peripheral surface of the connecting shaft 9a arranged on the inner diameter side of the torsion bar 15 is engaged with the inner peripheral surface of the other end of the output shaft 14 by involute spline engagement. , And non-relatively connected by key engagement or the like. At the same time, a retaining ring or the like (not shown) is used to prevent displacement of the connecting shaft 9a in the axial direction with respect to the output shaft 14. In this state, the other end portion (the right end portion in FIG. 42) of the connecting shaft 9 a is projected from the other end opening of the input shaft 13. The first encoder 10 is fitted and fixed to the other end of the connecting shaft 9a, and the second encoder 11 is fitted and fixed to the other end of the input shaft 13. Further, the sensor unit 12 is supported by a housing (not shown) in a state where the detection portions of the pair of sensors constituting the sensor unit 12 are opposed to the detection portions of the encoders 10 and 11.
FIG. 42 is a schematic diagram, and illustrations and reference numerals are omitted in some parts, but other configurations and operations are the same as those in the first example of the embodiment described above. A description of the equivalent parts is omitted.

[Fourteenth example of embodiment]
FIG. 43 shows a fourteenth example of the embodiment of the present invention corresponding to the first, third and sixth aspects. This example is a modification similar to the thirteenth example described above with respect to the ninth example of the embodiment shown in FIGS. 24 to 28 described above, and includes both the first and second encoders 10a and 11a and the sensor unit 12a. The input shaft 13 is concentrated around the other end portion.
Note that FIG. 43 is a schematic diagram, and illustrations and reference numerals are omitted in some parts, but other configurations and operations are the same as those in the ninth example of the above-described embodiment (the connection shaft 9a has been described above). Since this is the same as the case of the thirteenth example), the explanation about the equivalent part is omitted.

[Fifteenth example of embodiment]
FIG. 44 shows a fifteenth example of the embodiment of the present invention corresponding to the first, third, and seventh aspects. This example is a modification similar to the thirteenth example described above with respect to the tenth example of the embodiment shown in FIGS. 29 to 35 described above, and includes both the first and second encoders 10b and 11b and the sensor unit 12b. The input shaft 13 is concentrated around the other end portion.
Note that FIG. 44 is a schematic diagram, and illustrations and symbols are omitted in some parts, but other configurations and operations are the same as those in the tenth example of the above-described embodiment (the connection shaft 9a has been described above). Since this is the same as the case of the thirteenth example), the explanation about the equivalent part is omitted.

[Sixteenth example of embodiment]
FIG. 45 shows a sixteenth example of the embodiment of the present invention corresponding to the first, third and seventh aspects. This example is a modification similar to the thirteenth example described above with respect to the eleventh example of the embodiment shown in FIGS. 35 to 37, and includes both the first and second encoders 10c and 11c and the sensor unit 12b. The other end portion of the input shaft 13 is concentrated.
Note that FIG. 45 is a schematic diagram, and illustration and reference numerals are omitted in some parts, but other configurations and operations are the eleventh example of the above-described embodiment (the connection shaft 9a has been described above). Since this is the same as the case of the thirteenth example), the explanation about the equivalent part is omitted.

[Seventeenth example of embodiment]
FIG. 46 shows a seventeenth example of the embodiment of the present invention corresponding to the first, third, and eighth aspects. This example is a modification similar to the thirteenth example described above with respect to the twelfth example of the embodiment shown in FIGS. 38 to 41, and includes both the first and second encoders 10d and 11d and the sensor unit 12c. The input shaft 13 is concentrated around the other end portion.
46 is a schematic diagram, and illustrations and reference numerals are omitted in some parts, but other configurations and operations are the same as those in the twelfth example of the above-described embodiment (the connection shaft 9a has been described above). Since this is the same as the case of the thirteenth example), the explanation about the equivalent part is omitted.

[Eighteenth example of embodiment]
47 to 50 show an eighteenth example of the embodiment of the present invention corresponding to the second, third and fifth aspects. In the case of each example of the embodiment described above, both the first and second encoders and the sensor unit are concentrated on one end side of the rotary shaft unit, whereas in this example In this case, the first and second encoders 10e and 11e and the sensor unit 12d are concentrated in the intermediate portion of the rotary shaft unit 6a in a portion sandwiched between the input gear 7 and the output gear 8 in the axial direction. Arranged.

  For this reason, in the case of this example, the first encoder 10e is attached to the front end surface (the left end surface in FIGS. 47 and 50) of the parking lock gear 28 formed integrally with the inner peripheral portion of one side surface of the input gear 7. , Are integrally formed. That is, the first encoder 10e has a plurality of convex portions 50a, 50a made of magnetic metal, which are integrally formed so as to protrude in the axial direction from the front end surface of the parking lock gear 28, in the circumferential direction. Are arranged at an equal pitch. The entire first encoder 10e is a first detected portion 39e. The first encoder 10e is fixed to the input shaft 13 through the input gear 7 and the parking lock gear 28. The second encoder 11e is integrally formed at a portion near one end of the outer peripheral surface of the output shaft 14 and adjacent to the output gear 8 in the axial direction. That is, the second encoder 11e includes a plurality of convex portions 50b, 50b made of magnetic metal, which are integrally formed in a state where each protrudes in a radial direction from a portion near one end of the outer peripheral surface of the output shaft 14. They are arranged at equal pitches in the circumferential direction. The second encoder 11e as a whole is the second detected portion 40e. In the case of this example, the first and second encoders 10e and 11e have the same outer diameter, are arranged concentrically and adjacent to each other in the axial direction. The total number of the convex portions 50a and 50a and the total number of the convex portions 50b and 50b coincide with each other. Further, the circumferential widths of the convex portions 50a and 50a and the circumferential widths of the convex portions 50b and 50b are equal to each other. Further, the phases in the circumferential direction of the respective convex portions 50a, 50a and the respective convex portions 50b, 50b are made to coincide with each other in a state where torque is not transmitted.

  The sensor unit 12d includes a synthetic resin holder 41c and first and second sensors 42e and 42f embedded in the tip of the holder 41c. Among these sensor units 12d, the detection part of the first sensor 42e is the outer peripheral surface (first detected part 39e) of the first encoder 10e, and the detection part of the second sensor 42f is the second encoder. 11e is supported by a housing (not shown) in a state of being opposed to the outer peripheral surface (second detected portion 40e). The two sensors 42e and 42f are, among the permanent magnets magnetized in the direction in which the outer peripheral surfaces of the encoders 10e and 11e are opposed to their own detection units, and both end surfaces of the permanent magnets in the magnetization direction, And a magnetic detection element such as a Hall element, a Hall IC, an MR element, or a GMR element, disposed on an end face facing the outer peripheral surface of the encoders 10e and 11e. One permanent magnet can be used for both the sensors 42e and 42f.

  In this example, no connecting shaft is provided on the inner diameter side of the torsion bar 15a. An oil introduction path 43a that is open only on one end surface is provided at the radial center of the torsion bar 15a. In the case of this example, a pair of oil passages 44a provided in the portions closer to both ends of the rotary shaft unit 6a, the lubricating oil introduced into the oil introduction passage 43a through the end opening of the oil introduction passage 43a, 44b is supplied to the inside.

In the case of the rotation transmission device with a torque measuring device of the present example configured as described above, as in the case of the first example of the embodiment shown in FIGS. The frequency (and period) of the output signals of the second sensors 42e and 42f takes a value corresponding to the rotational speed of the rotary shaft unit 6a. Therefore, the rotational speed can be obtained based on this frequency (or period). The phase difference ratio (= phase difference / 1 period) between the output signals of the first and second sensors 42e, 42f is determined by the rotary shaft unit 6a between the input gear 7 and the output gear 8. The value is commensurate with the torque transmitted between the two. Therefore, the torque can be obtained based on the phase difference ratio.
Other configurations and operations are the same as in the case of the first example of the above-described embodiment, and thus description of equivalent parts is omitted.

  In the case of carrying out the present invention, as in the eighteenth example of the above-described embodiment, both the first and second encoders and the sensor unit are connected to the input gear and the output in the axial direction at the intermediate portion of the rotary shaft unit. In the case of adopting a configuration that concentrates on the portion sandwiched between the gears, the configurations of the first and second encoders and the sensor unit are the configurations of the inventions according to claims 6 to 8 ( For example, the configurations of the ninth to twelfth examples of the above-described embodiment may be employed.

  The present invention can also be implemented by applying the characteristic portions of the structures of the second to eighth examples of the above-described embodiment to the structures of the thirteenth to eighteenth examples of the above-described embodiment.

[Nineteenth and twentieth examples of embodiment]
When practicing the present invention, regarding the structure of the combined portion of the end portions of the input shaft 13 and the output shaft 14, the structure of the nineteenth example of the embodiment shown in FIG. 51 or the implementation shown in FIG. The structure of the twentieth example in the form can also be adopted.
Of these, in the case of the structure of the nineteenth example of the embodiment shown in FIG. 51, the radial bearing of the radial bearing and the thrust bearing installed in the combination part is a cylindrical sleeve that is a radial sliding bearing. The bearing 57 is used. On the other hand, the thrust bearing is a thrust needle bearing 58. The thrust needle bearing 58 is positioned in the radial direction by being externally fitted to the proximal end portion of the input side combination cylinder portion 16 without a large radial backlash.
On the other hand, in the case of the structure of the twentieth example of the embodiment shown in FIG. 52, the radial bearing and the thrust bearing installed in the combination part are used as a cylindrical sleeve bearing 57 and an annular thrust washer 21c. Yes. Of these, the thrust washer 21c is positioned in the radial direction by being externally fitted to the proximal end portion of the input side combination cylinder portion 16 without large backlash. At the same time, the thrust washer 21c is positioned in the circumferential direction by engaging a pin 59 implanted in the stepped surface 19 with an engagement hole 60 formed in a part of the thrust washer 21c.
In the case of the structures of the nineteenth example and the twentieth example of the embodiment shown in FIGS. 51 and 52, an oil passage 61 is provided at the base end of the input side combination cylinder part 16. Forming. Through the oil passage 61, the lubricating oil can be supplied from the cylindrical space 47 to a portion between the space where the radial bearing is installed and the space where the thrust bearing is installed. Thereby, the lubrication performance of the both bearings is improved.
Other configurations and operations are the same as those in the respective examples of the above-described embodiments, and thus illustrations and descriptions regarding equivalent parts are omitted.

The type of transmission used by incorporating the present invention is not particularly limited as long as it has a counter shaft and a counter gear. Automatic transmission (AT), continuously variable transmission (CVT), manual transmission (MT), etc. Various formats can be adopted. Further, the measured rotation speed and torque may be used for vehicle control other than shift control. Further, the prime mover 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 in a hybrid vehicle or an electric vehicle, for example.
Furthermore, when implementing the present invention, it is essential to measure the torque, but it is essential to measure the rotational speed except for some structures that induce a voltage in the coil (using induced electromotive force). is not. Even if rotation speed is required, it can be measured by a separate simple structure.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 2, 2a Encoder 3 Sensor 4 Harness 5 Sensor unit 6, 6a, 6b Rotating shaft unit 7 Input gear 8 Output gear 9, 9a, 9b Connecting shaft 10, 10a-10h First encoder 11, 11a-11h Second Encoder 12, 12a to 12d Sensor unit 13, 13a, 13b Input shaft 14, 14a Output shaft 15, 15a Torsion bar 16 Input side combination cylindrical portion 17 Output side combination cylindrical portion 18 Radial needle bearing 19 Stepped surface 20 Tip surface 21 , 21a-21c Thrust washer 22 Slit 23 Reinforcing cylindrical portion 24a-24e, 24a1, 24b1 Involute spline engaging portion 25a-25d Retaining ring 26a, 26b Cylindrical surface fitting portion 27 Step surface 28 Parking lock gear 29a-29d Conical Roll Receiving 30a-30d Inner ring 31 Spacer 32a, 32b Nut 33 Stepped surface 34 Gutter 35, 35a, 35b Core metal 36, 36a, 36b Core metal 37, 37a-37c Permanent magnet 38, 38a-38c Permanent magnet 39, 39a- 39e 1st to-be-detected part 40, 40a-40e 2nd to-be-detected part 41, 41a-41c Holder 42a-42f (1st, 2nd) Sensor 43, 43a Oil introduction path 44a, 44b Oil path 45a, 45b Annular space 46a , 46b Oil groove 47 Cylindrical space 48 Tip surface 49 Step surface 50, 50a, 50b Convex part 51, 51a-51d Tongue piece 52 Stator 53 Conductor 54 Coil 55 Core part 56 Rim part 57 Sleeve bearing 58 Thrust needle bearing 59 Pin 60 Engagement hole 61 Oil passage 62, 62a First male involute spline 6 63a First female involute spline portion 64, 64a Second male involute spline portion 65, 65a Second female involute spline portion 66a, 66b Groove 67a, 67b Through hole 68 Recessed hole 69 Pin 70a, 70b Recessed portion 71 Convex portion 72a, 72b Marking part 73a, 73b Marking part 74 First plating layer 75 Second plating layer 76 Cylindrical surface 77 Cylindrical surface

Claims (8)

A housing, a rotary shaft unit, a first gear, a second gear, a connecting shaft, a first encoder, a second encoder, and one sensor unit;
Among these, the rotary shaft unit includes both hollow first and second rotary shafts and a hollow torsion bar, and the first and second rotary shafts are concentric with each other. And is rotatably supported by the housing in a state in which one end portions of the first and second rotation shafts are combined so as to be rotatable relative to each other. Are arranged concentrically with both the first and second rotating shafts, and one end is connected to the first rotating shaft and the other end is connected to the second rotating shaft so as not to be relatively rotatable.
The first gear is fixed to an axially intermediate portion of the outer peripheral surface of the first rotating shaft,
The second gear is fixed to an axially intermediate portion of the outer peripheral surface of the second rotating shaft,
The connecting shaft is disposed concentrically with the torsion bar on the inner diameter side of the torsion bar, and one end portion thereof cannot be rotated relative to one of the first and second rotating shafts. In the connected state, the other end is projected in the axial direction from the other rotating shaft and the end of the torsion bar,
The first encoder has an annular first detected portion concentric with the connecting shaft in a state of being fixed to the other end portion of the connecting shaft, and the magnetic characteristics of the first detected portion are measured with a circumference. The direction is changed alternately and at an equal pitch,
The second encoder has an annular second detected portion concentric with the other rotating shaft in a state of being fixed to the other end of the other rotating shaft, and a magnetic field of the second detected portion. The characteristics are changed alternately and at equal pitches in the circumferential direction,
The first and second detected parts are arranged close to each other,
The sensor unit is supported by the housing in a state where a part of the sensor unit is opposed to the first and second detected parts, and the sensor unit itself is included in the first and second detected parts. A rotation transmission device with a torque measuring device that changes an output signal in response to a change in magnetic characteristics of a portion facing each other. A housing, a rotary shaft unit, a first gear, a second gear, a first encoder, a second encoder, and one sensor unit;
Of these, the rotary shaft unit includes both hollow first and second rotary shafts and a torsion bar, and the first and second rotary shafts are arranged concentrically with each other. In addition, one end of each other is rotatably supported by the housing, and the torsion bar is disposed on the inner diameter side of the first and second rotating shafts. It is arranged concentrically with both the first and second rotating shafts, one end is connected to the first rotating shaft, and the other end is connected to the second rotating shaft so as not to be relatively rotatable,
The first gear is fixed to an axially intermediate portion of the outer peripheral surface of the first rotating shaft,
The second gear is fixed to an axially intermediate portion of the outer peripheral surface of the second rotating shaft,
The first encoder is disposed at a position sandwiched between the first and second gears with respect to the axial direction, and is fixed to the first rotating shaft. And the first to-be-detected portion that is concentric and annular, and the magnetic characteristics of the first to-be-detected portion are changed alternately and at equal pitches in the circumferential direction,
The second encoder is disposed at a position sandwiched between the first and second gears with respect to the axial direction, and is fixed to the second rotating shaft. And a second to-be-detected portion that is concentric and annular, and the magnetic characteristics of the second to-be-detected portion are changed alternately and at equal pitches in the circumferential direction.
The first and second detected parts are arranged close to each other,
The sensor unit is supported by the housing in a state where a part of the sensor unit is opposed to the first and second detected parts, and the sensor unit itself is included in the first and second detected parts. A rotation transmission device with a torque measuring device that changes an output signal in response to a change in magnetic characteristics of a portion facing each other.   The axial dimension of a portion that elastically twists and deforms when transmitting torque at an intermediate portion in the axial direction of the torsion bar is larger than an axial interval between the two gears. A rotation transmission device with a torque measuring device according to any one of the above.   The rotary shaft unit is rotatably supported with respect to the housing by a plurality of rolling bearings, and an inner ring constituting at least one of the rolling bearings is the first rotary shaft or the The rotation transmission device with a torque measurement device according to any one of claims 1 to 3, wherein the rotation transmission device is integrally formed with the second rotation shaft. The sensor unit includes a first sensor opposed to the first detected portion and a second sensor opposed to the second detected portion. Both the first and second sensors are: Each of the first and second detected parts generates an output signal that changes in response to a change in the magnetic characteristics of the part facing itself.
The rotation transmission device with a torque measuring device according to any one of claims 1 to 4. The first and second encoders are each made of a magnetic material, and the first and second detected parts are alternately arranged with a thinning part and a solid part at equal pitches in the circumferential direction. These two detected parts are arranged in a radial or axial direction so as to be close to each other,
The sensor unit includes a stator made of a magnetic material and a plurality of coils made of one conductor, and an output current or output voltage of the conductor in a state where a drive voltage is applied to the conductor as an output signal. Each of the stators is long in the overlapping direction of the detected parts, and the front end surfaces of the stators are opposed to the detected parts from one side in the overlapping direction of the detected parts. A plurality of core portions arranged at an equal pitch in the circumferential direction, and an annular rim portion that connects the base end portions of each of the core portions, and each of the coils The cores are externally fitted one by one, and the winding directions are opposite to each other in the circumferentially adjacent coils.
The rotation transmission device with a torque measuring device according to any one of claims 1 to 4. The first and second encoders are each made of a magnetic material, and the first and second detected parts are alternately arranged with a thinning part and a solid part at equal pitches in the circumferential direction. The solid part constituting the first detected part and the solid part constituting the second detected part are alternately arranged in the circumferential direction with a circumferential gap interposed therebetween. ,
The sensor unit includes one sensor opposed to a portion where the solid portions of the two detected portions are alternately arranged, and the sensor includes the solid portions of the two detected portions alternately. An output signal that changes in response to a change in magnetic characteristics of a portion of the portion that is opposed to the portion,
The rotation transmission device with a torque measuring device according to any one of claims 1 to 4. The first and second detected parts are a pair of cylindrical surfaces opposed to each other in the radial direction or a pair of annular surfaces opposed to each other in the axial direction, each having an S pole and an N pole. It is arranged at equal pitches alternately in the circumferential direction,
The sensor unit includes a magnetic detection element or a coil disposed between the detected parts, and outputs an output voltage or output current of the magnetic detection element or an output voltage or output current of the coil. Used as a signal,
The rotation transmission device with a torque measuring device according to any one of claims 1 to 4.

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