JP5839693B2 - Transmission belt loss calculation method - Google Patents

Description

  The present invention relates to a transmission belt loss calculation method.

  Transmission belts are used in a wide range of fields such as automobiles, agricultural machinery, general industrial machinery, and office automation equipment. And the importance of an energy saving technique and an environmental load reduction technique is increasing with respect to the transmission belt used in any field | area.

  For example, Non-Patent Document 1 discloses various examples of improvements aimed at reducing loss as an environment-friendly energy-saving technology for transmission belts.

Bando Technical Port, No. 13, P16 (2009)

  The subject of this invention is isolate | separating the loss resulting from a transmission belt for every factor.

The present invention includes a drive pulley,
A drive shaft that is rotatably supported and supported by the drive pulley;
A rotational drive source that rotationally drives the drive pulley at a set rotational speed via the drive shaft;
A driven pulley provided so that a transmission belt can be wound around the drive pulley;
A driven shaft provided to be supported so that the driven pulley is supported and the shaft can rotate.
Torque detecting means for detecting torque generated in each of the drive shaft and the driven shaft;
A transmission belt loss calculation method using a belt transmission device having:
A drive belt is wound between the drive pulley and the driven pulley, and the drive pulley is rotated by the rotary drive source in a state in which no rotational load is applied to the driven pulley, so that the drive belt Depends on the belt running speed of the belt-induced loss torque (C + D) caused by the transmission belt based on the torque generated at the drive shaft and the driven shaft detected by the torque detection means at that time A first step of separating the belt-induced loss torque (C + D) for each belt travel speed into an intrinsic loss torque C that does not depend on the belt travel speed and a dependent loss torque D that depends on the belt travel speed;
A transmission belt is wound around the drive pulley and the driven pulley, and the drive pulley is rotated by the rotational drive source in a state where no rotational load is applied to the driven pulley, so that the transmission belt is driven at a constant belt The belt travels based on the torque generated in the drive shaft and the driven shaft detected by the torque detection means at that time, varying the level of the loss generation factor different from the belt travel speed. The dependence of the intrinsic loss torque C on the speed to the loss generation factor is obtained, and the intrinsic loss torque C at each level of the loss occurrence factor is determined as the intrinsic loss torque E independent of the loss occurrence factor and the loss occurrence factor. A second step of separating into a dependent loss torque F that depends,
Is provided.

  According to the present invention, by using the predetermined belt transmission device and following the predetermined first and second steps, the loss torque caused by the transmission belt is changed to the dependent loss torque D depending on the belt traveling speed, the belt traveling. It is possible to separate the characteristic loss torque E that does not depend on the loss generation factor different from the speed and the dependency loss torque F that depends on the loss generation factor.

It is a perspective view of a single cog belt. It is a top view of a belt run test machine. It is a top view of the belt running test machine which shows the test conditions in the procedure 1 of the 1st step. It is a graph which shows the belt running speed dependence relationship of bearing loss torque (A + B). It is a top view of the belt run test machine which shows the test conditions in procedure 2 of the 1st step. It is a graph which shows the belt running speed dependence relationship of the loss torque at the time of no load (X + Y). It is a graph which shows the belt running speed dependence relationship of belt-induced loss torque (C + D). It is explanatory drawing which shows the deformation | transformation of the cross-sectional shape of a single cog belt when receiving a side pressure. It is a graph which shows the axial load dependence relation of the intrinsic loss torque C which does not depend on belt running speed. It is a graph which shows the input torque dependence relationship of elastic slip loss motive power. It is a graph which shows the belt loss power in each input torque in case a shaft load is 284 N, and the breakdown of each loss generation factor. It is a graph which shows the breakdown of the belt loss power in each input torque in each case where axial load is 284N, 372N, and 529N, and each loss generation factor. It is a graph which shows the input torque dependence relationship of the sum of the elastic slip loss and the side pressure deformation / entrance / exit sliding loss power in each case where the axial loads are 284N, 372N and 529N.

  Hereinafter, embodiments will be described in detail based on actual cases based on FIGS.

  Based on the transmission belt loss calculation method according to the present embodiment, a single cog belt 10 as a transmission belt is tested using a belt running test machine 20 (belt transmission device), and the loss torque according to the first to third steps. And the loss power was quantified separately for each factor.

(Single cog belt 10)
FIG. 1 shows a single cog belt 10 as a transmission belt. The single cog belt 10 is widely used as a transmission V-belt for small motorcycles. The single cog belt 10 had a circumference of 830 mm, a belt width of 18.8 mm, and a belt thickness of 9.3 mm.

  This single cog belt 10 has a belt body 11 formed of a chloroprene rubber composition.

  The belt body 11 is formed in a trapezoidal shape with a transverse cross section tapered downward, and in a side view, a protrusion cog formed so as to extend in the belt width direction is formed on the inner peripheral side in the belt length direction. Are arranged at a constant pitch. A cotton upper canvas 12 is attached to the outer peripheral side of the belt main body 11 so as to cover the surface thereof. A bottom canvas 13 made of nylon fiber is attached to the inner peripheral side of the belt body 11 so as to cover the surface thereof. Note that both the upper canvas 12 and the bottom canvas 13 are subjected to an adhesion treatment for adhesion to the belt body 11.

  The belt body 11 has a two-layer structure of an adhesive rubber layer 11a on the outer peripheral side and a shape-retaining rubber layer 11b on the inner peripheral side. A polyester fiber core wire 14 is embedded in the adhesive rubber layer 11a so as to form a spiral having a pitch in the belt width direction at an intermediate portion in the belt thickness direction. Further, in the shape-retaining rubber layer 11b, a nylon fiber thread 15 is embedded in an intermediate portion in the belt thickness direction so as to form a waveform along the cogs. The core wire 14 and the staple 15 are also subjected to an adhesion process for adhesion to the belt body 11.

(Belt running test machine 20)
FIG. 2 shows a belt running test machine 20.

  This belt running test machine 20 includes a drive pulley 211 (pulley pitch diameter: 47.2 mm), a drive system constituted by a drive shaft 221 and an AC motor 231, a driven pulley 212 (pulley pitch diameter: 118 mm), a driven shaft 222, And a driven system constituted by a DC motor 232. The pulley pitch diameter is a bending diameter of the line of the core wire 14 when the single cog belt 10 is wound around the driving pulley 211 or the driven pulley 212.

  The driving pulley 211 has a V-groove for winding the single cog belt 10 around the periphery.

  The drive shaft 221 has one end coupled to the center of the drive pulley 211 and extends to one side of the drive pulley 211 (upper side in FIG. 2) to pivotally support the drive pulley 211 and is disposed at an interval. A pair of oil mist lubricated bearings 241 are provided so as to be capable of rotating the shaft. A drive side torque detector 251 is interposed between the pair of bearings 241 of the drive shaft 221. It should be noted that both ends of the shaft inserted through the torque detector 251 on the drive side are coupled to one end side portion and the other end side portion of the drive shaft 221 through the coupling 261, respectively, thereby the intermediate portion of the drive shaft 221. Is configured. The drive shaft 221 is provided with a rotation detector (not shown).

  The AC motor 231 is provided on the side of the drive shaft 221 so that the shaft extends in parallel with the drive shaft 221. Drive pulleys 271 and 281 are attached to the other end of the drive shaft 221 and the tip of the shaft of the AC motor 231 so as to be provided in the same plane, and the drive pulleys 271 and 281 are connected between the drive pulleys 271 and 281. A belt 291 is wound around. The AC motor 231 is configured such that the drive pulley 211 can be rotationally driven at a set rotational speed via the drive belt 291 and the drive shaft 221. Therefore, this AC motor 231 constitutes a rotational drive source.

  Similarly to the drive pulley 211, the driven pulley 212 is formed with a V-groove for winding the single cog belt 10 on the periphery, and the drive pulley so that the single cog belt 10 can be wound around the drive pulley 211. 211 is provided in the same plane.

  The driven shaft 222 has one end coupled to the center of the driven pulley 212 and extends to the other side of the driven pulley 212 (the lower side in FIG. 2) to pivotally support the driven pulley 212 and is disposed at an interval. A pair of oil mist lubricated bearings 242 are provided so as to be capable of rotating the shaft. A driven side torque detector 252 is interposed between the pair of bearings 242 of the driven shaft 222. The driven-side torque detector 252 and the driving-side torque detector 251 constitute torque detecting means for detecting torque generated in each of the drive shaft 211 and the driven shaft 221. The shaft inserted into the driven-side torque detector 252 is coupled at both ends to the one end side portion and the other end side portion of the driven shaft 222 via the coupling 262, thereby the intermediate portion of the driven shaft 222. Is configured. The driven shaft 222 is provided with a rotation detector (not shown).

  The DC motor 232 is provided on the side of the driven shaft 222 such that the shaft extends in parallel with the driven shaft 222. The driven pulleys 272 and 282 are attached to the other end of the driven shaft 222 and the shaft tip of the DC motor 232 so as to be provided in the same plane, and the driven pulleys 272 and 282 are driven between them. A belt 292 is wound around. The DC motor 232 is configured to apply a rotational load to the driven pulley 212 via the driven belt 292 and the driven shaft 232. Therefore, this DC motor 232 constitutes a rotational load source. The DC motor 232 is also configured to be able to rotate the driven pulley 212 at a set rotational speed via the driven belt 292 and the driven shaft 222. Therefore, the DC motor 232 also constitutes another rotational drive source.

  In the belt running test machine 20, the drive system is configured to be movable so that the shaft interval between the drive pulley 211 and the driven pulley 212 is variable, and thereby, a predetermined set axial load is applied to the drive shaft 211 and the driven shaft 222. Is provided so that the set belt tension can be applied to the single cog belt 10 wound between the drive pulley 211 and the driven pulley 212.

(First step)
In the first step, the single cog belt 10 is wound around the drive pulley 211 and the driven pulley 212 and no rotation load is applied to the driven pulley 212, and in this state, the drive pulley 211 is rotationally driven by the AC motor 231. Then, the single cog belt 10 is caused to travel while varying the belt traveling speed, and the torque generated on the drive shaft 221 and the driven shaft 222 detected by the torque detector 251 on the driving side and the torque detector 252 on the driven side at that time. Based on the above, the belt running speed dependence of the belt-induced loss torque (C + D) caused by the single cog belt 10 was obtained.

  Specifically, the belt-induced loss torque (C + D) was obtained by subtracting the loss torque caused by the system other than the single cog belt 10 from the loss torque of the entire belt running test machine 20 according to the following procedures 1 to 3.

  When there is no or very small loss torque due to the system other than the single cog belt 10 in the loss torque of the belt running test machine 20 as a whole, the drive side torque detector 251 and the driven side torque detector are used. The sum of the torques generated in the drive shaft 221 and the driven shaft 222 detected by 252 can be used as the belt-induced loss torque (C + D) as it is. However, from the viewpoint of quantifying and separating the loss torque with high accuracy, it is preferable to reduce the loss torque caused by the system other than the single cog belt 10 from the loss torque of the belt running test machine 20 as a whole.

<Procedure 1>
In step 1, as shown in FIG. 3, the single cog belt 10 is not wound between the drive pulley 211 and the driven pulley 212 and no rotational load is applied to the driven pulley 212. In this state, the drive shaft 221 and The rotational speed dependency of the bearing loss torque (A + B) generated in the drive shaft 221 and the driven shaft 222 when the driven shaft 222 is rotated at the same rotational speed by varying the rotational speed is converted into a belt travel speed dependency. Asked. This bearing loss torque (A + B) is a loss torque caused by a system other than the single cog belt 10 out of the loss torque of the belt running test machine 20 as a whole.

  Specifically, the drive pulley 211 is rotated by the AC motor 231 and the driven pulley 212 is rotated by the DC motor 232 at the same rotation speed, and the loss torque of the drive shaft 221 detected by the drive-side torque detector 251 at that time. The sum of the loss torque of the driven shaft 222 detected by the driven-side torque detector 252 is defined as the bearing loss torque (A + B).

  The rotational speeds of the driving pulley 211 and the driven pulley 212 were varied to 1000 rpm, 2000 rpm, 3000 rpm, 4000 rpm, 5000 rpm, and 5500 rpm. These are equivalent to 2.5 m / s, 5.0 m / s, 7.5 m / s, 10.0 m / s, 12.5 m / s, and 13.7 m / s, respectively, in terms of belt running speed.

  The bearing loss torque for each belt running speed is 0.083 Nm at 2.5 m / s, 0.092 Nm at 5.0 m / s, 0.095 Nm at 7.5 m / s, and 0 at 10.0 m / s. It was 0.110 Nm at 0.098 Nm, 12.5 m / s, and 0.093 Nm at 13.7 m / s.

  FIG. 4 shows the belt running speed dependency of the bearing loss torque (A + B).

  According to this, the belt running speed dependency relationship of the bearing loss torque (A + B) can be linearly approximated by a linear expression. If the extrapolated value (0.083 Nm) of the belt travel speed = 0 of the approximate straight line is the inherent loss torque A independent of the belt travel speed, the bearing loss torque (A + B) at each belt travel speed is the belt travel. The characteristic loss torque A that does not depend on the speed and the dependency loss torque B that depends on the remaining belt traveling speed obtained by reducing the characteristic loss torque A can be separated.

  When the loss torques of the drive system and the driven system are the same, only the drive pulley 211 or only the driven pulley 212 is rotated to detect the loss torque, and then doubled. May be the bearing loss torque (A + B). Further, the bearing loss torque (A + B) may be obtained from the catalog value of the loss torque of the bearings 241 and 242 without actually detecting the loss torque.

<Procedure 2>
In step 2, as shown in FIG. 5, the single cog belt 10 is wound between the driving pulley 211 and the driven pulley 212, and a constant axial load (284 N dead weight) is applied to the driving shaft 221 and the driven shaft 222. A constant belt tension (143N) is applied to the single cog belt 10 and no rotational load is applied to the driven pulley 212. In this state, the drive pulley 211 is rotationally driven by the AC motor 231 and the single cog belt 10 is rotated. The belt travel speed is varied, and at that time, the no-load loss torque (X + Y) generated in the drive shaft 221 and the driven shaft 222 detected by the drive-side torque detector 251 and the driven-side torque detector 252 is detected. ) Was determined. The no-load loss torque (X + Y) is a loss torque of the entire belt running test machine 20 including the single cog belt 10.

  Belt running speeds converted from the number of rotations of the drive pulley 211 are 2.5 m / s, 5.0 m / s, 7.5 m / s, 10.0 m / s, 12.5 m / s, and 13.7 m / s. It was changed to s.

  The no-load loss torque (X + Y) for each belt running speed is 0.224 Nm at 2.5 m / s, 0.247 Nm at 5.0 m / s, 0.245 Nm at 7.5 m / s, and 10. It was 0.265 Nm at 0 m / s, 0.269 Nm at 12.5 m / s, and 0.275 Nm at 13.7 m / s.

  FIG. 6 shows the belt running speed dependency of the no-load loss torque (X + Y).

  According to this, the belt running speed dependency relationship of the no-load loss torque (X + Y) can also be linearly approximated by a linear expression. If the extrapolated value (0.218 Nm) of the belt running speed = 0 of the approximate straight line is the inherent loss torque X independent of the belt running speed, the no-load loss torque (X + Y) at each belt running speed is The characteristic loss torque X that does not depend on the belt travel speed and the dependency loss torque Y that depends on the remaining belt travel speed obtained by subtracting the inherent loss torque X can be separated.

<Procedure 3>
In the procedure 3, the belt running speed dependency relationship of the bearing loss torque (A + B) obtained in the procedure 1 is subtracted from the belt running speed dependency relationship of the no-load loss torque (X + Y) obtained in the procedure 2, and each belt running speed is determined. The belt-induced loss torque (C + D) was obtained. As described above, the belt-induced loss torque (C + D) resulting from the single cog belt 10 at no load can be separated and quantified from the no-load loss torque (X + Y) of the entire belt running test machine 20.

  The belt-induced loss torque (C + D) for each belt running speed is 0.141 Nm at 2.5 m / s, 0.155 Nm at 5.0 m / s, 0.150 Nm at 7.5 m / s, 10.0 m / s. And 0.167 Nm at 12.5 m / s and 0.182 Nm at 13.7 m / s.

  FIG. 7 shows the belt running speed dependency of the belt-induced loss torque (C + D).

  According to this, the belt traveling speed dependence relationship of the belt-induced loss torque (C + D) can also be linearly approximated by a linear expression.

  In the first step, the belt-induced loss torque (C + D) for each belt travel speed is changed from the belt-induced loss torque (C + D) to the inherent loss torque C independent of the belt travel speed based on the belt travel speed dependency relationship. , Separated into a dependent loss torque D depending on the belt running speed.

  Specifically, the extrapolated value (0.089 Nm) of the belt running speed = 0 of the approximate straight line in FIG. 7 showing the belt running speed dependency relationship of the belt-induced loss torque (C + D) obtained in the first step is the belt running speed. The inherent loss torque C that does not depend on the belt, and the belt-induced loss torque (C + D) at each belt traveling speed depends on the inherent loss torque C that does not depend on the belt traveling speed and the remaining belt traveling speed obtained by subtracting the inherent loss torque C. And the dependent loss torque D. As described above, the belt-induced loss torque (C + D) can be further separated for each factor depending on the presence or absence of dependence on the belt running speed. The intrinsic loss torque C is obtained by subtracting the intrinsic loss torque A from the intrinsic loss torque X, and the dependent loss torque D is obtained by subtracting the intrinsic loss torque B from the dependent loss torque Y.

  Here, since it is considered that the intrinsic loss torque C is a factor that does not depend on the belt running speed, the loss torque (hereinafter referred to as “belt”) caused by the bending of the belt due to the single cog belt 10 being wound around the driving pulley 211 or the driven pulley 212. Bending loss torque ”)), when the single cog belt 10 is wound around the driving pulley 211 or the driven pulley 212, the single cog belt 10 receives a lateral pressure from the driving pulley 211 or the driven pulley 212, as shown in FIG. Loss torque (hereinafter referred to as “side pressure deformation loss torque”) due to deformation to warp, and sliding at the beginning and end of winding of the single cog belt 10 around the driving pulley 211 or the driven pulley 212. Loss torque caused by That.) It is considered to be included.

(Second step)
In the second step, the single cog belt 10 is wound around the driving pulley 211 and the driven pulley 212, and the driving pulley 211 is rotationally driven by the AC motor 213 without applying a rotational load to the driven pulley 212. The driving torque detector 251 and the driven torque detector 252 are driven at a constant belt running speed (13.7 m / s) while varying the axial load as a loss generation factor different from the belt running speed. Based on the torque generated in the drive shaft 221 and the driven shaft 222 detected by the above, the dependency of the inherent loss torque C on the shaft load at the belt traveling speed was obtained.

  Specifically, for each axial load, the belt travel obtained in step 1 from the torque generated in the drive shaft 221 and the driven shaft 222 detected by the drive-side torque detector 251 and the driven-side torque detector 252. By subtracting the bearing loss torque (A + B) at the speed and the dependent loss torque D depending on the belt running speed at the belt running speed obtained in the second step, the inherent loss torque C at each shaft load was obtained.

  FIG. 9 shows the axial load dependency relationship of the intrinsic loss torque C independent of the belt running speed.

  According to this, the axial load dependence relationship of the intrinsic loss torque C can be approximated by a quadratic curve.

  In the second step, the intrinsic loss torque C at each axial load is separated into an intrinsic loss torque E that does not depend on the axial load and a dependent loss torque F that depends on the axial load.

  Specifically, the extraordinary value (0.089 Nm) of the approximate load in FIG. 8 showing the axial load dependence relationship of the intrinsic loss torque C is set as the intrinsic loss torque E that does not depend on the axial load. The natural loss torque C in FIG. 2 is separated into an intrinsic loss torque E that does not depend on the axial load and a dependent loss torque F that depends on the remaining axial load obtained by reducing the intrinsic loss torque E. Thus, by determining the dependency of the inherent loss torque C on the axial load applied to the drive shaft 211 and the driven shaft 212, the inherent loss torque C at each axial load is changed to the inherent loss torque E independent of the axial load. And the dependent loss torque F depending on the axial load.

  Here, since the intrinsic loss torque E is considered to be a factor independent of the belt running speed and the axial load, it can be considered as a belt bending loss torque.

  The dependency loss torque F is a bearing loss torque generated by the system based on the application of an axial load to the drive shaft 211 and the driven shaft 221 (hereinafter referred to as “bearing load dependent bearing loss torque G”). Therefore, the highly accurate dependent loss torque H was obtained by subtracting the shaft load dependent bearing loss torque G from the dependent loss torque F and separating it. The bearing load dependent bearing loss torque G was based on the catalog value of the bearing 23. The high-accuracy dependent loss torque H is considered to be a factor that does not depend on the belt traveling speed and depends on the shaft load, and therefore includes side pressure deformation loss torque and in / out sliding loss torque. If there is no or very small bearing load dependent bearing loss torque G, it is not always necessary to separate the bearing load dependent bearing loss torque G from the dependent loss torque F, but the loss torque is quantified with high accuracy. From the viewpoint of separating them, it is preferable to obtain the high-precision dependent loss torque H by separating the shaft load dependent bearing loss torque G from the dependent loss torque F.

  As described above, the loss torque of the entire belt running test machine 20 is divided into the dependent loss torque D, the inherent loss torque E, and the high-precision dependent loss torque H (or the dependent loss torque F) caused by the single cog belt 10, It can be separated into a bearing loss torque (A + B) and a shaft load dependent bearing loss torque G caused by a system other than the above.

(Third step)
In the third step, the single cog belt 10 is wound around the drive pulley 211 and the driven pulley 212 and the same constant axial load (284 N dead weight) as that in the procedure 2 is applied to the drive shaft 221 so that the single cog belt 10 is fixed. A belt tension (143N) is applied and a constant rotational load is applied to the driven pulley 212 by the DC motor 232. In this state, the drive pulley 211 is rotationally driven by the AC motor 231 and the single cog belt 10 is moved. , And traveling at the same constant belt traveling speed (13.7 m / s) as in the third step, and obtained based on the torque T generated in the drive shaft 221 detected by the drive side torque detector 251 at that time. input torque [Delta] T, the rotational speed N _i1 of the drive pulley 211, and single cog belt It was determined elastic slip power loss ΔW based on 0 of the slip rate s.

  Specifically, the input torque ΔT was obtained by subtracting the no-load loss torque (X + Y) at the belt running speed obtained in the procedure 2 from the torque T.

Further, the input power W was calculated from the input torque ΔT and the rotational speed N _i1 of the drive pulley 211 based on the following formula (1).

The input rotational speed N _i1 when the driving pulley 211 is loaded in the belt traveling test, the input rotational speed N _i0 when the driving pulley 211 is unloaded under the same traveling condition, and the driven pulley 212 of the belt traveling test. The slip ratio s was calculated based on the following equation (2) from the output rotation speed N _s1 when loaded and the output rotation speed N _s0 when no load was applied under the same traveling condition of the driven pulley 212.

  And elastic slip loss power (DELTA) W was computed based on following formula (2) as a product of input power W and slip ratio s.

  Then, the rotational load applied to the driven pulley 212 by the DC motor 232, that is, the input torque was varied, and the elastic slip loss power ΔW at each input torque was obtained. The elastic slip loss power ΔW is 0.003 kW when the input torque is 1 Nm, 0.011 kW when the input torque is 2 Nm, 0.021 kW when the input torque is 3 Nm, 0.047 kW when the input torque is 4 Nm, and 0.047 kW when the input torque is 5 Nm. When the input torque was 6 Nm, it was 0.117 kW, and when the input torque was 7 Nm, it was 0.201 kW.

  FIG. 10 shows the input torque dependency of the elastic slip loss power ΔW. This shows that the increase rate of the elastic slip loss power ΔW increases as the input torque increases.

  In the “Practical design of belt transmission and precision conveyance” edited by Yokendo Co., Ltd., the belt transmission technology symposium, the elastic slip loss power is proportional to the square of the effective tension and the belt running speed. It is disclosed that the product ES of the belt longitudinal stiffness coefficient E and the belt cross-sectional area S is inversely proportional. Therefore, the input torque dependency of the elastic slip loss power ΔW can also be obtained by calculation. Here, the belt longitudinal rigidity coefficient E of the transmission belt is obtained from the belt bending rigidity EI of the transmission belt.

  Next, according to the above equation (2), the dependence loss torque D that depends on the belt running speed, the intrinsic loss torque E that does not depend on the axial load (belt tension), and the high accuracy dependence that depends on the axial load (belt tension). Loss torque H was converted to loss power. The belt running speed-dependent loss power D, the belt bending loss power E, and the side pressure deformation / out-and-out sliding loss power H were respectively set. The belt running speed dependent loss power D was 0.020 kW, the belt bending loss power E was 0.051 kW, and the side pressure deformation / entrance / exit sliding loss power H was 0.046 kW. As described above, the loss power caused by the single cog belt 10 is converted from the elastic slip loss power ΔW, the loss power C converted from the dependency loss torque C depending on the belt running speed, and the inherent loss torque E independent of the shaft load. And predicting separately for each loss generation factor of loss power E converted from high-precision loss torque H depending on shaft load and loss power H converted from dependency load torque F (loss power F converted from dependency loss torque F) Can do.

  FIG. 11 shows a breakdown of the loss power at each input torque expected for the single cog belt 10 and its loss generation factors. According to this, if the input torque is up to 2 Nm, the influence of the belt bending loss power E and the side pressure deformation / in / out sliding loss power H is large, but if the input torque becomes larger than that, the elastic slip loss power The effect of ΔW is expected to increase.

  Next, the elastic slip loss ΔW, the belt running speed dependent loss power D, the belt bending loss power E, and the lateral pressure deformation / entry / slide sliding loss power H were also obtained in each case where the axial loads were 372N and 529N. When the axial load is 372 N, the elastic slip loss ΔW is 0.002 kW when the input torque is 1 Nm, 0.009 kW when the input torque is 2 Nm, 0.018 kW when the input torque is 3 Nm, 0.036 kW when the input torque is 4 Nm, When the input torque was 5 Nm, it was 0.059 kW, when the input torque was 6 Nm, it was 0.089 kW, and when the input torque was 7 Nm, it was 0.153 kW. The belt running speed dependent loss power D was 0.020 kW, the belt bending loss power E was 0.051 kW, and the side pressure deformation / entrance / exit sliding loss power H was 0.070 kW. When the axial load is 529 N, the elastic slip loss power ΔW is 0.001 kW when the input torque is 1 Nm, 0.008 kW when the input torque is 2 Nm, 0.015 kW when the input torque is 3 Nm, and 0.031 kW when the input torque is 4 Nm. When the input torque was 5 Nm, it was 0.054 kW, when the input torque was 6 Nm, it was 0.080 kW, and when the input torque was 7 Nm, it was 0.114 kW. The belt running speed-dependent loss power D was 0.020 kW, the belt bending loss power E was 0.051 kW, and the side pressure deformation / entrance / exit sliding loss power H was 0.128 kW.

  FIG. 12 shows a breakdown of the belt loss power at each input torque expected for the single cog belt 10 and its loss generation factor by adding the results of the cases where the shaft loads are 372N and 529N to FIG. . According to this, as the axial load, that is, the belt tension increases, it is expected that the lateral pressure deformation / in / out sliding loss power H increases. This is because when the axial load increases and the belt tension increases, when the single cog belt 10 is wound around the drive pulley 211 or the driven pulley 212, the single cog belt 10 receives a lateral pressure from the drive pulley 211 or the driven pulley 212, and FIG. It is considered that this is because the side pressure deformation loss torque resulting from the deformation so as to warp in the belt width direction increases as indicated by the broken line in FIG. Further, it is expected that the elastic slip loss ΔW decreases as the axial load increases. This is because when the axial load increases and the belt tension increases, the side pressure received by the single cog belt 10 from the drive pulley 211 or the driven pulley 212 when the single cog belt 10 is wound around the drive pulley 211 or the driven pulley 212 increases. This is considered to be because the power transmission force due to the frictional force increases and the slip becomes smaller.

  Next, the input torque dependence relationship of the elastic slip loss ΔW and the sum H of the lateral pressure deformation / out-and-out sliding loss power, which are presumed to be greatly influenced by the axial load from the above results, was examined for each axial load. When the axial load is 284 N, the sum of the elastic slip loss ΔW and the side pressure deformation / exit sliding torque power H is 0.050 kW when the input torque is 1 Nm, 0.058 kW when the input torque is 2 Nm, and 0 when the input torque is 3 Nm. 0.069 kW for an input torque of 4 Nm, 0.119 kW for an input torque of 5 Nm, 0.164 kW for an input torque of 6 Nm, and 0.248 kW for an input torque of 7 Nm. When the axial load is 372 N, the sum of the elastic slip loss ΔW and the side pressure deformation / in / out sliding loss power H is 0.073 kW when the input torque is 1 Nm, 0.079 kW when the input torque is 2 Nm, and 0 when the input torque is 3 Nm. It was 0.106 kW when the input torque was 4 Nm, 0.129 kW when the input torque was 5 Nm, 0.160 kW when the input torque was 6 Nm, and 0.223 kW when the input torque was 7 Nm. When the shaft load is 529 N, the sum of the elastic slip loss ΔW and the lateral pressure deformation / in / out sliding loss power H is 0.130 kW when the input torque is 1 Nm, 0.136 kW when the input torque is 2 Nm, and 0 when the input torque is 3 Nm. It was 0.159 kW when the input torque was 4 Nm, 0.182 kW when the input torque was 5 Nm, 0.209 kW when the input torque was 6 Nm, and 0.243 kW when the input torque was 7 Nm.

  FIG. 13 shows the input torque dependency of the sum of the elastic slip loss ΔW and the side pressure deformation / in / out sliding loss power H when the axial loads are 284N, 372N, and 529N. As the axial load increases, the elastic slip loss ΔW decreases, while the side pressure deformation / in / out sliding loss power H increases. According to this, in the low input torque range of 6 Nm or less, the sum of the loss power is low. It can be seen that the load is smaller, and in the high input torque range, the sum of the loss power is smaller when the high-axis load is applied. Accordingly, by applying an appropriate axial load corresponding to the input torque, that is, by setting and applying an axial load that minimizes the sum of the elastic slip loss ΔW and the side pressure deformation / out-and-out sliding loss power H, the single cog belt 10 The loss can be reduced and the efficiency can be improved.

  As described above, the loss torque caused by the single cog belt 10 is separated from the loss torque of the entire belt running test machine 20 including the single cog belt 10, and the loss torque caused by the single cog belt 10 is further separated for each loss generation factor. By separating them into the causes, optimization guidelines for reducing the loss of the entire belt transmission device and the direction of improvement as the single cog belt 10 can be found.

(Other embodiments)
In the above-described embodiment, the single cog belt 10 is targeted. However, the present invention is not particularly limited thereto, and a flat belt, a V-belt, a V-ribbed belt, a high load transmission V-belt composed of a tension band and a block, a toothed belt, and the like. Can also be targeted.

  In the above embodiment, the axial load is a loss generation factor. However, the present invention is not particularly limited to this. For example, the pulley diameter of the drive pulley 211 and / or the driven pulley 212, the rotational speed of the drive pulley 211 and the driven pulley 212, and the like. The ratio, belt length, friction coefficient of the belt surface, and the like may be varied as loss generation factors. In particular, the influence of the pulley diameters of the drive pulley 211 and the driven pulley 212 on the loss torque is considered to be large. Therefore, the pulley diameters of the drive pulley 211 and / or the driven pulley 212 are varied as a loss generation factor, and the intrinsic loss It is also a preferable aspect to separate the torque C into an intrinsic loss torque E that does not depend on the pulley diameter and an intrinsic loss torque F that depends on the pulley diameter.

  In the above embodiment, the biaxial belt running test machine 20 having one drive pulley 211 and one driven pulley 221 is used. However, the present invention is not particularly limited to this, and there are two or more driven pulleys (for example, driven pulleys). A belt running test machine having 2 to 4 pulleys may be used. In this case, if the driven pulley is a variable factor, the loss for each pulley can be separated and quantified.

  The present invention is useful for a transmission belt loss calculation method.

10 Single cog belt (power transmission belt)
DESCRIPTION OF SYMBOLS 11 Belt main body 11a Adhesive rubber layer 11b Shape-retaining rubber layer 12 Upper canvas 13 Bottom canvas 14 Core wire 15 Sudare 20 Belt running test machine (belt transmission device)
211 Drive pulley 221 Drive shaft 231 AC motor (rotary drive source)
221 driven pulley 222 driven shaft 232 DC motor (rotational load source, other rotational drive source)
241,242 Bearings 251,252 Torque detector (torque detection means)
261, 262 Coupling 271, 272 Driving pulley 281, 282 Driven pulley 291 Drive belt 292 Driven belt

Claims (6)

A driving pulley;
A drive shaft that is rotatably supported and supported by the drive pulley;
A rotational drive source that rotationally drives the drive pulley at a set rotational speed via the drive shaft;
A driven pulley provided so that a transmission belt can be wound around the drive pulley;
A driven shaft provided to be supported so that the driven pulley is supported and the shaft can rotate.
Torque detecting means for detecting torque generated in each of the drive shaft and the driven shaft;
A transmission belt loss calculation method using a belt transmission device having:
A drive belt is wound between the drive pulley and the driven pulley, and the drive pulley is rotated by the rotary drive source in a state in which no rotational load is applied to the driven pulley, so that the drive belt Depends on the belt running speed of the belt-induced loss torque (C + D) caused by the transmission belt based on the torque generated at the drive shaft and the driven shaft detected by the torque detection means at that time A first step of separating the belt-induced loss torque (C + D) for each belt travel speed into an intrinsic loss torque C that does not depend on the belt travel speed and a dependent loss torque D that depends on the belt travel speed;
A transmission belt is wound around the drive pulley and the driven pulley, and the drive pulley is rotated by the rotational drive source in a state where no rotational load is applied to the driven pulley, so that the transmission belt is driven at a constant belt The belt travels based on the torque generated in the drive shaft and the driven shaft detected by the torque detection means at that time, varying the level of the loss generation factor different from the belt travel speed. The dependence of the intrinsic loss torque C on the speed to the loss generation factor is obtained, and the intrinsic loss torque C at each level of the loss occurrence factor is determined as the intrinsic loss torque E independent of the loss occurrence factor and the loss occurrence factor. A second step of separating into a dependent loss torque F that depends,
Loss calculation method for transmission belts equipped with In the transmission belt loss calculation method according to claim 1,
A transmission belt loss calculation method in which the loss generation factor is an axial load applied to the drive shaft and the driven shaft or a pulley diameter of the drive pulley and / or the driven pulley. In the loss calculation method of the transmission belt according to claim 1 or 2,
The belt transmission device further includes a rotational load source configured to apply a rotational load to the driven pulley via the driven shaft,
A transmission belt is wound between the driving pulley and the driven pulley, and the driving pulley is rotationally driven by the rotational driving source in a state where a constant rotational load is applied to the driven pulley by the rotational load source. The belt is driven at the same constant belt running speed as in the second step, and the input torque obtained based on the torque generated in the drive shaft detected by the torque detecting means at that time, the rotation of the drive pulley A transmission belt loss calculation method further comprising a third step of obtaining an elastic slip loss power ΔW based on the number and the slip ratio of the transmission belt. In the transmission belt loss calculation method according to any one of claims 1 to 3,
The first step is
The drive shaft and the driven shaft were rotated at the same rotational speed by varying the rotational speed in a state where no transmission belt was wound between the driving pulley and the driven pulley and no rotational load was applied to the driven pulley. A procedure 1 for converting the rotational speed dependency of the bearing loss torque (A + B) generated in the drive shaft and the driven shaft into a belt running speed dependency,
A drive belt is wound between the drive pulley and the driven pulley, and the drive pulley is rotated by the rotary drive source in a state in which no rotational load is applied to the driven pulley, so that the drive belt Step 2 for determining the belt travel speed dependency of the no-load loss torque (X + Y) generated in the drive shaft and the driven shaft detected by the torque detection means at that time,
The belt-induced loss torque (C + D) is obtained by subtracting the belt running speed dependency of the bearing loss torque (A + B) obtained in the procedure 1 from the belt running speed dependence relationship of the no-load loss torque (X + Y) obtained in the procedure 2 above. Step 3 for obtaining the belt running speed dependency of
The loss calculation method of the transmission belt which has this. In the transmission belt loss calculation method according to claim 4,
The belt transmission has another rotational drive source that rotationally drives the driven pulley at a set rotational speed via the driven shaft,
In the procedure 1, the drive pulley is rotated by the rotational drive source and the driven pulley is rotated at the same rotational speed by the other rotational drive source, respectively, and the drive shaft detected by the torque detecting means and the A transmission belt loss calculation method in which the torque generated in the driven shaft is a bearing loss torque (A + B). In the transmission belt loss calculation method according to any one of claims 1 to 5,
In the second step, a transmission belt that separates a bearing loss torque G generated by applying a constant axial load to the drive shaft and the driven shaft from a dependent loss torque F depending on the loss generation factor. Loss calculation method.

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