JP4478225B2 - Transmission vehicle - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
  The present invention relates to a continuously variable transmission provided in industrial machines such as machine tools, vehicles, motors, etc.etcIt relates to a variable diameter transmission vehicle used in
[0002]
[Prior art]
  FIG. 1 is a conceptual cross-sectional view of a continuously variable transmission that can change a transmission gear ratio (that is, a ratio N1 / N0 of an input rotation speed N1 and an output rotation speed N0) steplessly. The technology of this type of continuously variable transmission is described in, for example, Japanese Patent No. 2,562,081, and is well known.
[0003]
  A characteristic of this transmission is that a spring 3 is used for the driven transmission wheel 1. The principle of operation of this transmission is that a transmission body 4 is wound around a driven (output) side transmission wheel 1 and a driving (input) side transmission wheel 2 to rotate. Therefore, the first (movable) disc wheel 2a of the drive-side transmission wheel 2 is moved toward the second (fixed) disc wheel 2b so that the relative distance between the two disc wheels can be contracted or extended during rotation. In this structure, a pressing force larger than that of the means 3 is applied via a screw shaft 6 from a variable speed power supply source such as an external handle 12 via a bearing 5.
[0004]
  At this time, the transmission body 4 increases in speed if the contact radius at the transmission wheels 1 and 2 changes according to the pressing force and increases the pressing force, but conversely if the pressing force of the device 6 is decreased, the pressing force of the elastic means 3 is increased. Starts to decelerate, and the position of the transmission body 4 is automatically and stably transmitted at the position where the centering is automatically performed by the action of the elastic means 3.
[0005]
  However, in an industrial machine to which this type of transmission is applied, in general, it is often required to transmit a predetermined transmission horsepower Q0 in both the low speed range and the high speed range. Thus, it is impossible to stably transmit the predetermined horsepower Q0 over the entire speed change region.
[0006]
  The reason will be described with reference to FIGS. FIG. 2 is a diagram for explaining the operation of the transmission, and FIG. 3 is a pressure characteristic diagram of the elastic means 3. In FIG. FIG. 2 shows the contact radius r of the transmission body 4 in the driven-side transmission wheel 1 by the minimum speed radius rL and the maximum speed radius rH by a solid line and a broken line, respectively. FIG. 3 also shows that the elastic means 3 has a positive pressure inclination characteristic (abbreviated as a positive characteristic in the present specification) by increasing the pressure with the forward compression by the first disc wheel 1a. Show.
[0007]
  Usually, the predetermined horsepower Q transmitted by the transmission wheel 1 is the relationship between the rotational speed N and the torque T.
        Q [W] = 1.027 x N [rpm] x T [kgm]
Indicated by Therefore, in the elastic means 3 having the positive characteristics, the rotational speed N and the applied pressure increase as the speed increases, but the contact area with the transmission body decreases, so that the maximum transmission horsepower Qmax is transmitted at the maximum speed, but in the low speed area. As the power reaches, the transmission capacity of the power Q decreases at the same time as the rotational speed N and the applied pressure, but the contact area increases.as a resultLittle change in torque TAlmost constantBut the transmission ability isAs output speed N decreasesDescent rapidly.
[0008]
  That is, this means that if the transmission horsepower is forcibly increased in the low speed range, the tension T of the transmission body 4 increases more than necessary, increasing the burden. Further, although the contact surface SL of the transmission wheel 1 is remarkably increased as compared with the area SH at the maximum speed as shown in FIG. 2, when the rotational speed N is low, the elastic means 3 is added as shown in FIG. The pressure is quite fragile. Therefore, slip occurs on the friction surface, and the transmission body 4 is burned and cut in a short time by heat generated by the contact friction pressure.
[0009]
  Therefore, in this type of transmission, the transmission power Q is reduced to the cube of the rotational speed N (N^Three ) There is a defect that it can be applied only to industrial machines having so-called special properties, such as those that obey the laws, or those that do not require transmission horsepower in the low speed range. Inevitably, even during transmission of low horsepower, it was extremely uneconomical to increase the frame number and select a large transmission.
[0010]
  However, the biggest problem isThe transmission torque cannot be secured.This type of transmission cannot exhibit the capability of transmitting a predetermined power in a low speed range, and therefore cannot exhibit the capability of a general industrial machine itself that requires it. The current situation is that there is no way to reach the transmitter.
[0011]
[Problems to be solved by the invention]
  In the present invention, while using elastic means having positive characteristics, the elastic pressure applied to the at least one disc wheel of the transmission wheel via the elastic means increases, for example, in the low speed region during mounting operation. However, the contact between the disc wheel and the transmission body is improved by improving the pressurizing mechanism of the actuator to apply the pressing force to the elastic means according to the command from the outside so that it decreases as it goes to the high speed rangefrictionAs a result, change the pressure to the transmission caranyIt is an object to provide a transmission wheel having a variable diameter capable of continuously varying the transmission torque.
[0012]
[Means for Solving the Problems]
  According to the present invention, the elastic means for increasing the elastic pressure against the compression, the pressing force from the pressure mechanism and the pressure of the elastic means are superimposed on each other in series, and the pressure is applied to the one disc wheel. When the pressure and pressure are applied in the direction of the axis of rotation of the transmission wheel, the elastic means is coaxial with the transmission wheel and the pressurizing mechanism is coaxially or parallel to the transmission wheel to prevent reverse rotation of the command. The actuator with the mechanism compresses the elastic means according to the external commandContact friction pressure due to elastic pressure atThe transmission vehicle is characterized in that the transmission torque is variably applied to the transmission vehicle by increasing or decreasing the control.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
  As a result, the actuator reverses a pressing force that is approximately equal to or at least equal to the maximum load at the maximum speed, with respect to the elastic means that originally has a pressurizing characteristic that increases the pressing force against forward compression. Direction, ieFor exampleDecreasing as the speed reaches the high speed range and increasing as the speed reaches the low speed range As a direction to increase the pressure gradient in the negative direction with respect to the rotational speed (positive characteristic for the speed ratio)Contact friction pressureCan be pressurized by a proportional operation, so that a larger transmission torque TL [kgm] can be secured even for the rotational speed NL [rpm] in the low speed range. Therefore, the power transmission capability in the low speed range does not decrease, but rather the predetermined transmission horsepower can be maintained by increasing the pressing force of the actuator.
[0014]
  In particular, the elastic means automatically aligns with large pressure at low speed and small pressure at high speed against the error factors unique to this type of transmission, such as wear on the transmission body or wear on the frictional contact surface of the transmission wheel. Therefore, the power transmission function can be smoothly performed against these error factors. This function also smoothly absorbs impact vibration from the rotating load side or prime mover side.
[0015]
【Example】
[First embodiment]
  FIG. 4 is a sectional view of a continuously variable transmission to which the transmission wheel of the first embodiment of the present invention is applied. In FIG. 4, 1 and 2 are transmission wheels, bothPressurization is performed by the pressurization mechanisms 14b, 24b, and 24c.A sliding disc wheel, i.e., the first disc wheels 1a, 2a, and a fixed disc wheel, i.e., the second disc wheels 1b, 2b, are arranged opposite to each other. The winding point is the same as in FIG. In FIG. 4, for convenience of understanding the operation description, the contact radius r between the transmission wheels 1 and 2 and the transmission body 4 with the center line as a boundary is conveniently depicted as a maximum diameter on the right side and a minimum diameter on the left side, The depiction of the connection of the endless transmission body 4 in the middle of the drawing is omitted. In addition, details such as the key structure and the lubricating structure are omitted from the drawing.
[0016]
  The drive-side transmission wheel 2 is equipped with a shaft end of an induction motor as an input shaft 7 as a prime mover 11 attached to a fixed disk 10. As in FIG. 1, a manual handle 12 as a shift command supply source 9 is a shift press actuator connected by a connecting rod 13 and a joint 8.6 pressure mechanism 14bIs connected to the first disc wheel 2 a via a bearing 5. Here, the shift press actuator 6 is a screw jack having a trapezoidal screw shaft having the characteristic of preventing reverse rotation.Pressure jack mechanismWorms and worm wheels that are well-known as having a reversal prevention propertyWorm transmission machine 14a consisting ofIs fixed to the transmission main body 10, and the pressure coupling body 15 a and the screw shaft 15 move up and down according to the handle 12.
[0017]
  On the other hand, the technical concept of the transmission wheel of the present invention is applied to the driven transmission wheel 1. A rotary shaft equipped with the transmission wheel 1, that is, the output shaft 20 of the transmission 10, is provided with a through hole 21 coaxially with the shaft core and is cantilevered by bearings 22 and 23, and is entirely supported by a shaft frame 29. It is supported by the main body 10.
[0018]
  The shift reverse press actuator 25 is slightly different from the screw jack of the shift press actuator 6 working in the reverse direction in this example.Has a pressure jack mechanisming. Worm and worm wheel worm transmission with reverse-rotation characteristics24aAre composed of a jack body 24 having a built-in structure, a trapezoidal screw shaft 26, and, in this example, two pressure coupling bodies 27 and 28 shown by two feed nuts. Non-rotating levers 27a and 28a for securing the reference position are provided. The screw shaft 26 isOf output shaft 20Threaded grooves 26 a and 26 b that are threaded through the through-hole 21 and projecting from the hole 21 are formed in a reverse screw relationship with each other, and the feed nuts 27 and 28 are reversed to each other by the rotation of the screw shaft 26. Arranged to go in the direction. Warm of this jack body 24TransmitterOne end of 24a is provided with a hinge 16b, and the worm of another jack body 14 is provided.Transmitter14a is connected to the hinge 16a by a connecting means 19 having a connecting rod 17 and an expansion / contraction part 18, and both the shift power and the speed ratio signal are synchronized between the actuators 6 and 24 as a shift command. Link transmission.
[0019]
  The shift reverse press actuator 25 is different from the shift press actuator 6 in two points in addition to the above.PressurizationThe mechanism works differently. The first difference is the warm of the actuator 25TransmitterWith the rotation of 24a, the screw shaft of the actuator 25 only rotates in principle. The second difference is that the end of the screw shaft 26 and the worm wheel 43 are engaged by a spline shaft, as shown in FIG. Thereby, not only the transmission of the rotational power of the worm wheel 43 but also the purpose of the fine adjustment action as will be described later,Accompanying the elastic vibration of the elastic means 30The structure allows a slight amount of vertical movement.
[0020]
  The shift reverse pressing actuator 25 of the present embodiment is a second formed by a thread groove 26a for pressing the pressing movement of the elastic means 30, that is, the second displacement L2, and a feed nut 27 of the pressure coupling body.PressurizationA first actuator 25a as a jack mechanism, and a disc wheel 1a of the transmission wheel 1 are simply formed by a thread groove 26b and a pressure coupling body 28 for displacing the shift movement, that is, the first displacement L1.PressurizationThe pressure mechanism of the example which the 1st actuator 25b as a jack mechanism shared as a biasing power source with the common single screw shaft 26 and the jack 24 was shown. However, as long as the gear ratio signal can be obtained in conjunction with the shift command supply source 9 or the like, the two energizing power sources may be separated completely.
[0021]
  FIG. 5 is an enlarged cross-sectional view of the elastic means 30 of the present embodiment. The elastic means 30 accommodates four coil springs 33a, 33b, 33c, 33d having diameters that increase sequentially in a pre-pressurized state concentrically and coaxially with the rotary shaft 20 of the transmission wheel 1, and a bottom cover 36 and a case 35. Thus, the elastic means is a single structure. The spring may have any other shape. As shown in FIG. 10 described later, the annular leaf springs may be connected in a single shape. In this embodiment, however, the feed amount of the feed nut 27 is adjusted in order to obtain a step characteristic approximating a proportional operation as shown in FIG. Accordingly, the interlocking rings 37a, 37b, 37c, and 37d applied to the springs are sequentially connected to form a cascade structure in which the applied pressure is added stepwise.
[0022]
  In this embodiment, the elastic means 30 adopts a special structure in order to secure a pressing force that cannot be formed by a single coil spring in a small space. That is, the inside of the case 35 is provided with stepped contact portions 38a, 38b, 38c, and 38d. Since the innermost diameter of each contact portion 38 is larger than the innermost diameter of each interlocking ring 37, each interlocking ring protrudes. . This projecting portion is structured to engage with the adjacent interlocking ring 37 in accordance with the displacement of the feed nut 27 and sequentially increase the pressing force. With the above configuration, the rotational power of the transmission 10 is output from the sheave 41 formed integrally with the transmission wheel 1 via the other transmission body 40 and is connected to a main shaft such as a milling machine or a drilling machine (not shown).
[0023]
  Next, the operation of the first embodiment transmission wheel will be described with reference to FIGS. In FIG. 4, when the initial state of the transmission 10 is assumed to be the highest speed state, the first disc wheels 1a and 2a of the transmission wheels 1 and 2 on the driven side and the driving side are at the HIGH position in the drawing. State.
[0024]
  Assuming that the handle 12 is operated from this state and rotated in the decelerating direction, the shift press actuator 6Pressurization mechanismAs a result, the screw shaft 15 descends downward and starts releasing the pressure on the disc wheel 2a. At this time, the first disc wheel 1 a of the transmission wheel 1 is constantly pressurized by the bearing 5, the feed nut 28, the lead screw 26 and the feed nut 27. In addition, only the first spring 33a in the spring 33 of the elastic means 30 is always pressurized independently. This initial pressure P11 (= Pmin minimum pressure) is a pressure that is adjusted in advance by the positioning operation of the feed nut 27.
[0025]
  A cross-sectional view of the left half of the driven transmission wheel 1 shown in FIG. 4 shows an initial state at the maximum speed before the deceleration operation. Accordingly, when the pressure on the actuator 6 for positioning the transmission wheel 2 by decelerating starts to be released, the pressing force of the driven disk wheel 1a becomes larger than the pressing force of the driving transmission wheel 2, so that the transmission body 4 The contact radius rH increases on the driven vehicle 1 side to become rH ′, and on the drive vehicle 2 side.The contact radius ofSince it acts in a decreasing direction, the rotational speed of the transmission wheel 1 is decelerated.
[0026]
  At this time, the turning force of the handle 12 is also applied to each pressurizing mechanism of the shift reverse pressing actuator 25 from the worm shaft of the driving side pressing actuator 6 through the connecting means 19. Therefore, the feed nut 27 of the second driven actuator 25a starts to rise, increasing the pressing force to the first spring 33a. At the same time, the feed nut 28 of the first driven actuator 25b has the thread grooves 26a and 26b opposite to each other, so that the first disc wheel 1a is lowered and the pressing force increased by the second actuator 25a is superimposed in series. However, it is applied downward with a stronger pressing force. Therefore, the relative distance from the second disc wheel 1b is contracted, and at the same timeElasticityPressure increases in the opposite direction to transmission wheel 2Increased contact friction pressureAs a result, the torque of the transmission wheel 1 increases.
[0027]
  As a result, the transmission ratio as the transmission 10 begins to increase, and the pressure applied to the first disc wheel 1a of the transmission wheel 1 increases conversely even though the transmission speed is decelerated from the highest speed state. Yes. This is because, as shown in FIG. 7, the pressurizing characteristic of the elastic means 3 to the transmission wheel 1 is a positive characteristic having a positive slope with respect to the gear ratio, whereas the elastic means to the transmission wheel 1 of the present invention. As shown by the characteristic line I of the first spring 33a in FIG. 7, the pressure force characteristic indicated by 30 is a negative characteristic having a negative slope with respect to the rotational speed of the transmission wheel 1. Show. Therefore, the shift reverse pressing actuator 25 originally means that the positive elastic means 30 is acting as a negative pressurizing characteristic.
[0028]
  Subsequently, when the handle 12 is further decelerated, the pressing force applied to the nut 2 7 increases, and when it reaches P10 of the characteristic line I, the interlocking ring 38a that is welded and fixed to the first spring 33a of the elastic means 30 in advance is provided. After contacting the second spring 33b, the two springs 33a and 33b start to cooperate at the same time. As shown in the characteristic diagram of FIG. 7, the applied pressure applied to the first disc wheel 1a via the screw shaft 26 suddenly increases stepwise and reaches P21, and shifts from the characteristic line I to the characteristic line II. It will be. Subsequently, when the speed is further reduced, the applied pressure increases along the negative slope along the characteristic line II of the sum of the first and second springs along the characteristic line II.
[0029]
  Thereafter, when the handle 12 is similarly decelerated to the minimum speed state, the same operation as described above is sequentially repeated. In FIG. 4, when the first disc wheels 1a, 2a of the transmission wheels 1, 2 on the driven side and the driving side reach the LOW position in FIG. 4, at this time, all the springs 33a of the elastic means 30 are obtained. , 33b, 33c, and 33d reach the fully pressed state as shown in the right half of FIG. 5, and the applied pressure P40 as the sum of all the spring loads in the lowest speed state becomes the maximum applied pressure Pmax. The characteristic diagram is a negative slope characteristic as shown in FIG.The maximum torque TBecome.
[0030]
  Next, the case where the handle 12 is operated to increase the speed will be described. In this case, the operation at the time of the deceleration operation is completely opposite. When the speed is increased from the minimum speed state, the maximum pressure Pmax is applied to the driven vehicle 1, but the speed ratio is the maximum speed reduction ratio εmax. If the pressing force reduced by the ratio of the reduction ratio εmax is secured from the shift pressing actuator 6, the speed increasing operation can be performed. Accordingly, the pressure applied to the first disc wheel 1a of the transmission wheel 1 by the operation of increasing the speed of the handle 12 starts to drop along the step-like characteristic line in FIG. 7, and decreases as the speed increases sequentially.
[0031]
  As described above, in this embodiment, both the normal elastic means in which the pressing force increases with forward compression and the actuator 25 that supplies the pressing force superimposed in series on the pressing force correspond to the gear ratio. The applied pressure is applied, and the total applied pressure is applied between the first disc wheel 1a and the fixed main body 10, thereby applying a negative force to the first disc wheel 1a with respect to the rotational speed. The shaft torque of the driven vehicle 1 is arbitrarily selected. This means that the pressing force of the shift reverse pressing actuator increases as the relative distance Dm between the first and second disc wheels 1a, 1b in the transmission wheel 1 contracts, slides and decelerates, and conversely the relative distance Dm. It shows that it is acting so as to decrease as it elongates and slides and speeds up. Therefore, it is clearly different from the characteristic line of FIG. 3 as a conventional example, and this actuator 25 shows that the pressure applied by the elastic means 30 gives a negative characteristic to the rotational speed of the driven vehicle 1.
[0032]
  When applying the pressure characteristic line A to the transmission wheel 1, the tension of the transmission body 4 during mounting operation is used below the characteristic line A as shown by the characteristic line B in FIG. However, if the pressure difference between the two increases, heat generation during transmission increases and transmission efficiency also deteriorates. Therefore, ideally, the variation characteristic of the mounting characteristic line B for continuously proportionally controlling the torque is assumed rather than the stepped characteristic A, and the linear pressure characteristic close to this is assumed to be the mounting characteristic line B as described later. Desirable to be applied as a larger characteristic line A 'So there is an advantage that can be used for fine adjustment of various allowable transmission capacity.
[0033]
  As shown in FIG. 2, this type of transmission means that the contact area SL or the contact friction pressure at the lowest speed has already automatically secured several times the SH at the highest speed. As a result, the rotation shaft torque, that is, the transmission torque T received by the transmission wheel rotation shaft from the transmission body 4 can be increased conversely as the rotational speed N decreases. And it shows that it was controlled variably.
[0034]
  This indicates that the transmission horsepower Q can be kept constant if the rotational speed N or the speed ratio and the transmission torque T are applied to each transmission vehicle in synchronization with each other according to the relational expression described above. Incidentally, the pressurization characteristic line D in FIG. 7 shows the positive pressurization characteristic when only the single spring 33a is used and the variable speed reverse press actuator 25 is not used, just like the conventional example in FIG. .
[0035]
  Next, an automatic alignment function such as an error factor of the speed change mechanism and a load side impact factor will be described with reference to FIGS. Here, there are various error factors to the transmission output. Typical examples are (1) elongation of the transmission body 4, (2) deterioration wear of the contact surface of the transmission body 4, (3) There are dimensional wear on the contact surfaces of the disc wheels 1a and 1b, and (4) wear on the jack wheel. In either case, as a result, a constant pressure is constantly applied to the transmission body 4, so that the driven transmission wheel 1 is automatically pressed and aligned during rotation.
[0036]
  6 is an internal structural view of the worm body 24 of FIG. For example, when the transmission wheel 1 in FIG. 4 is in a HIGH (shown in the left half) state at the time of external command at the maximum speed, it is assumed that the transmission body 4a extends to the broken line 4a ′. At this time, the corresponding first pressure spring 33a feeds the screw shaft 26a and the nut 27 presses downward. Therefore, the worm wheel 43 in the jack body 24 is rotatably connected to a spline shaft portion 26c provided on the lower end portion of the screw shaft 26.
[0037]
Therefore, the entire screw shaft 26 moves downward through the wheel 43 by a minute amount M of the extension of the transmission body 4a ', and automatically aligns while rotating. In addition, similar automatic alignment functions with a large applied pressure in the low speed range and with a small applied pressure in the high speed range. This means that the amount of pressurization varies according to the gear ratio in the gear range, so that the contact pressure does not become unstable in any gear region, and all the disturbances in slip and belt transmission can be absorbed. is doing.
[0038]
  In particular, this automatic alignment function absorbs errors with weak pressing force at high speed and strong pressing force at low speed, so the advantage of stable alignment without disturbing the transmission operation during rotation is due to long-term use As an effect of absorbing all the error factors, the transmission vehicle is given practical value. Further, this function is also immediately absorbed by the elastic means 30 and the screw shaft 26 when a vibration shock, which is a sudden load fluctuation on the load side, is applied or when it occurs on the prime mover 11 side. It also fulfills the function of automatically returning.
[0039]
[Second Embodiment]
  FIG. 8 is a sectional view of the transmission wheel 1 according to the second embodiment of the present invention. Differences from the embodiment of FIG. 4 are as follows. (1) One end of the elastic means 30 is directly attached to the first disc wheel instead of the fixed main body 10 and presses the disc wheel directly. (2) The screw shaft 26 of the actuator 25 is provided with a long screw groove 26d at one location, and (3) the stroke of the feed nut 28 as the pressure coupling body is an elastic means as the second actuator. Since the movement of the pressing movement L2 of 30 and the shifting movement L1 of the disc wheel 1a as the first actuator are shared and moved on the single lead portion 26b, the resultant stroke is the sum of both movements. L0 (= L1 + L2) is necessary and greatly increased. For this reason, the thread groove is longer than the drive actuatorConsists of a pressure jack mechanism(4) Since the elastic means 30 directly presses the disc wheel 1a, the spline coupling is unnecessary and fixed so as not to be finely movable between the screw groove 26 and the worm wheel 43 as shown in FIG. (5) There are five springs of the elastic means 30 and the like. Although the operation of this embodiment is controlled by an externally controlled power source, it is almost the same as that of the embodiment of FIG.
[0040]
[Third embodiment]
  FIG. 9 is a sectional view of the transmission wheel 1 according to the third embodiment of the present invention. In the figure, three springs 30a, 30b, 30c are directly mounted on the first disc wheel 1 and pressurized simultaneously to increase the pressure. In the present application, since the plurality of springs all operate in the same manner, they are collectively defined as a single spring 30. Reverse pressing actuator 25Pressure jack mechanismThe hydraulic pressure is adjusted by the pressure fluid from the transmission ratio means which is constituted by a pressure fluid jack having a cylinder, a plunger and a transmission ratio means and supplies a transmission ratio signal by a known transmission means 54 and a fluid positioner 53. It is an example shown by an actuator. The feature of this embodiment is that the characteristic line (A) shown in the stepped shape of FIG. 7 is not a stepped shape but a proportional operation of an accurate linear linear characteristic (A ′). The amount of inclination of the negative characteristic with respect to the rotational speed is changed from the transmission means 54 having a pump or the like to process the supply of hydraulic pressure, etc., from the speed ratio means of the positioner 53 which is a control device for detecting and servo-controlling the supply pressure state quantity, The pressure is determined by the pressure and area of the plunger 46 and the pressure chamber 45 as a pressure coupling body via 48 and the spring pressure of the elastic means 30. In addition, this pressurization mechanism can increase the pressurization speed from low speed to high speed, so that there is an advantage that the responsiveness is high and a large pressurizing force can be obtained. Further, when the internal combustion engine is rotationally input, it is also required to change the pressing force to the elastic means 30 by a control element other than the gear ratio signal in accordance with the fluctuation of the input rotational speed. A pressure detector 53a may be introduced to add cascade control along with the gear ratio.
[0041]
[Fourth embodiment]
  FIG. 10 shows a sectional view of the transmission wheel 1 of the fourth embodiment of the present invention. As in the case of FIG. 9, it is an example of the transmission wheel 1 having a pressure jack mechanism with a linear characteristic by a pressure fluid pump such as hydraulic pressure or pneumatic pressure and a gear ratio means. However, also in this case, if pressure fluid is supplied stepwise as in FIG. 4, stepwise pressurization characteristics are possible. Differences from the example of FIG. 9 are as follows. That is, (1) The member of the elastic means 30 is not a linear positive characteristic, but is a combination of a plurality of composites of conical annular leaf springs 59a and 59b. And (2) a pressure reverse jack actuator 25 fixed to the fixed body 10mechanismThe unit 60 is composed of a plunger 61 as a pressure connection body, a first interlocking connection body 56, and a second interlocking connection body 55. (3) A radial rotational force is separated by the bearing 5 between the elastic means 30 and the actuator 25. That is, the pressure fluid jack 60 is not rotated. The pressure fluid jack 60 with pump, cylinder and plunger is well known and will not be described in detail.
[0042]
[Fifth embodiment]
  FIG. 11 shows a sectional view of a transmission wheel 1 according to a fifth embodiment of the present invention. In this example, the shift actuator 25 is electricallyPressurizationA pressing unit 65 is used as an operating device for the servo-type reverse pressing actuator 25 to be controlled.With pressure jack mechanismAn integral operation shifter, that is, a first interlocking coupling body 66 that is integrated with a feed nut 28 as a pressure coupling body of the actuator 25 is applied to the elastic means 30 while being detachably assembled to the transmission main body 10 while being integrated. The second interlocking connecting body 55 is connected to the D-shaped cut surface 55a. The power of the reversible electric motor 62 and the gear head 63 is applied to the cam lead 70 and the trapezoidal screw, that is, the screw shaft 26 of the jack through the gear group 68, and the cam lead 70 changes the gear ratio by the position of the shifter 66. The signal is detected by a signal and supplied to the servo circuit 71. On the other hand, the screw shaft 26 moves up and down the shifter 66 and pressurizes and controls the elastic means 30 via the pressure coupling body 55. The actuator 25 further includes a control device that detects and servo-controls a state quantity with respect to the gear ratio, and an operating device that has a reversible electric motor 62 and a gearhead 63 to apply pressing force to the elastic means in response to the control command. It is an example which has. The sensor 54 detects a change in the state quantity, and externally controls the reversible electric motor 62 with the operation output of the control device through the amplitude discriminating circuit 71 and the switch energizing circuit 72 for the deviation from the fed back shifter position signal. Is.
[0043]
  In addition, when the transmission body 4 is replaced, if the reverse pressing actuator 25 is removed from the main body 10, there is a risk that the elastic body 30 that has been in a pressurized state until then is scattered. Therefore, the lid 77 is opened in advance and the connecting body 55 is pressed and cured by the auxiliary tool 75 having the screw 76 indicated by the broken line, and then the actuator 25 is attached and detached. The trapezoidal screw and the feed nut may be ball screws, and the reversible electric motor 62 and the gear head 63 may be pressure fluid motors such as hydraulic pressure.
[0044]
[Other Examples]
  Since the above embodiment is disclosed mainly for machine tools such as a milling machine and a drilling machine, the transmission is shown as a dry type used in an air atmosphere. However, in heavy machinery such as a vehicle, a wet type that transmits in an oil chamber is used. It is also easy to do. Actuators 6, 25Pressure jack mechanismAs shown, various types of manual and automatic types are also availablePressurizationA mechanism is conceivable. Furthermore, the elastic means 30 can be made into a can as shown in FIG. 5 because the elastic means 30 itself is made of a shape memory alloy material, and a mechanism for controlling the temperature with an actuator such as a heater is also possible. It is only necessary to obtain pressure characteristics. It is obvious that a person skilled in the art naturally installs a known shift power source 9 such as an electric reversible motor or pressure fluid motor and a gear ratio means in place of the handle 12 of FIG. This is an easily feasible range.
[0045]
  FIG. 12 is an explanatory view showing a combination form when the idea of the present invention is used in various aspects. The idea of the present invention is that the axial force applied to the first disc wheel 1a sliding in the axial direction through the reverse pressing actuator (ACT) 25 and the elastic means (ELS) 30 with the main body 10 as a reference position. It is controlled according to the gear ratio of the urging. Here, the main body refers to a body whose relative distance from the housing 10 does not change in the axial direction regardless of the presence or absence of rotational force. Accordingly, the presence or absence of a force in the rotational direction is irrelevant to the idea of the present invention, but in reality, the first disc wheel 1a is always rotating while the main body 10 serving as a reference is often fixed. For this reason, separation of rotational force is required, and the embodiment in the case of considering the relationship with the bearing 5 (BRG) is shown.
[0046]
  12A and 12E are examples of the cantilever support structure of the rotating shaft 20 of the transmission wheel 1, and FIGS. 12D and 12H are examples of the support structure of the both end bearings of the transmission wheel 1. FIG. In either case, the pressure wheel of the actuator 25 and the elastic means 30 are rotated together with the transmission wheel 1, and the main body 10 is also rotated but is fixed in the axial direction. The embodiment of FIG. 8 shows an example of FIG. (B), (C), (F) and (G) show examples in which the actuator 25 or the elastic means 30 is fixed to the non-rotating main body 10 with the bearing 5 interposed. The embodiment of FIG. 4 shows an example of FIG. 4F, and the embodiments of FIGS. 8, 10 and 11 all show the example of FIG.
[0047]
  FIG. 12 (I) is an example in which the pressing force of the shape memory alloy is controlled by heater control, and FIG. 12 (J) is an example in which the actuator 25 is separated into two. For example, in the embodiment of FIG. 4, the screw shaft 26a and the feed nut 27 form a second actuator (ACT-1) 25a that acts on the elastic means 30, and the screw shaft 26b and the feed nut 28 are first circles. In this example, the first actuator (ACT-2) 25b for shifting and sliding the plate wheel is formed, and the common screw shaft 26 and the jack body 24 are applied to each other. It shows that you can do it. As described above, the idea of the present invention is included in the idea of the present invention regardless of the presence or absence of the bearing (BRG) as long as the pressurizing force and the pressing force in the axial direction are superimposed in series and applied to the disc wheel 1a. Is done.
[0048]
【The invention's effect】
  According to the transmission wheel of the present invention, while using normal elastic means having a property of positive characteristics with respect to forward compression, the applied force generated by increasing / decreasing the elastic means is applied to the transmission wheel. By controlling the contact friction pressure between the transmission bodies, there is an advantage that the transmission wheel rotation shaft torque can be variably controlled continuously and applied to the transmission wheel according to an external command. . This means that a way has been opened for automatic control of industrial machines that require this variable control for the state quantity of transmission torque. In the present embodiment, this is adopted in an actuator that operates as a pressurizing characteristic in which the relationship between the rotation speed of the transmission wheel and the applied pressure is a negative pressure characteristic, and the transmission torque can be arbitrarily controlled from the outside as a result. Achieves a predetermined capacity of power transmission in the entire speed rangeRealized constant horsepower variable transmissionThere are advantages you can do. In particular, this indicates that the field of industrial machines to which transmissions using this type of transmission vehicle can be applied can be expanded from a special field to a wide field. At the same time, it becomes possible to realize a large-capacity transmission of several hundred horsepower [HP] or more, which has been considered impossible in the past, and contributes to labor saving and energy saving of the majority of industrial machinery.
[0049]
  Further, according to the present invention, even with a variable-diameter transmission wheel having the same diameter, any transmission torque can be secured independently by changing the pressurizing amount and pressing amount of the elastic means and the actuator. A transmission with a large transmission capacityTweakSelect arbitrarilyoperationTherefore, productivity according to the model is remarkably improved. At the same time, since the transmission efficiency of the transmission vehicle itself can be designed by arbitrarily controlling the pressure characteristics with respect to the gear ratio, high efficiency and high load transmission as a transmission can be achieved.
[0050]
  In conventional transmissions, the amount of pressure applied to the disc wheel is reduced at low speeds, so the transmission body is likely to be disturbed by the impact at the time of start-up, and the life of the transmission body is likely to be lost due to the number of times the transmission starts and stops. . However, in the present invention, since the transmission body is held by a large load in the low speed region, not only is there no damage due to starting and stopping, but also pressure is applied via elastic means, so the transmission body is stretched, worn, etc. Even in the case of error factors based on deterioration of the engine and disturbances such as sudden load fluctuations and fluctuations on the prime mover side, these are instantly absorbed in the entire range of the shift range and returned to the original state.MakeAutomatic alignmentPerform functionSo stable power transmissionMovementQuick with the machinevariableResponsivevariableControl mechanism is guaranteed.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a transmission using a conventional transmission wheel.
FIG. 2 is an operation explanatory diagram of a conventional transmission wheel.
FIG. 3 is a pressure characteristic diagram with respect to the number of rotations of elastic means applied to a disc wheel of a conventional transmission wheel.
FIG. 4 is a cross-sectional view of a transmission using a transmission wheel according to a first embodiment of the present invention.
FIG. 5 is an enlarged view of the elastic means shown in the first embodiment.
FIG. 6 is used in the transmission vehicle of the first embodiment.Worm transmission machineFIG.
FIG. 7 is a pressure characteristic diagram with respect to the number of rotations applied to the disc wheel of the transmission wheel of the first embodiment.
FIG. 8 is a sectional view of a transmission wheel according to a second embodiment of the present invention.
FIG. 9 is a sectional view of a transmission wheel according to a third embodiment of the present invention.
FIG. 10 is a sectional view of a transmission wheel according to a fourth embodiment of the present invention.
FIG. 11 is a sectional view of a transmission wheel according to a fifth embodiment of the present invention.
FIG. 12 is a conceptual explanatory diagram showing various combination modes as another embodiment of the present invention, and (A) to (J) all indicate combination modes.
[Explanation of symbols]
  1 Transmission vehicle or driven vehicle
  1a First disc car
  1b Second disc wheel
  2 Transmission vehicle or driving vehicle
  3,30 Elastic means
  4 Transmitter
  5 Bearing
  9 Shifting power supply source
  15 Screw shaft
  15a Pressure connector, connector or feed nut
10 Body
24 Jack or jack body
24a Worm transmission machine
24b, 24c Pressure mechanism or pressure jack mechanism
25 Actuator
25a firsttwoActuator
25b No.oneActuator
26a, 26b Thread groove or gear ratio means
27, 28 Pressure coupling body, coupling body or feed nut
46,61 Pressurized coupling body, coupling body or plunger
54 Transmission means

Claims (12)

First and second disc wheels are arranged opposite to each other coaxially with an axis of a rotation shaft supported by a main body, and the first disc wheel faces the second disc wheel. It is configured to be slidable in the axial direction in order to contract or extend the relative distance from the second disc wheel while being always given elastic pressure in the axial direction through elastic means arranged coaxially with In a transmission vehicle
And the elastic means of the positive characteristics increasing the pressurized pressure against compression, further sliding the the pressurized pressure applied via the connecting member from the elastic means to the first disc wheel above the rotational axis coaxial or parallel And an actuator for applying the elastic means by increasing / decreasing the elastic means in accordance with an external command with a pressing force generated by a dynamic displacement mechanism, and the elastic means is applied to at least the first disc wheel with respect to the main body. transmitted with the pressing force and to the mandrel direction superimposed in series above the transmission wheel by the pressurization control the first disc wheel above from the actuator with a reverse rotation prevention function of the external instruction given pressure A transmission wheel characterized in that contact friction pressure between the body and the body is variably increased and transmission torque is arbitrarily selected and imparted to the transmission wheel. First and second disc wheels are arranged opposite to each other coaxially with an axis of a rotation shaft supported by a main body, and the first disc wheel faces the second disc wheel. It is configured to be slidable in the axial direction in order to contract or extend the relative distance from the second disc wheel while being always given elastic pressure in the axial direction through elastic means arranged coaxially with In a transmission vehicle
The elastic means for increasing the pressure against forward compression, and the pressure applied to the first disc wheel via the connecting body to the elastic means is arbitrarily controlled and in series with the pressure. An actuator having a pressurizing mechanism arranged coaxially or in parallel with the rotating shaft for supplying the pressing force in the axial direction to the elastic means in accordance with the gear ratio or the number of rotations, and further preventing reverse rotation of the given external command And an operating device that gives the external command as urging power to the actuator, and the pressing force of the actuator is at least a relative distance between the first disc wheel and the second disc wheel, or Arbitrary transmission torque can be applied to the transmission wheel from the outside by applying the pressing force of the elastic means along the axial direction so as to be negative with respect to the rotational speed or positive with respect to the gear ratio. For the continuous grant Transmission wheel characterized in that the disc wheel variably and pressurization control. 3. The actuator according to claim 1, wherein the actuator includes a first actuator that slides and displaces a first displacement amount L1 of the first disc wheel according to a transmission gear ratio or a rotational speed, and the first actuator according to a transmission gear ratio or a rotational speed. The second actuator that presses and imparts the second displacement amount L2 to the elastic means is constituted by the above-described pressurizing mechanisms that are separate from each other using a jack and is energized by a separate or common transmission power supply source. Characteristic transmission vehicle. According to claim 1 or 2, the actuator includes a first displacement amount L1 sliding displacement of the first disc wheel above in accordance with the gear ratio or rotational speed, the elastic hand stages according to the gear ratio or rotational speed and a second displacement amount L2 for pressing granted transmission wheel, characterized in that the energized by each other the pressure-common grant vital in pressure mechanism transmit power source of a single common with the jack.   5. The actuator according to claim 3, wherein the actuator detects an amount of state corresponding to a gear ratio or a rotational speed and servo-controls the operating device with the external command, and the transmission vehicle in response to the control device. And a transmission vehicle controlled by the operating device of the variable speed power supply source, which is a reversible electric motor that applies pressing power to the elastic means or an externally controlled power source of a pressure fluid power source. First and second disc wheels are arranged opposite to each other coaxially with an axis of a rotation shaft supported by a main body, and the first disc wheel faces the second disc wheel. It is configured to be slidable in the axial direction in order to contract or extend the relative distance from the second disc wheel while being always given elastic pressure in the axial direction through elastic means arranged coaxially with In a transmission vehicle
The elastic means for increasing the pressure against forward compression, and a pressurizing mechanism comprising a jack for applying a pressing force according to the gear ratio or the rotational speed to the elastic means via a connecting body. The pressurizing mechanism is arranged coaxially or in parallel with the rotating shaft so that the pressing force of the pressing mechanism is applied in series to the pressing force of the elastic means and applied to the first disc wheel in the axial direction. An actuator, an operating device having a function of preventing reverse rotation of the given external command, and providing a variable speed power supply source as urging power to the actuator; and a control device for giving the external command for controlling the operating device; And the elastic means applies the pressurizing force to the first disc wheel on the basis of the main body with a negative characteristic with respect to the relative distance or the rotational speed or a positive characteristic with respect to the transmission ratio. Continuous transmission torque of transmission vehicle For variably imparting controlled externally from the control device transmission wheel, characterized in that pressurized first disc wheel above. 7. The actuator according to claim 6, wherein the jack presses and displaces the first actuator for slidingly displacing the first disc wheel according to a gear ratio or a rotational speed, and the elastic means according to the gear ratio or the rotational speed. transmission wheel characterized by having a worm and a worm wheel as the worm transfer machine for rotating the common screw shaft pressing force of each of the second actuator series composite to. 8. The actuator according to claim 7, wherein the screw shaft is formed such that the first screw groove for the first actuator and the second screw groove for the second actuator are opposite to each other. A transmission wheel characterized in that a first and a second connecting body are applied to the first and second thread grooves by a feed nut, and the elastic means is disposed between the main body and the actuator. 8. The actuator according to claim 7, wherein the screw shaft includes a first screw groove for sliding displacement of the first disc wheel and a second screw groove for pressing displacement of the elastic means . A transmission wheel formed in a screw groove in the same direction and applied with a single common connecting body by a feed nut, and the elastic means is disposed between the connecting body and the first disc wheel. . The actuator according to claim 8 or 9, wherein the actuator includes the connecting body formed of a feed nut, the nut and the screw shaft are formed of a trapezoidal screw or a ball screw, and the actuator includes the elastic means and the first disc wheel. A transmission wheel arranged between the screw shaft and the wheel so as to be finely movable in the axial direction. The actuator according to claim 8 or 9, wherein the connecting body is formed of a feed nut, the nut and a screw shaft are formed of a trapezoidal screw or a ball screw, and the actuator is disposed between the elastic means and the main body. A transmission wheel characterized in that it is disposed between the screw shaft and the wheel so as not to be finely movable in the axial direction. According to claim 5, 7, 10 or 11, the transmission wheel includes a transmission pressing actuator of the driven transmission wheel of the actuator and the drive-side transmission wheel which acts as a transmission opposite the pressing actuator, with coupling means and the shifting power supply A transmission vehicle characterized in that it is applied to the driven transmission vehicle of a continuously variable power transmission that is coupled and transmits an external command to the shift reverse press and shift press actuator via the connecting means.

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