JP4983301B2 - Transmission - Google Patents

Description

  The present invention relates to a transmission capable of shifting and transmitting power from an input shaft to an output shaft, and more particularly to a transmission including a continuously variable transmission mechanism capable of continuously changing a gear ratio.

  The related art of this type of transmission is disclosed in Patent Document 1 below. As shown in FIGS. 12 and 13, the transmission according to Patent Document 1 includes an input shaft 103 on the prime mover side, an output shaft 105 on the load side, and a belt type continuously variable transmission 107 having a pair of transmission pulleys 131 and 133. The first transmission mechanism 109 and the first clutch 117 disposed between the input shaft 103 and one transmission pulley 131, and the second transmission mechanism disposed between the input shaft 103 and the other transmission pulley 133. The transmission mechanism 111 and the second clutch 119, the third transmission mechanism 113 and the third clutch 121 disposed between the output shaft 105 and one transmission pulley 131, the output shaft 105 and the other transmission pulley 133. And a fourth transmission mechanism 115 and a fourth clutch 123 disposed between the two. The first and second speed change mechanisms 109 and 111 are composed of gears 171, 173, 175 and 177, and the third and fourth speed change mechanisms 113 and 115 are composed of gears 183, 185 and 187. Yes. The belt type continuously variable transmission 107 can continuously change the speed ratio within the range of the minimum speed ratio 1 / RM or more and the maximum speed ratio RM or less, and the speed ratio of the first speed change mechanism 109 becomes RM. The gear ratio of the second transmission mechanism 111 is set to 1 / RM. The transmission ratios of the third and fourth transmission mechanisms 113 and 115 are set to be equal to each other.

In a state where the second and third clutches 119 and 121 are engaged and the first and fourth clutches 117 and 123 are released, the power is transmitted to the second transmission mechanism 111, the transmission pulley 133, Transmission is performed in the order of the transmission pulley 131 and the third transmission mechanism 113. If the gear ratio of the belt type continuously variable transmission 107 is changed from 1 / RM to RM in this state, the gear ratio of the entire transmission changes from 1 / RM ² to 1. On the other hand, in the state where the first and fourth clutches 117 and 123 are engaged and the second and third clutches 119 and 121 are disengaged, as shown in FIG. 13, the motive power is the first transmission mechanism 109, the transmission pulley. 131, transmission pulley 133, and fourth transmission mechanism 115 are transmitted in this order. That is, the input / output (power transmission direction) of the belt type continuously variable transmission 107 is reversed. When the gear ratio of the belt type continuously variable transmission 107 is changed from 1 / RM to RM in this state, the gear ratio of the entire transmission is changed from 1 to RM ^2. As a result, the transmission ratio of the whole transmission is wider transmission band than the belt-type continuously variable transmission 107 single shift range ^{1 / RM~RM 1 / RM 2 ~RM} 2 is obtained.

  As another related technique, a transmission according to Patent Document 2 below is disclosed.

JP 7-293663 A JP 2001-343059 A

  In Patent Document 1 (configuration shown in FIGS. 12 and 13), in order to increase the variable range of the gear ratio, input / output (power transmission direction) of only the continuously variable transmission (belt type continuously variable transmission 107) is provided. It has been replaced. However, in that case, between the input shaft 103 and one transmission pulley 131, between the input shaft 103 and the other transmission pulley 133, between the output shaft 105 and one transmission pulley 131, and between the output shaft 105 and It is necessary to provide transmission mechanisms 109, 111, 113, and 115 between the other transmission pulley 133. As a result, the overall structure of the transmission is increased.

  It is an object of the present invention to provide a transmission that can widen the variable range of the transmission ratio and realize downsizing.

  The transmission according to the present invention employs the following means in order to achieve the above-described object.

The transmission according to the present invention is a transmission capable of shifting and transmitting power from an input shaft to an output shaft, and includes a first rotation element and a second rotation that rotates in conjunction with the first rotation element. An infinitely variable transmission mechanism capable of continuously changing a gear ratio between the first rotating element and the second rotating element, a third rotating element coupled to the second rotating element, A transmission mechanism that includes a fourth rotation element that rotates in conjunction with the third rotation element, and that is capable of shifting and transmitting power between the third rotation element and the fourth rotation element; An input-side switching mechanism that selectively connects to the first rotating element and the fourth rotating element; and an output-side switching mechanism that selectively connects the output shaft to the first rotating element and the fourth rotating element. If the transmitting power to the output shaft from the axis, connecting the input shaft through the input-side switching mechanism to the first rotating element and A first speed change mode for changing the speed ratio of the continuously variable transmission mechanism in a state of connecting the output shaft to the fourth rotary element by a force-side switching mechanism connects the input shaft to the fourth rotary element by the input-side switching mechanism and the output A second speed change mode in which the speed ratio of the continuously variable transmission mechanism is changed in a state where the output shaft is connected to the first rotation element by the side switching mechanism, and the input shaft is connected to the first rotation element by the input side switching mechanism and the output side A direct connection mode in which the output shaft is connected to the first rotating element by the switching mechanism, or the input shaft is connected to the fourth rotating element by the input side switching mechanism, and the output shaft is connected to the fourth rotating element by the output side switching mechanism; The rotation element connected to the input shaft for the input side switching mechanism is switched from the first rotation element to the fourth rotation element, and the rotation element connected to the output shaft for the output side switching mechanism is changed from the fourth rotation element to the fourth rotation element. 1 By switching on the rolling element, it is summarized in that switching from the first shift mode to the second shift mode.

According to the present invention, the first transmission mode and the second transmission mode are selectively switched so that the continuously variable transmission mechanism and the transmission mechanism that transmits and transmits power are connected in series with the input / output (power) of the transmission mechanism. By changing the transmission direction), the variable range of the transmission ratio of the entire transmission can be made wider than the variable range of the transmission ratio of the continuously variable transmission mechanism alone, and the number of transmission mechanisms provided between the input shaft and the output shaft Can be reduced. Therefore, it is possible to widen the variable range of the gear ratio of the entire transmission, and it is possible to reduce the size of the entire transmission. Furthermore, by switching to the direct connection mode, power can be transmitted from the input shaft to the output shaft without using a continuously variable transmission mechanism, so that power transmission efficiency can be improved.

In one aspect of the present invention, the continuously variable transmission mechanism has a speed ratio γcvt from the first rotating element to the second rotating element in the range of 1 / γ ₁ or more and γ ₂ or less (γ ₁ × γ ₂ > 1). It is a mechanism that can be continuously changed, and the gear ratio γ ₃ from the third rotating element to the fourth rotating element of the transmission mechanism is
γ ₃ ≠ 1 and 1 / γ ₂ ≦ γ ₃ ≦ γ ₁
It is preferable that the value is set to satisfy. As a result, the speed ratio of the entire transmission can be continuously changed within the range of the minimum speed ratio and the maximum speed ratio. Here, γ ₁ = γ ₂ may be satisfied, or γ ₁ ≠ γ ₂ may be satisfied.

In one aspect of the present invention, it is preferable that the speed ratio γ ₃ from the third rotating element to the fourth rotating element of the transmission mechanism is set to 1 / γ ₂ or γ ₁ . Thereby, the variable range of the gear ratio of the entire transmission can be further expanded.

In one aspect of the present invention, in the first speed change mode, when the speed ratio γcvt from the first rotation element to the second rotation element of the continuously variable transmission mechanism is substantially equal to 1 / γ ₃ , the second speed change mode is set. It is preferable to switch. As a result, vibration and shock when switching from the first shift mode to the second shift mode can be reduced.

In one aspect of the present invention, in the second speed change mode, when the speed ratio 1 / γcvt from the second rotation element to the first rotation element of the continuously variable transmission mechanism is substantially equal to γ ₃ , the first speed change mode is set. It is preferable to switch. As a result, vibration and shock when switching from the second shift mode to the first shift mode can be reduced.

  In one aspect of the present invention, the continuously variable transmission mechanism further includes a belt wound around the first pulley and the second pulley, wherein the first rotating element and the second rotating element are a first pulley and a second pulley, respectively. A mechanism that changes the gear ratio between the first pulley and the second pulley by changing the diameter of the belt on the first pulley and the second pulley is preferable.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings.

“Embodiment 1”
1 and 2 are diagrams showing a schematic configuration of a transmission according to Embodiment 1 of the present invention, FIG. 1 shows a conceptual diagram, and FIG. 2 shows a side view. The transmission according to the present embodiment includes an input shaft 12 on the prime mover side, an output shaft 22 on the load side, a continuously variable transmission 14, a transmission mechanism 16 connected in series to the continuously variable transmission 14, and an input shaft. 12 is selectively connected to the continuously variable transmission 14 and the transmission mechanism 16, and the output side switching mechanism 20 is configured to selectively connect the output shaft 22 to the continuously variable transmission 14 and the transmission mechanism 16. And comprising. The transmission according to the present embodiment can shift the power from the prime mover transmitted to the input shaft 12 and transmit it to the output shaft 22 (load). Note that the transmission according to the present embodiment can be mounted on, for example, a vehicle, and the power transmitted to the output shaft 22 is transmitted to driving wheels (not shown) via, for example, a differential gear 15 so that the vehicle Used for driving.

  The continuously variable transmission 14 includes a primary pulley (first rotating element) 30 connected to the first pulley shaft 24, a secondary pulley (second rotating element) 32 connected to the second pulley shaft 26, and the primary pulley 30. And a belt-type continuously variable transmission including an endless belt 34 wound around the secondary pulley 32. The rotation center of the first pulley shaft 24 (the rotation center of the primary pulley 30) coincides with the rotation center of the input shaft 12, and the second pulley shaft 26 is arranged in parallel with the first pulley shaft 24 (input shaft 12). ing. The output shaft 22 is parallel to the first pulley shaft 24 and the second pulley shaft 26, and is disposed between the first pulley shaft 24 and the second pulley shaft 26.

  The primary pulley 30 includes a primary movable sheave 30 a and a primary fixed sheave 30 b that can move along the axial direction of the first pulley shaft 24, and the secondary pulley 32 is configured in the axial direction of the second pulley shaft 26. The secondary movable sheave 32a and the secondary fixed sheave 32b that can move along The endless belt 34 is sandwiched between the primary movable sheave 30a and the primary fixed sheave 30b and between the secondary movable sheave 32a and the secondary fixed sheave 32b. The rotation of the primary pulley 30 is transmitted to the secondary pulley 32 via the endless belt 34, and the secondary pulley 32 rotates in conjunction with the rotation of the primary pulley 30.

  The primary movable sheave 30a moves along the axial direction of the first pulley shaft 24 and the secondary movable sheave 32a moves along the axial direction of the second pulley shaft 26 by the hydraulic pressure supplied to the primary pulley 30 and the secondary pulley 32. As a result, the rotation radius (belt engagement diameter) of the portion where the endless belt 34 is wound around the primary pulley 30 and the secondary pulley 32 changes steplessly. Thereby, the gear ratio between the primary pulley 30 and the secondary pulley 32 changes continuously.

FIG. 2 shows an example in which the variable range of the engagement diameter of the endless belt 34 to the secondary pulley 32 is set equal to the variable range of the engagement diameter of the endless belt 34 to the primary pulley 30. In this example, the continuously variable transmission 14 sets the value of γcvt to 1 / where the gear ratio from the primary pulley 30 to the secondary pulley 32 (rotational speed Np of the primary pulley 30 / rotational speed Ns of the secondary pulley 32) is γcvt. It can be continuously changed within the range of γ ₁ or more and γ ₁ or less (γ ₁ > 1). In other words, the input / output (power transmission direction) of the continuously variable transmission 14 is reversed, in other words, the gear ratio from the secondary pulley 32 to the primary pulley 30 (the rotational speed Ns of the secondary pulley 32 / the rotational speed Np of the primary pulley 30). Is 1 / γcvt, and the value of 1 / γcvt can also be continuously changed within the range of 1 / γ ₁ or more and γ ₁ or less.

  The transmission mechanism 16 has a pair of transmission gears 44 and 46 that mesh with each other, and the transmission gear (fourth rotation element) 46 rotates in conjunction with the rotation of the transmission gear (third rotation element) 44. Here, the transmission mechanism 16 is a gear transmission mechanism capable of shifting and transmitting power between the transmission gear 44 and the transmission gear 46. The transmission gear 44 is connected to the secondary pulley 32 via the second pulley shaft 26, so that the transmission mechanism 16 is connected in series to the continuously variable transmission 14. The rotation center of the transmission gear 44 coincides with the rotation center of the second pulley shaft 26 (the rotation center of the secondary pulley 32), and the rotation center of the transmission gear 46 coincides with the rotation center of the output shaft 22.

In FIG. 2, the outer diameter (pitch circle diameter) of the transmission gear 46 is set to be larger than the outer diameter (pitch circle diameter) of the transmission gear 44, and the gear ratio from the transmission gear 44 to the transmission gear 46 ( When the rotational speed Nc) a gamma ₃ of the rotation speed Ns / transmission gear 46 of the transmission gear 44, the value of the gamma ₃ is an example that has been set to a value greater than 1. Here, the value of γ ₃ is set to γ ₁ . Therefore, the transmission mechanism 16 functions as a speed reduction mechanism that decelerates and transmits power when the power transmission direction is the direction from the speed change gear 44 to the speed change gear 46. In other words, the input / output (power transmission direction) of the transmission mechanism 16 is reversed, in other words, the gear ratio from the gear 46 to the gear 44 (the rotational speed Nc of the gear 46 / the rotational speed of the gear 44). Ns) is 1 / γ ₃ , and the value of 1 / γ ₃ is set to a value smaller than 1 (1 / γ ₁ ). Therefore, the transmission mechanism 16 functions as a speed increasing mechanism that speeds up and transmits power when the power transmission direction is from the speed change gear 46 to the speed change gear 44.

  The rotation center of the gear 47 coincides with the rotation center of the first pulley shaft 24 and meshes with the transmission gear 46 of the transmission mechanism 16. The outer diameter (pitch circle diameter) of the gear 47 is set equal to the outer diameter (pitch circle diameter) of the transmission gear 46, and the transmission ratio from the gear 47 to the transmission gear 46 is set to 1. The gear 48 is connected to the primary pulley 30 via the first pulley shaft 24, and the rotation center thereof coincides with the rotation center of the first pulley shaft 24. The rotation center of the gear 49 coincides with the rotation center of the output shaft 22 and meshes with the gear 48. The outer diameter (pitch circle diameter) of the gear 48 is set equal to the outer diameter (pitch circle diameter) of the gear 49, and the gear ratio from the gear 48 to the gear 49 is set to 1.

  The input side switching mechanism 18 has clutches C1 and C2. The clutch C1 can selectively connect and release the input shaft 12 and the gear 47 by switching the engagement / release. The clutch C2 can selectively connect and release the input shaft 12 and the first pulley shaft 24 by switching the engagement / release. The input shaft 12 can be connected to the primary pulley 30 via the first pulley shaft 24 by engaging the clutch C2 and releasing the clutch C1. On the other hand, by engaging the clutch C1 and releasing the clutch C2, the input shaft 12 can be connected to the transmission gear 46 via the gear 47. In this way, the input side switching mechanism 18 switches the clutch to be engaged from among the clutches C1 and C2, so that the input shaft 12 is connected to the primary pulley 30 of the continuously variable transmission 14 and the transmission gear 46 of the transmission mechanism 16. Can be selectively linked.

  The output side switching mechanism 20 has clutches C3 and C4. The clutch C3 can selectively connect and release the output shaft 22 and the transmission gear 46 by switching the engagement / release. The clutch C4 can selectively connect and release the output shaft 22 and the gear 49 by switching the engagement / release. By engaging the clutch C3 and releasing the clutch C4, the output shaft 22 can be connected to the transmission gear 46. On the other hand, by engaging the clutch C4 and releasing the clutch C3, the output shaft 22 can be connected to the primary pulley 30 via the gears 49, 48 and the first pulley shaft 24. As described above, the output side switching mechanism 20 switches the clutch to be engaged from the clutches C3 and C4, so that the output shaft 22 is connected to the primary pulley 30 of the continuously variable transmission 14, the transmission gear 46 of the transmission mechanism 16, and the like. Can be selectively linked.

  The reverse gear 50 has its rotation center coincident with the rotation center of the second pulley shaft 26 and meshes with the reverse idler gear 51. The reverse idler gear 51 rotates in conjunction with the rotation of the output shaft 22. The clutch C5 can selectively connect and release the second pulley shaft 26 and the reverse gear 50 by switching the engagement / release. By engaging the clutch C <b> 5, the rotation of the secondary pulley 32 is transmitted to the output shaft 22 with the reverse direction reversed by the reverse gear 50 and the reverse idler gear 51.

  Note that the control of the transmission ratio of the continuously variable transmission 14 and the switching of the engagement / release of the clutches C1, C2, C3, C4, and C5 are performed by an electronic control unit (not shown).

  Next, in the operation of the transmission according to the present embodiment, particularly when power is transmitted from the input shaft 12 to the output shaft 22 (from the prime mover to the load), the speed ratio of the entire transmission (the rotational speed Nin of the input shaft 12). The operation of changing the rotational speed Nout) γt of the output shaft 22 will be described.

First, the operation when the speed ratio γt of the entire transmission is reduced from the maximum speed ratio will be described. In that case, for the input side switching mechanism 18, the clutch C2 is controlled to be in the engaged state and the clutch C1 is in the released state, and for the output side switching mechanism 20, the clutch C3 is controlled to be in the engaged state and the clutch C4 is in the released state. The clutch C5 is controlled to the released state. That is, the input shaft 12 is connected to the primary pulley 30 of the continuously variable transmission 14 and the output shaft 22 is controlled to be connected to the transmission gear 46 of the transmission mechanism 16. Then, in order to control the speed ratio γt of the entire transmission to the maximum speed ratio, and controls the transmission ratio of the continuously variable transmission 14 Ganmacvt (transmission ratio from the primary pulley 30 toward the secondary pulley 32) to the maximum speed ratio gamma ₁ . Hereinafter, the clutches C2, C3 are engaged and the clutches C1, C4, C5 are disengaged (the input shaft 12 is connected to the primary pulley 30 and the output shaft 22 is connected to the transmission gear 46). A transmission mode in which the transmission ratio of the step transmission 14 is changed is referred to as a first transmission mode.

In the first speed change mode, as shown in FIG. 3, the power from the prime mover transmitted to the input shaft 12 is transmitted to the primary pulley 30 of the continuously variable transmission 14 via the clutch C2. The power transmitted to the primary pulley 30 is shifted at a gear ratio γcvt, transmitted to the secondary pulley 32, and transmitted to the transmission gear 44 of the transmission mechanism 16. The power transmitted to the transmission gear 44 of the transmission mechanism 16 is shifted (decelerated) at a transmission gear ratio γ ₃ (= γ ₁ ), transmitted to the transmission gear 46, and transmitted to the output shaft 22 via the clutch C3. The The power transmitted to the output shaft 22 is transmitted to driving wheels (not shown) via the differential gear 15 and used for forward driving of the vehicle. Thus, in the first speed change mode, the power transmission direction of the transmission is a direction from the continuously variable transmission 14 to the transmission mechanism 16, and the power transmission direction of the continuously variable transmission 14 is from the primary pulley 30 to the secondary pulley 32. The power transmission direction of the transmission mechanism 16 is from the transmission gear 44 to the transmission gear 46. Since the transmission ratio γt of the entire transmission is γcvt × γ _1, the gear ratio Ganmacvt of the continuously variable transmission 14 to control the maximum gear ratio gamma _1, the maximum transmission ratio the transmission ratio γt of the entire transmission It can be controlled to γ ₁ ² .

In the first speed change mode, the Ganmacvt (transmission ratio from the primary pulley 30 toward the secondary pulley 32) gear ratio of the continuously variable transmission 14 in response to decrease from the maximum gear ratio gamma _1, the overall transmission speed ratio γt (= Γcvt × γ ₁ ) also decreases from the maximum gear ratio γ ₁ ² . Then, when the gear ratio γcvt of the continuously variable transmission 14 is the minimum speed ratio 1 / gamma _1, gear ratio γt of the entire transmission becomes 1. For this reason, in the first speed change mode, the speed change ratio γcvt of the continuously variable transmission 14 is continuously changed within the range of the minimum speed change ratio 1 / γ ₁ or more and the maximum speed ratio γ ₁ or less. The speed ratio γt can be continuously changed within a range of 1 or more and γ ₁ ² (= γ ₃ ² ) or less.

  When the transmission ratio γt of the entire transmission is controlled to a value of 1 or less, the clutch to be engaged is switched to switch the transmission mode. In that case, with respect to the input side switching mechanism 18, the clutch to be engaged is switched from the clutch C2 to the clutch C1, and the clutch C1 is controlled to be in the engaged state and the clutch C2 is in the released state. The clutch to be engaged is switched from the clutch C3 to the clutch C4, and the clutch C4 is controlled to be engaged and the clutch C3 is controlled to be released. In other words, the input shaft 12 is connected to the transmission gear 46 of the transmission mechanism 16 and the output shaft 22 is controlled to be connected to the primary pulley 30 of the continuously variable transmission 14. Hereinafter, the clutches C1, C4 are engaged and the clutches C2, C3, C5 are disengaged (the input shaft 12 is connected to the transmission gear 46 and the output shaft 22 is connected to the primary pulley 30). A transmission mode in which the transmission ratio of the step transmission 14 is changed is referred to as a second transmission mode.

In the first speed change mode (the state shown in FIG. 3), when the speed ratio γcvt of the continuously variable transmission 14 is equal to the minimum speed ratio 1 / gamma _1, that is, when the gear ratio γt of the entire transmission is 1, input The rotational speed Nin of the shaft 12 and the rotational speed Nout of the output shaft 22 are equal. At this time, the rotational speed is the same between the input shaft 12 and the gear 47 (transmission gear 46), and the rotational speed is the same between the output shaft 22 and the gear 49 (primary pulley 30). Therefore, in the first speed change mode, the speed ratio (speed ratio from the primary pulley 30 to the secondary pulley 32) γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) the minimum speed ratio 1 / γ ₁ (= 1 / γ ₃ ). When the clutch to be engaged is switched from the clutches C2 and C3 to the clutches C1 and C4, slippage of the clutches C1 and C4 can be suppressed, and vibration can be suppressed.・ Shock can be reduced.

In the second speed change mode, as shown in FIG. 4, the power from the prime mover transmitted to the input shaft 12 is transmitted to the speed change gear 46 of the transmission mechanism 16 via the clutch C <b> 1 and the gear 47. The power transmitted to the speed change gear 46 is changed (accelerated) at a speed change ratio 1 / γ ₃ (= 1 / γ ₁ ) and transmitted to the speed change gear 44 to the secondary pulley 32 of the continuously variable transmission 14. Communicated. The power transmitted to the secondary pulley 32 is shifted at a gear ratio 1 / γcvt, transmitted to the primary pulley 30, and transmitted to the output shaft 22 via the gears 48 and 49 and the clutch C4. Thus, in the second speed change mode, the power transmission direction of the transmission is a direction from the transmission mechanism 16 toward the continuously variable transmission 14, and the power transmission direction of the continuously variable transmission 14 is from the secondary pulley 32 to the primary pulley 30. The power transmission direction of the transmission mechanism 16 is from the transmission gear 46 to the transmission gear 44. That is, in the second speed change mode, the input / output (power transmission direction) of the continuously variable transmission 14 and the transmission mechanism 16 is reversed from the first speed change mode. Since the gear ratio γt of the entire transmission is 1 / (γcvt × γ ₁ ), the gear ratio of the continuously variable transmission 14 (the gear ratio from the secondary pulley 32 to the primary pulley 30) 1 / γcvt is the maximum gear ratio. When γ ₁ , the gear ratio γt of the entire transmission is 1.

In the second speed change mode, the speed ratio of the continuously variable transmission 14 to 1 / γcvt (gear ratio from the secondary pulley 32 toward the primary pulley 30) in response to decrease from the maximum gear ratio gamma _1, shift of the entire transmission The ratio γt (= 1 / (γcvt × γ ₁ )) decreases from 1. When the speed ratio 1 / γcvt of the continuously variable transmission 14 is the minimum speed ratio 1 / γ ₁ , the speed ratio γt of the entire transmission becomes the minimum speed ratio 1 / γ ₁ ² . Therefore, in the second speed change mode, the speed change ratio 1 / γcvt of the continuously variable transmission 14 is continuously changed within the range of the minimum speed change ratio 1 / γ ₁ or more and the maximum speed ratio γ ₁ or less. The overall gear ratio γt can be continuously changed within a range of 1 / γ ₁ ² or more and 1 or less.

Minimum Moreover, when increasing the speed ratio γt of the entire transmission from the minimum speed ratio 1 / gamma ₁ ^2, in the second speed change mode (the state shown in FIG. 4), the gear ratio 1 / γcvt of the continuously variable transmission 14 The transmission ratio is increased from 1 / γ ₁ . When the speed ratio 1 / γcvt of the continuously variable transmission 14 is the maximum speed ratio γ ₁ , the speed ratio γt of the entire transmission becomes 1, and the rotational speed Nin of the input shaft 12 and the rotational speed of the output shaft 22 Nout becomes equal. At this time, the input shaft 12 and the primary pulley 30 have the same rotational speed, and the output shaft 22 and the transmission gear 46 have the same rotational speed. Therefore, in the second speed change mode, the speed ratio of the continuously variable transmission 14 (speed ratio from the secondary pulley 32 to the primary pulley 30) 1 / γcvt is equal to (or substantially equal to) the maximum speed ratio γ ₁ (= γ ₃ ). When the clutch to be engaged is switched from the clutch C1, C4 to the clutch C2, C3, the slippage of the clutch C2, C3 is suppressed by switching to the first speed change mode (the state shown in FIG. 3). Vibration and shock can be reduced. In the first speed change mode, as described above, the speed ratio (speed ratio from the primary pulley 30 to the secondary pulley 32) γcvt of the continuously variable transmission 14 is set to the minimum speed ratio 1 / γ ₁ or more and the maximum speed ratio γ. by continuously changing within a range of ₁ or less, it is possible to continuously change the gear ratio γt of the entire transmission within 1 or more and gamma ₁ ² or less. As described above, in the present embodiment, by selectively switching between the first speed change mode and the second speed change mode, the speed change ratio γt of the entire transmission is reduced to the minimum speed change ratio 1 / γ ₁ ² (= 1 / γ ₃ ^2. ) And can be continuously changed within the range of the maximum gear ratio γ ₁ ² (= γ ₃ ² ) or less.

  In the present embodiment, power can be transmitted from the input shaft 12 to the output shaft 22 without shifting by the continuously variable transmission 14. In that case, for the input side switching mechanism 18, the clutch C1 is controlled to be engaged and the clutch C2 is controlled to be released, and for the output side switching mechanism 20, the clutch C3 is controlled to be engaged and the clutch C4 is controlled to be released. The clutch C5 is controlled to the released state. That is, both the input shaft 12 and the output shaft 22 are controlled to be connected to the speed change gear 46 of the transmission mechanism 16. Hereinafter, a state in which the clutches C1 and C3 are engaged and the clutches C2, C4, and C5 are released (a state in which the input shaft 12 and the output shaft 22 are connected to the transmission gear 46) is referred to as a direct connection mode.

In the direct connection mode, as shown in FIG. 5, the power from the prime mover transmitted to the input shaft 12 is transmitted to the transmission gear 46 of the transmission mechanism 16 via the clutch C <b> 1 and the gear 47. The power transmitted to the transmission gear 46 is transmitted to the output shaft 22 via the clutch C3. Since the speed ratio from the gear 47 to the speed change gear 46 is set to 1, in the direct connection mode, the speed ratio γt of the entire transmission is 1 and power is not shifted from the input shaft 12 to the output shaft 22. Communicated. Therefore, in the first speed change mode, the speed ratio (speed ratio from the primary pulley 30 to the secondary pulley 32) γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) the minimum speed ratio 1 / γ ₁ (= 1 / γ ₃ ). It is also possible to switch to the direct connection mode. As a result, power can be transmitted from the input shaft 12 to the output shaft 22 without using the continuously variable transmission 14, and power transmission efficiency can be improved. Further, when the clutch to be engaged is switched from the clutch C2 to the clutch C1, it is possible to prevent the clutch C1 from slipping and to reduce vibrations and shocks. In the second speed change mode, the speed ratio of the continuously variable transmission 14 (speed ratio from the secondary pulley 32 to the primary pulley 30) 1 / γcvt is equal to (or substantially equal to) the maximum speed ratio γ ₁ (= γ ₃ ). Sometimes it is possible to switch to direct connection mode. Thereby, power transmission efficiency can be improved. Further, when the clutch to be engaged is switched from the clutch C4 to the clutch C3, it is possible to prevent the clutch C3 from slipping and to reduce vibration and shock.

  However, in this embodiment, when switching to the direct connection mode, the clutches C2 and C4 are controlled to be engaged and the clutches C1, C3 and C5 are controlled to be disengaged, that is, both the input shaft 12 and the output shaft 22 are controlled to the gear 48. It can also be controlled to be connected to the (primary pulley 30). In the direct connection mode in which the input shaft 12 and the output shaft 22 are connected to the primary pulley 30, the power from the prime mover transmitted to the input shaft 12 is output to the output shaft 22 via the clutch C2, the gears 48 and 49, and the clutch C4. Is transmitted to. Since the gear ratio from the gear 48 to the gear 49 is set to 1, the gear ratio γt of the entire transmission device is 1, and the power is transmitted from the input shaft 12 to the output shaft 22 without being shifted.

  Further, when power is transmitted from the input shaft 12 to the output shaft 22 with the rotation direction reversed, the clutches C2 and C5 are controlled to be in an engaged state and the clutches C1, C3 and C4 are controlled to be in a released state. That is, the input shaft 12 is connected to the primary pulley 30 and the output shaft 22 is controlled to be connected to the secondary pulley 32 via the reverse idler gear 51 and the reverse gear 50. Hereinafter, this state is referred to as a reverse mode.

  In the reverse mode, as shown in FIG. 6, the power from the prime mover transmitted to the input shaft 12 is transmitted to the primary pulley 30 of the continuously variable transmission 14 via the clutch C2. The power transmitted to the primary pulley 30 is shifted at a gear ratio γcvt, transmitted to the secondary pulley 32, and transmitted to the reverse gear 50 via the clutch C5. The power transmitted to the reverse gear 50 is transmitted to the output shaft 22 through the reverse idler gear 51 with the rotation direction reversed. The power transmitted to the output shaft 22 is transmitted to drive wheels (not shown) via the differential gear 15 and used for driving the vehicle backward. In the reverse mode, the gear ratio γt of the entire transmission is γcvt × γr, where γr is the gear ratio from the reverse gear 50 to the reverse idler gear 51.

  In each operation (mode) of the present embodiment described above, the gear ratio of the continuously variable transmission 14, the gear ratio of the transmission mechanism 16, the gear ratio of the entire transmission, and the clutches C1, C2, C3, C4, and C5. The table below summarizes the merge / release. However, in the following table, the forward direction represents the direction from the primary pulley 30 to the secondary pulley 32 in the continuously variable transmission 14, the direction from the transmission gear 44 to the transmission gear 46 in the transmission mechanism 16, and the reverse direction represents In the continuously variable transmission 14, the direction from the secondary pulley 32 to the primary pulley 30, and in the transmission mechanism 16, the direction from the transmission gear 46 to the transmission gear 44. ◯ represents engagement of the clutch, and x represents release of the clutch. As described above, in the present embodiment, when power is transmitted from the input shaft 12 to the output shaft 22, the first shift mode, the second shift mode, the direct connection mode, and the reverse mode can be selectively switched.

In the present embodiment described above, the first transmission mode and the second transmission mode are selectively switched so that the continuously variable transmission 14 and the transmission mechanism 16 that transmits and transmits power are connected in series. By switching the input / output (power transmission direction), the variable range of the gear ratio γt of the entire transmission can be made wider than the variable range of the gear ratio γcvt of the continuously variable transmission 14 alone. However, in order to widen the variable range of the gear ratio γt by switching the input and output of the continuously variable transmission 14, a transmission mechanism that shifts and transmits power in both the first speed change mode and the second speed change mode. The power transmission path between the input shaft 12 and the output shaft 22 needs to be arranged. On the other hand, in the present embodiment, not only the continuously variable transmission 14 but also the input / output of the transmission mechanism 16 connected in series with the continuously variable transmission 14 is switched, so that the power between the input shaft 12 and the output shaft 22 is changed. The transmission mechanism provided in the transmission path can be shared between the first transmission mode and the second transmission mode, and the number of transmission mechanisms can be reduced. Therefore, according to this embodiment, the variable range of the gear ratio of the entire transmission can be widened, and the overall configuration of the transmission can be reduced in size. Further, in the present embodiment, the transmission gear ratio γ ₃ from the transmission gear 44 to the transmission gear 46 of the transmission mechanism 16 is set to γ ₁ , so that the transmission gear ratio γt of the entire transmission device is set to the minimum transmission ratio 1 / γ _1. ^While being able to change continuously within the range of ² or more and the maximum gear ratio γ ₁ ² or less, the variable range of the gear ratio γt can be further expanded.

  In Patent Document 1, the second and third clutches 119 and 121 are engaged and the first and fourth clutches 117 and 123 are released (the state shown in FIG. 12), and the first and fourth clutches When the clutches 117 and 123 are engaged and the second and third clutches 119 and 121 are released selectively (the state shown in FIG. 13), the clutch slips. When switching from the state shown in FIG. 12 to the state shown in FIG. 13, the first clutch 117 slips. When switching from the state shown in FIG. 13 to the state shown in FIG. 12, the second clutch 119 slips. Arise. For example, under the conditions of RM = 2 and the rotational speed of the input shaft 103 = 3000 rpm, as shown in the table below, the first clutch 117 needs to absorb a rotational difference of 1500 rpm, and the second clutch 119 rotates at 3000 rpm. It is necessary to absorb the difference. Therefore, when switching the clutch to be engaged, vibration and shock are likely to occur, and the durability of the clutches 117 and 119 is also likely to be reduced.

  On the other hand, in the present embodiment, when the clutch to be engaged is switched to selectively switch between the first shift mode and the second shift mode, the rotational speed Nin of the input shaft 12 and the rotational speed Nout of the output shaft 22 are selected. Since the input and output of the speed change mechanism can be interchanged in the state where the two are equal (or substantially equal), it is possible to prevent the clutches C1, C2, C3 and C4 from slipping. Therefore, vibrations and shocks can be reduced when the transmission mode is switched, and the durability of the clutches C1, C2, C3, and C4 can be improved.

  Further, in the present embodiment, by selecting the direct connection mode, power transmission can be performed from the input shaft 12 to the output shaft 22 without using the continuously variable transmission 14, so that power transmission efficiency can be improved. . Further, when the direct connection mode is selected, the mode can be switched to the direct connection mode when the rotational speed Nin of the input shaft 12 and the rotational speed Nout of the output shaft 22 are equal (or substantially equal). Therefore, vibration and shock can be reduced when switching to the direct connection mode.

In the first embodiment, the speed ratio γ ₃ from the speed change gear 44 to the speed change gear 46 in the transmission mechanism 16 may be set to a value different from γ ₁ . For example, the speed ratio γ ₃ from the speed change gear 44 to the speed change gear 46 can be set to a value larger than _{1 and} smaller than γ ₁ . In this case, by selectively switching between the first speed change mode and the second speed change mode, the speed change ratio γt of the entire transmission is set to a minimum speed change ratio 1 / (γ ₁ × γ ₃ ) or more and the maximum speed change ratio γ ₁ × It can be continuously changed within a range of γ ₃ or less. In the first speed change mode, when the speed ratio γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) 1 / γ ₃ , slipping occurs in the clutches C1 and C4 by switching to the second speed change mode. Can be suppressed. Further, in the second speed change mode, when the speed ratio 1 / γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) γ ₃ , slipping occurs in the clutches C2 and C3 by switching to the first speed change mode. Can be suppressed. Further, in the first speed change mode, when the speed ratio γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) 1 / γ ₃ , the direct connection mode can be switched. In the second speed change mode, the direct connection mode can be switched also when the gear ratio 1 / γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) γ ₃ .

In the first embodiment, for example, the diameter of the secondary pulley 32 is different from the diameter of the primary pulley 30, and the variable range of the engagement diameter of the endless belt 34 to the secondary pulley 32 is changed to the engagement of the endless belt 34 to the primary pulley 30. It can also be different from the variable range of diameter. In this case, the continuously variable transmission 14 has a gear ratio γcvt from the primary pulley 30 to the secondary pulley 32 of 1 / γ ₁ or more and γ ₂ or less (γ ₁ × γ ₂ > 1, γ ₁ ≠ γ ₂ ). It can be changed continuously within the range. In other words, the input / output (power transmission direction) of the continuously variable transmission 14 is reversed, in other words, the gear ratio 1 / γcvt from the secondary pulley 32 to the primary pulley 30 is in the range of 1 / γ ₂ or more and γ ₁ or less. Can be changed continuously. In this case, the gear ratio gamma ₃ of toward the speed change gear 46 from speed change gear 44, for example, by setting the large and gamma ₁ less than 1, the minimum gear ratio γt of the entire transmission gear ratio 1 / It can be continuously changed within the range of (γ ₂ × γ ₃ ) or more and the maximum gear ratio γ ₂ × γ ₃ or less. Further, by setting the transmission ratio γ ₃ from the transmission gear 44 to the transmission gear 46 to γ ₁ , the transmission ratio γt of the entire transmission device is greater than the minimum transmission ratio 1 / (γ ₂ × γ ₁ ) and the maximum transmission speed. The ratio can be continuously changed within a range of γ ₂ × γ ₁ or less.

“Embodiment 2”
FIG. 7 is a side view showing a schematic configuration of the transmission according to Embodiment 2 of the present invention. In the following description of the second embodiment, the same or corresponding components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.

In the present embodiment, compared to the first embodiment, the outer diameter (pitch circle diameter) of the transmission gear 46 is set smaller than the outer diameter (pitch circle diameter) of the transmission gear 44. The speed ratio γ _{3 applied} to the speed change gear 46 is set to a value smaller than 1. Here, the value of γ ₃ is set to 1 / γ ₁ . Therefore, the transmission mechanism 16 functions as a speed increasing mechanism that speeds up and transmits power when the power transmission direction is from the speed change gear 44 to the speed change gear 46. In other words, when the input / output (power transmission direction) of the transmission mechanism 16 is reversed, the speed ratio 1 / γ ₃ from the speed change gear 46 to the speed change gear 44 is set to a value greater than 1 (γ ₁ ). Yes. Therefore, the transmission mechanism 16 functions as a speed reduction mechanism that decelerates and transmits the power when the power transmission direction is a direction from the speed change gear 46 to the speed change gear 44.

In the present embodiment, as shown in FIG. 8, when the first speed change mode is selected, the speed ratio of the continuously variable transmission 14 (speed ratio from the primary pulley 30 to the secondary pulley 32) γcvt is set to the minimum speed ratio. By continuously changing within the range of 1 / γ ₁ or more and the maximum transmission ratio γ ₁ or less, the transmission gear ratio γt of the entire transmission device is continuously changed within the range of 1 / γ ₁ ² or more and 1 or less. be able to. As shown in FIG. 9, when the second speed change mode is selected, the speed ratio of the continuously variable transmission 14 (speed ratio from the secondary pulley 32 to the primary pulley 30) 1 / γcvt is set to the minimum speed ratio 1 By continuously changing within the range of / γ ₁ or more and the maximum gear ratio γ ₁ or less, the gear ratio γt of the entire transmission can be continuously changed within the range of 1 or more and γ ₁ ² or less. . Therefore, by selectively switching between the first speed change mode and the second speed change mode, the speed change ratio γt of the entire transmission apparatus becomes greater than the minimum speed change ratio 1 / γ ₁ ² (= γ ₃ ² ) and the maximum speed change ratio γ ₁ ^2. (= 1 / γ ₃ ² ) It can be changed continuously within the following range.

In the first speed change mode, when the speed change ratio γcvt of the continuously variable transmission 14 is equal (or substantially equal) to the maximum speed change ratio γ ₁ (= 1 / γ ₃ ), the clutch is changed to the second speed change mode. C1 and C4 can be prevented from slipping, and vibration and shock can be reduced. Further, in the second speed change mode, when the speed ratio 1 / γcvt of the continuously variable transmission 14 is equal (or substantially equal) to the minimum speed ratio 1 / γ ₁ (= γ ₃ ), the first speed change mode is switched. Further, it is possible to prevent the clutches C2 and C3 from slipping and to reduce vibrations and shocks.

Further, in the first speed change mode, when the speed change ratio γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) the maximum speed change ratio γ ₁ , for example, as shown in FIG. In the second speed change mode, even when the gear ratio 1 / γcvt of the continuously variable transmission 14 is equal to the minimum speed ratio 1 / gamma ₁ (or approximately equal) can be switched to direct mode.

  Further, as shown in FIG. 11, power is transmitted from the input shaft 12 to the output shaft 22 by selecting the reverse mode and transmitting power from the input shaft 12 to the output shaft 22 via the reverse gear 50 and the reverse idler gear 51. Can be transmitted with the direction of rotation reversed, and the vehicle can be moved backward.

In the present embodiment as well as the first embodiment, the variable range of the transmission ratio of the entire transmission can be widened, and the overall configuration of the transmission can be reduced in size. Furthermore, in this embodiment, the transmission gear ratio γ ₃ from the transmission gear 44 to the transmission gear 46 of the transmission mechanism 16 is set to 1 / γ ₁ , so that the transmission gear ratio γt of the entire transmission device is set to the minimum transmission ratio 1 /. While being able to change continuously within the range of γ ₁ ² or more and the maximum gear ratio γ ₁ ² or less, the variable range of the gear ratio γt can be further expanded.

In the second embodiment, the transmission gear ratio γ ₃ from the transmission gear 44 to the transmission gear 46 in the transmission mechanism 16 can be set to a value different from 1 / γ ₁ . For example, the transmission gear ratio γ ₃ from the transmission gear 44 to the transmission gear 46 can be set to a value larger than 1 / γ ₁ and smaller than 1. In this case, by selectively switching between the first speed change mode and the second speed change mode, the speed change ratio γt of the entire transmission is set to a minimum speed change ratio 1 / (γ ₁ × γ ₃ ) or more and the maximum speed change ratio γ ₁ × It can be continuously changed within a range of γ ₃ or less. In the first speed change mode, when the speed ratio γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) 1 / γ ₃ , slipping occurs in the clutches C1 and C4 by switching to the second speed change mode. Can be suppressed. Further, in the second speed change mode, when the speed ratio 1 / γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) γ ₃ , slipping occurs in the clutches C2 and C3 by switching to the first speed change mode. Can be suppressed. Further, in the first speed change mode, when the speed ratio γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) 1 / γ ₃ , the direct connection mode can be switched. In the second speed change mode, the direct connection mode can be switched also when the gear ratio 1 / γcvt of the continuously variable transmission 14 is equal to (or substantially equal to) γ ₃ .

Also in the second embodiment, for example, the diameter of the secondary pulley 32 is different from the diameter of the primary pulley 30, and the variable range of the engagement diameter of the endless belt 34 to the secondary pulley 32 can be changed to the engagement of the endless belt 34 to the primary pulley 30. It can also be different from the variable range of diameter. In this case, the continuously variable transmission 14 has a gear ratio γcvt from the primary pulley 30 to the secondary pulley 32 of 1 / γ ₁ or more and γ ₂ or less (γ ₁ × γ ₂ > 1, γ ₁ ≠ γ ₂ ). It can be changed continuously within the range. In this case, the speed ratio γ ₃ from the speed change gear 44 to the speed change gear 46 is set to a value that is, for example, 1 / γ ₂ or more and less than 1, so that the speed ratio γt of the entire transmission is reduced to the minimum speed ratio γ. It can be continuously changed within the range of ₃ / γ ₁ or more and the maximum gear ratio γ ₁ / γ ₃ or less. Further, by setting the transmission ratio γ ₃ from the transmission gear 44 to the transmission gear 46 to 1 / γ ₂ , the transmission ratio γt of the entire transmission apparatus is set to be equal to or greater than the minimum transmission ratio 1 / (γ ₂ × γ ₁ ) and It can be continuously changed within the range of the maximum gear ratio γ ₂ × γ ₁ or less.

From the first and second embodiments described above, the continuously variable transmission 14 can continuously change the speed ratio γcvt from the primary pulley 30 to the secondary pulley 32 within a range of 1 / γ ₁ or more and γ ₂ or less. In this case, the transmission gear ratio γ ₃ from the transmission gear 44 to the transmission gear 46 is
γ ₃ ≠ 1 and 1 / γ ₂ ≦ γ ₃ ≦ γ ₁
By setting to a value that satisfies the above, it is possible to continuously change the speed ratio γt of the entire transmission within a range not less than the minimum speed ratio and not more than the maximum speed ratio. However, in the first embodiment, the gear ratio γ ₃ from the transmission gear 44 to the transmission gear 46 can be set to a value larger than γ _{1. In the} second embodiment, the transmission gear 44 to the transmission gear can be set. It is also possible to set the gear ratio γ ₃ over 46 to a value smaller than 1 / γ ₂ . Also in this case, the variable range of the gear ratio γt of the entire transmission can be widened.

  In the first and second embodiments described above, the continuously variable transmission 14 can continuously change the gear ratio by using a continuously variable transmission other than the belt type continuously variable transmission. In the first and second embodiments, the transmission mechanism 16 can also shift the power using a transmission mechanism other than the gear transmission mechanism.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and it can implement with a various form in the range which does not deviate from the summary of this invention. Of course.

It is a figure which shows schematic structure of the transmission which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of the transmission which concerns on Embodiment 1 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 1 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 1 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 1 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 1 of this invention. It is a figure which shows schematic structure of the transmission which concerns on Embodiment 2 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 2 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 2 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 2 of this invention. It is a figure explaining operation | movement of the transmission which concerns on Embodiment 2 of this invention. It is a figure which shows schematic structure of the transmission which concerns on related technology. It is a figure which shows schematic structure of the transmission which concerns on related technology.

Explanation of symbols

  12 input shaft, 14 continuously variable transmission, 16 transmission mechanism, 18 input side switching mechanism, 20 output side switching mechanism, 22 output shaft, 30 primary pulley, 32 secondary pulley, 34 endless belt, 44, 46 gear for shifting, 47 , 48, 49 Gear, 50 Reverse gear, 51 Reverse idler gear, C1, C2, C3, C4, C5 Clutch.

Claims (6)

A transmission capable of shifting and transmitting power from an input shaft to an output shaft,
A first rotation element and a second rotation element that rotates in conjunction with the first rotation element, and the gear ratio between the first rotation element and the second rotation element can be continuously changed. A step transmission mechanism;
A third rotating element coupled to the second rotating element, and a fourth rotating element that rotates in conjunction with the third rotating element, wherein the power is shifted between the third rotating element and the fourth rotating element. A transmission mechanism capable of transmitting;
An input side switching mechanism for selectively connecting the input shaft to the first rotating element and the fourth rotating element;
An output side switching mechanism for selectively connecting the output shaft to the first rotating element and the fourth rotating element;
With
When transmitting power from the input shaft to the output shaft,
A first speed change mode for changing a gear ratio of the continuously variable transmission mechanism in a state where the input shaft is connected to the first rotating element by the input side switching mechanism and the output shaft is connected to the fourth rotating element by the output side switching mechanism ;
A second speed change mode for changing a gear ratio of the continuously variable transmission mechanism in a state where the input shaft is connected to the fourth rotating element by the input side switching mechanism and the output shaft is connected to the first rotating element by the output side switching mechanism ;
The input side switching mechanism connects the input shaft to the first rotating element and the output side switching mechanism connects the output shaft to the first rotating element, or the input side switching mechanism connects the input shaft to the fourth rotating element and outputs. A direct connection mode in which the output shaft is connected to the fourth rotating element by the side switching mechanism;
Selectively switching the,
For the input side switching mechanism, the rotating element connected to the input shaft is switched from the first rotating element to the fourth rotating element, and for the output side switching mechanism, the rotating element connected to the output shaft is switched from the fourth rotating element to the first rotating element. The transmission is switched from the first transmission mode to the second transmission mode . The transmission according to claim 1,
The continuously variable transmission mechanism can continuously change the speed ratio γcvt from the first rotation element to the second rotation element within a range of 1 / γ ₁ or more and γ ₂ or less (γ ₁ × γ ₂ > 1). Possible mechanism,
The gear ratio γ ₃ from the third rotating element to the fourth rotating element of the transmission mechanism is
γ ₃ ≠ 1 and 1 / γ ₂ ≦ γ ₃ ≦ γ ₁
A transmission that is set to a value that satisfies The transmission according to claim 2, wherein
A transmission in which a transmission ratio γ ₃ from the third rotation element to the fourth rotation element of the transmission mechanism is set to 1 / γ ₂ or γ ₁ . The transmission according to claim 2 or 3,
In the first speed change mode, the transmission is switched to the second speed change mode when a speed ratio γcvt from the first rotation element to the second rotation element of the continuously variable transmission mechanism is substantially equal to 1 / γ ₃ . The transmission according to any one of claims 2 to 4,
In the second speed change mode, the transmission is switched to the first speed change mode when a gear ratio 1 / γcvt from the second rotation element to the first rotation element of the continuously variable transmission mechanism is substantially equal to γ ₃ . The transmission according to any one of claims 1 to 5,
The continuously variable transmission mechanism
The first rotating element and the second rotating element are respectively a first pulley and a second pulley;
A belt wound around the first pulley and the second pulley;
A transmission device that is a mechanism that changes a transmission ratio between the first pulley and the second pulley by changing a belt engagement diameter of the first pulley and the second pulley .

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