JPS62255661A - Power division type continuously variable transmission - Google Patents

Abstract

PURPOSE:To obtain the same speed change range in normal and reverse revolution regions, by providing a variable speed mechanism, to which one part of rotary power is transmitted from a power source, while a rotary power addition mechanism which adds rotary power, output from said variable speed mechanism, to the residual rotary power from the power source. CONSTITUTION:A variable speed mechanism is constituted of a double speed inverting mechanism 4, static fluid pressure type speed change mechanism 5 and an equal speed normal revolution mechanism 29. Said variable speed mechanism changes a speed ne of rotary power from a power source 1 into a speed nv, but speed change ratio is set to be changed from -2 to 0. Accordingly, the speed nv changes in a range from -2ne to 0. And a planetary gears mechanism 3, serving for a rotary power addition mechanism, reduces the speed nv by 1/2 times while the speed ne of the residual rotary power from the power source 1 by 1/2 times, adding the both speeds. As a result, a relation of the particular expression is established, and a speed change range in a normal revolution region is equalized to that in a reverse revolution region.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a power split type continuously variable transmission suitable for use in vehicles, linear 7 actuators, etc. The present invention relates to a power split type continuously variable transmission in which the ranges are the same.

[Conventional technology]

In general, variable tf
IW using a hydraulic pump and a fixed displacement hydraulic motor
A hydraulic transmission mechanism is used.

However, such hydrostatic pressure shifting 8! ! Since the transmission mechanism has low power transmission efficiency, part of the rotational power from the power source is transmitted to the hydraulic transmission mechanism, and the rotational power output from this hydraulic transmission mechanism and the remaining rotation from the power source are Power and power add up to 8! Conventionally, a power split type continuously variable transmission has been developed in which the rotational power is transmitted to the rotational gear and added to the rotational power of the rotating gear.

That is, in the conventional power split type m-stage transmission, as shown in FIG. The output shaft of the hydraulically variable gear structure 2 is the rotary power before gmh
The output shaft of the power source 1 is also directly connected to the differential 7 differential gear 3'.

# In the hydraulic transmission mechanism 2, the rotation r! of the rotational power from the power source 1! t7Le is shifted to become the rotational speed nv that is input to the differential gear 73', but the ratio of the rotational speed nv to the rotational speed 7Le is γ=πv/ne
...(1) is set to vary from γ1 to 72.

Further, the differential gear 3' multiplies the rotational speed 7Lv of the rotational power from the hydrostatic pressure transmission mechanism 2 by 0, and multiplies the rotational speed of the remaining rotational power from the power source 1 by β, and then combines both. configured to add. In other words, the rotational speed n of the rotational power output from the differential gear 3'
0 is π. = απV + βne −−−−(2
), and if we use the above equation (1) in equation (2), we get
It is expressed as n,=(α・γ×β)7Le (3).

Then, the gear ratio γ in the hydrostatic transmission mechanism 2 is γ
Since it can be changed from I to γ2, the range of output rotation speed obtained from the above power split type continuously variable transmission is n, = (Oγ1 + β) 7Le --- (4) to n2 = (Qγ2 + β) ne ...The range is up to (5). It is assumed here that the rotation speed takes a positive value during forward rotation and a negative value during reverse rotation.

[Problem that the invention seeks to solve, α]

By the way, in the power split type continuously variable transmission described above, the power source 1 rotates in a constant direction and at a constant rotation speed, and is configured so that any rotation speed from a normal rotation range to a reverse rotation range can be obtained as an output. However, since the above 7I+γ2°α and β are arbitrarily determined, the shift range in the normal transmission range and the shift range in the reverse rotation range are different.

That is, the relationship π,=-n2 (6) does not hold between 7LI and n2 in equations (4) and (5).

For this reason, when the power split type continuously variable transmission is used in a vehicle, sufficient drivability cannot be obtained, and even if it is used in a linear actuator for control, sufficient performance cannot be obtained. be.

Additionally, if a continuously variable transmission is configured using a reversing clutch, in which the speed change range in the forward rotation range is equal to the speed change range in the reverse rotation range, the problem is that it will be large and heavy, and its structure will be extremely complicated. There are also points.

The present invention aims to solve the above-mentioned problems, and an object thereof is to provide a power split type continuously variable transmission that can obtain the same speed change range in the forward rotation range and the reverse rotation range. shall be.

[Means for solving problems]

For this reason, the power split type continuously variable power split type of the present invention? B8! is a variable speed mechanism to which part of the rotational power from the power source is transmitted, and the rotational power output from the variable speed mechanism and the remaining rotational power from the power source are transmitted and the two are added. a rotational power addition mechanism, such that the ratio of the rotational speed of the rotational power output from the variable speed mechanism to the rotational speed of the rotational power transmitted from the power source to the variable speed mechanism varies from 11 to 72. At the same time, the rotational power key W1. The structure is variable speed 8! The rotational speed of the rotational power from the power source is multiplied by 0, and the rotational speed of the remaining rotational power from the power source is multiplied by β, and then the two are added. A vf image is a configuration that satisfies the following conditional expression including a and β.

a(A,+γ,)+2β=O [Function] In the power split type continuously variable transmission of the present invention described above, the variable speed mr with respect to the rotational speed of the rotational power transmitted from the power source to the variable speed mechanism. , q is changed from 11 to γ2, and at the same time, in the rotational power addition mechanism, the rotational speed of the rotational power from the variable speed mechanism is multiplied by 0, and the rotational speed from the power source is After the rotational speed of the remaining rotational power is multiplied by β, both are added, and the following conditional expression including the above-mentioned γyo and γ21''lβ is satisfied.

a(γ1+γ2)+2β=O [Example] Examples of the present invention will be described below with reference to the drawings.
Fig. 1 shows a power split type continuously variable transmission as a first embodiment of the present invention, Fig. 1(a) is its block diagram, and Fig. 1(b) is its typical screen configuration diagram. , FIG. 1(e) is a schematic diagram of the main part thereof.

As shown in FIGS. 1(a) to (c), a large gear 8 is fixed to the output shaft of the power source 1, and the canine teeth 418 are small teeth fixed to the drive shaft of the variable displacement hydraulic pump 10. meshes with 9.

The gear ratio between the large gear 8 and the small teeth $9 is 2:1, and the drive shaft of the variable displacement hydraulic pump 10 rotates in the opposite direction to the output shaft of the power source 1. The rotation speed is twice the rotation speed ne of the power source 1.

Then, with the above-mentioned large gear 8 and small gear 9, a double speed reversing machine vI
I4 is configured.

The variable displacement hydraulic pump 10 also includes two liquid path pipes 14.
A fixed-capacity hydraulic motor 11 is connected via. This variable displacement hydraulic pump 10 has a variable swash plate for adjusting the amount of liquid fed to the fixed displacement hydraulic motor 11! 91 mechanism 12 is provided, and by operating the same swash plate variable mechanism 12, the rotation speed of the output shaft of the fixed capacity hydraulic motor 11 is variable'! The rotation speed is adjusted within a range from the rotation speed 2πe, which is equal to the rotation speed of the drive shaft of the 8i hydraulic pump 10, to the rotation WLo.

Further, the output shaft of the fixed displacement hydraulic motor 11 is configured to rotate in the same direction as the drive shaft of the variable displacement Jfl hydraulic pump 10.

The above variable it? I! Pressure pump 10. Fixed capacity hydraulic motor 11 and liquid path Ir! 14 and hydrostatic pressure shifting 8! groove(
A continuously variable transmission mechanism) 5 is constructed.

On the other hand, the gear 15 fixed to the variable displacement hydraulic pump 10 meshes with the idler 13, and the idler 13 meshes with the input gear 16 of the idle US quasi-mechanism 3 as the rotational power addition mechanism. Rotates at rotation speed nv.

These teeth J′1L15, idler 13 and input tooth 411
13 constitutes a constant speed forward rotation fivt29, and the double speed Tomomatsu fi? tt4, the hydrostatic pressure type transmission 615, and the constant speed normal rotation mechanism 29 constitute a variable speed mechanism.

The gear ratio between the gear 15 and the input gear 16 is 1:1, and the input gear 16 rotates in the same direction and at the same rotation speed as the gear 15, and the input gear 16 is connected to the second input shaft. (Sheath shaft) is fixed to 21'.

In addition, the output shaft of the "power source" is directly connected to the first input shaft 21 of the 11-star gear mechanism 3, and the first input shaft 21 is connected to the first
A second sun gear 26 is fixed to the second input shaft 21', and the second input shaft 21' with the second sun gear 26 is connected to the input shaft 21 of Pt51. It is rotatably supported around the

Furthermore, a member rotatable around the first input shaft 21 (
carrier) 22 has first and second pinion ears 27
．． 28 is rotatably pivoted, each Pt 51 and second pinion gear 27, 28 mesh with the first sun gear 25 and second sun gear 26 to rotate, and together with the member 22, the first and second pinion gears 27, 28 rotate. Second pinion gear 27.
It revolves around 28.

And the first and Pt52 pinion gears 27°28
are in mesh, as shown in Figure 1(e), and! ￥S1
The pinion gear 27 does not mesh with the second sun gear 26, and! 1112 pinion gear 28 is the first sun gear 2
It doesn't mesh with 5.

Further, an output gear 20 is fixed to the member 22, and the output teeth 1120 are connected to the gear 2 fixed to the drive shaft of the load 24.
It meshes with 3.

Then, the first sun gear 25 and the first pinion gear 27
The gear ratio between the second sun gear 26 and the second pinion gear 28, and the gear ratio between the output gear 20 and the gear 23 are all set to 1=1.

Since the power split type continuously variable M machine as the first embodiment of the present invention is configured as described above, the rotational speed ne of the rotational power of the power source 1 is changed in the variable speed mechanism, and the rotational speed nv However, since the gear ratio γ determined by the above equation (1) is set to vary from γ1=-2 to 12=0, the rotation speed nv mentioned above varies in the range from -2πe to O. do. However, the negative sign of γ1 is the variable speed +
This indicates that the rotational direction of the rotational power output from the fi 4M is opposite to the rotational direction of the rotational power from the power source 1.

In addition, in the i-layer surface II mechanism 3, after the rotational speed πV of the rotational power from the variable speed mechanism is multiplied by 172, and the rotational speed nc of the remaining rotational power from the power source 1 is multiplied by 172, both is added.

That is, in the above equation (2), α=1/2°β=
172, and further using γl = -2172 = 0 in equations (4) and (5) above, the planetary gear mounted vI
The rotational speed of the rotational power output from 3 is: n+=t(1/2)X(-2)+(1/2)lπe=
(1/2)7Le to nt=l(1/2)XO+(1/2)17Le=(1/
2) It can be seen that it changes within the range of the ne image.

In other words, the first pinion gear 27 is rotated by the sun gear 25 of MSl at a constant rotation speed πC, but this l
A second pinion gear 28 that meshes with the pinion gear 27 of
The rotational state from normal rotation to reverse rotation is determined according to the rotational state of .

As a result, in the power split type continuously variable transmission as the first embodiment of the present invention described above, the above 72. γ2゜α, β is γ
Since l''21γz=ow'=1/2+β=172, the speed change range in the normal rotation range and the speed change range in the reverse rotation range are equal, and this is based on the following principle.

In other words, the range of output rotation speed obtained from the above power split type continuously variable transmission is as shown in the following equations (4) and (5), n1=(αγ1+β)ne...From (4) The range is up to 7L2=(ffFt+β)ne=(5). Note that here, ne is the rotational speed of the rotational power from the power source 1. Further, the above-mentioned rotation speed assumes a positive value during forward rotation and a negative value during reverse rotation.

At this time, the necessary and sufficient condition for the shift range in the forward rotation range to be equal to the shift range in the reverse rotation range is that the following equation (6), n, = -n, ... (6) holds true. It is. Therefore, by substituting equation (4)*(5) into equation (6), (aγ1+β)ne=-(eγ2+β)7Le, that is, a(γ1+γ,)+2β=0 ・ ・ ・ ())
The following formula is obtained.

In the first embodiment of the present invention described above, γl =-2112=
0. α=1/2. Since β=172, which satisfies equation ()), the shift range in the normal rotation range and the shift range in the reverse rotation range are equal. However, as mentioned above (
7) It is not only the first embodiment described above that satisfies the expression, but there are countless combinations.

Therefore, to explain a power split type continuously variable transmission as a second embodiment of the present invention, FIG. 2(,) is a block diagram thereof, and FIG. 2(b) is a simplified side configuration diagram thereof.

As shown in FIGS. 2(B) and 2(L+), in the second embodiment of the present invention, the power! Teeth 1113' are fixed to the output shaft of the variable displacement hydraulic pump 10, and the gear 8' meshes with a gear 9' fixed to the drive shaft of the variable displacement hydraulic pump 10 via an idler 13'. The gear ratio between the gear 9' and the gear 9' is set at 1:1, and the constant forward rotation Iff mechanism 4' is constituted by the same plane 1% 8', 9' and the idler 13'.

Further, a fixed chamber fl hydraulic motor 11 is connected to the variable displacement hydraulic pump 10 via two liquid pipes 14, and the rotation speed of the output shaft of the fixed chamber tL hydraulic motor 11 is variable. In the range from the rotational speed πε, which is equal to the rotational speed of the drive shaft of the dish hydraulic pump 10, to the rotational speed 0: f4 is adjusted.

The output shaft of the fixed displacement hydraulic motor 11 rotates in the same direction as the drive shaft of the variable displacement hydraulic pump 10.

and a fixed capacity hydraulic motor 11. The variable displacement hydraulic pump 10 and the liquid path pipe 14 constitute a hydrostatic variable speed rocker structure 5.

Furthermore, a large gear 1 fixed to a fixed capacity hydraulic motor 11
5'' meshes with the input gear 16 of the planetary float mechanism 3, and the gear ratio between the large gear 15' and the input gear 16 is set to 2:1. The double speed inversion W1 mechanism 30 is configured, and the input gear 16 rotates twice as many times as the large gear 15' in the opposite direction.

The constant speed normal rotation mechanism 4', the hydrostatic pressure type transmission mechanism 5, and the double speed reverse rotation mechanism 30 constitute a variable speed mechanism.

Note that the reference numerals already mentioned in the drawings indicate almost the same parts.

Since the power split type continuously variable transmission according to the second embodiment of the present invention is constructed as described above, the variable speed 8! In the structure, the rotation wtne of the rotary power from the power source 1 is shifted to the rotation speed nv, but the gear ratio γ determined by the above equation (1) is changed from γ1=-2 to 72=0. Therefore, the rotational speed πV changes by ins from -2πe to 0.

In addition, when the planet teeth 4 are connected to the Isoshitsu 3, the rotational speed of the rotational power from the variable speed mechanism is multiplied by 7LV, and the rotational speed of the remaining rotational power from the power source 1 is multiplied by 72. Later, both are weighted.

That is, in the above equation (2), ff=1/21β=
172, and if γ+=2.72=0 is also considered, the above-mentioned (7
) is satisfied, and the speed change range in the forward rotation range and the speed change range in the reverse rotation range are equal.

In addition, the output shaft of the fixed customer fi hydraulic motor 11 is
The hydraulic pump 10 may be configured to rotate at twice the rotation speed of the drive shaft, and in that case, in the first embodiment described above, the gear ratio between the canine tooth 1μ8 and the small gear 9 is 1:1. In the fi2 embodiment described above, the gear ratio between the canine tooth 1115'' and the input gear 46 is set to 1=1.

Moreover, in the second embodiment, teeth! If the liquid path pipe 14 is connected so that the rotation directions of the gear 119 and the gear 15 are reversed, the idler 13' can be omitted.

In the above-described 1.2 embodiment of the present invention, the gear ratio between the first sun gear 25 and the first pinion gear 27, the gear ratio between the second sun gear 26 and the second pinion gear, the first
By appropriately determining the gear ratio between the pinion gear 27 and the second pinion gear 28, the above-mentioned a, β and (Q
/β) can be changed.

Further, Fig. 3 shows a power split type continuously variable transmission as an @3 embodiment of the present invention, Fig. 3(a) is its block diagram, and Fig. 3(b) is its typical side view. FIG.

As shown in FIGS. 3(a) and 3(b), in the third embodiment of the present invention, a large gear 8 is fixed to the output shaft of the power i1, and the large gear ftL8 is connected to the variable displacement hydraulic pump 10. It meshes with a small gear 9 fixed to the drive shaft.

This large gear 8 and small! ! The gear ratio with the ifu 9 is 2:1, and the drive shaft of the variable displacement hydraulic pump 10 is connected to the power source 1.
The rotation speed of the drive shaft is twice the rotation speed of the power source 1.

Then, the large gear 8 and the small teeth 119 rotate the double speed reversing rock 6.
1 is? +11 is achieved.

The variable displacement hydraulic pump 10 also includes two liquid path pipes 14.
The stationary officer 1 hydraulic motor 11 is connected via the stationary station 1 hydraulic motor 11. This variable displacement hydraulic pump 10 is equipped with a variable swash plate mechanism 12 for adjusting the aift supplied to the fixed displacement hydraulic motor 11, and by operating the variable swash plate mechanism 12, The rotation speed of the output shaft of the fixed displacement hydraulic motor 11 is a rotation speed 2 equal to the rotation speed of the drive shaft of the variable displacement hydraulic pump 10.
It is adjusted in the range from 7Le to rotation speed O.

In addition, the output shaft of the fixed t7fi hydraulic motor 11 is
It is designed to rotate in the same direction as the drive shaft of the variable displacement hydraulic pump 10.

Variable displacement hydraulic pump 10 above. Fixed capacity hydraulic motor 1
1 and the liquid path pipe 14 constitute a hydrostatic pressure type transmission mechanism 5.

On the other hand, teeth TtL1 fixed to the variable displacement hydraulic pump 10
5 meshes with an idler 13, and this idler 13 further meshes with an input tIJrrL16 of a differential 7-lens gear 73' serving as a rotary power adding mechanism, and this input source 111G rotates at a rotational speed of 7LV.

These gears 15, the feeder 13, and the input gear 16 constitute a constant velocity normal rotation machine slide 29, which includes the double speed reversing mechanism 4, the thin hydraulic transmission mechanism 5, and the constant velocity normal rotation 8! A variable speed mechanism is constituted by the rotor 29.

The gear ratio between the above gear 15 and the input (ff4116 is 1;
1, and the input gear 1a (111115) rotates in the same direction at the same number of rotations, and this input gear 16 is fixed to the second input shaft (sheath shaft) 21°.

Further, the output shaft of the power source 1 is directly connected to the first input shaft 21 of the differential gear 73, and the input shaft 21 of the differential gear 73
A bevel gear 19 is fixed to the input shaft 21 of @2.
A bevel gear 17 is fixed to ゛, and this bevel tooth]rL1
A second input shaft 21' with 7 is rotatably supported around the first input shaft 21.

Furthermore, a member rotatable around the first input shaft 21 (
Career) 22 has 'i! L star bevel gears 18 and 18 are pivotally connected, and each planetary bevel tooth IILI 8, 18 meshes with the bevel tooth r1117 and the bevel gear 19 and rotates,
Moreover, together with the member 22, it revolves around one bevel gear 17°.

Further, an output tooth rIL20 is fixed to the member 22,
This output gear 20 meshes with a gear 23 fixed to a drive shaft of a load 24.

And the gear ratio between the bevel gear 17 and the planetary bevel gear 18,
The gear ratio between the bevel gear 19 and the 11 star bevel teeth 11118 and the gear ratio between the output gear 20 and the tooth 1t123 are all 1:
Set to 1.

Power split type j! as a third embodiment of the present invention! ! Since the step-change transmission is configured as described above, in the variable speed mechanism, the rotational speed ne of the rotary power from the power source 1 is changed to rotation *nv, but the speed change determined by the above equation (1) is Since the ratio γ is set to vary from γ,cony to 72=0, the rotational speed nv changes in the range from -2πe to 0. However, the negative sign of γ1 means that the rotational direction of the rotational power output from the variable speed mechanism is
This indicates that the direction of rotation of the rotational power from the

In addition, in the differential 7-renial gear 3', the rotational speed nv of the rotational power from the variable speed W1 mechanism is multiplied by 172,
In addition, after the rotational speed ne of the remaining rotational power from the power ai is multiplied by 172, both are added.

That is, as shown in the first embodiment, in the above equation (2), ff4116. β = 172, and if 1+ = -2172 = 0 is used in equations (4) and (5) above, the rotational speed of the rotational power output from the differential gear 73' is n 1 = ( (1/2)X(-2)+(1/2)l?Le
= −(1/2)ne to π, = t(1/2)xO+(1/2 month 7L e= (
It can be seen that it changes in the range up to 1/2) 7L e.

As a result, the power split type stepless unit as the third embodiment of the present invention described above is realized. In rapid production, the above γ3. γ2゜a, β is 7
+=-21γz=o*('=1/2+β=172, so the shift range in the forward rotation range and the shift range in the reverse rotation range are equal, but this is based on the following principle.

That is, the range of output rotation speed obtained from the above power split type continuously variable transmission is as shown in the following equations (4) and (5): 7L+=('7+10β)we... 4) to n2=(αγ2+β)ne (5). Note that here, ne is the rotational speed of the rotational power from the power 'a1. Further, the above-mentioned rotation speed assumes a positive value during forward rotation and a negative value during reverse rotation.

At this time, the necessary and sufficient condition for the speed change range in the forward rotation region and the speed change range in the reverse rotation region to be equal is that equation (6) shown in the diagram, πl = -n 2 ... (6) holds. be. Therefore, in equation (6), (4), (5
), the following equation is obtained: (a7.1β) ne = −(aγ2+β)x6, that is, a(γ, +γ2)+2β=0 (7).

In the third embodiment of the present invention described above, γI''-2fγ.

=O,Q=172. Since β=l/2 and formula (7) is satisfied, the speed change range in the normal rotation range and the speed change range in the reverse rotation range are equal. However, as mentioned above (
7) It is not only the third embodiment described above that satisfies the expression, but there are countless combinations.

Therefore, to explain a power split type continuously variable transmission as a fourth embodiment of the present invention, FIG. 4(a) is a block diagram thereof, and FIG. 154(1,) is a schematic configuration diagram thereof.

As shown in FIG. 4(a) and (1+), $44 of the present invention
In practice, a gear 8' is fixed to the output shaft of the power source 1 in a configuration substantially similar to that of the first embodiment described above.
18' meshes with a gear 9' fixed to the drive shaft of the variable displacement hydraulic pump 10, so that the gear ratio between these gears 8' and m-table 9' is set at 1:1, and 8', 9
'' constitutes a structure 4'' for constant velocity reversal.

A fixed capacity hydraulic motor 11 is connected to the variable capacity hydraulic pump 10 via two liquid line pipes 14, and this fixed capacity hydraulic motor 11 is
The rotation speed of the output shaft of the variable displacement hydraulic motor 11 is adjusted in the range from a rotation speed 27Le, which is equal to the rotation speed of the drive shaft of the variable displacement hydraulic pump 10, to a rotation speed of 0. However, the output shaft of the fixed displacement teaching pressure motor 11 is the variable displacement hydraulic pump 10.
The drive shaft rotates in the opposite direction.

and a fixed capacity hydraulic motor 11. A hydrostatic transmission mechanism (
g-stage It: Hayaisokarae) 5' is constructed.

Furthermore, a large tooth 11 fixed to a fixed capacity hydraulic motor 11
j l 5' meshes with the input tooth +IB6 of the differential gear 3', and the large gear 15' and the input gear 1G
The gear ratio is set to 2:1. As a result, large tooth r
rL15' and the input gear 16 cause the double speed reversing mechanism 30 to
Thus, the input vlJIIt1G rotates at twice the rotation speed ny in the opposite direction to the large tooth +1LIs'.

A variable speed mechanism is constituted by the above-mentioned constant speed and shift transmission VT4'', the above-mentioned hydrostatic pressure type speed change mechanism 5', and the double speed inversion Pyi chain 30.

Note that the reference numerals already mentioned in the drawings indicate almost the same parts.

Since the power split type continuously variable transmission according to the fourth embodiment of the present invention is configured as described above, the rotational speed ne of the rotational power from the power source 1 is changed in the variable speed mechanism.
The speed ratio γ determined by the above equation (1) is set to vary from γ1=-2 to 72=0, so the rotation speed πV is set to vary from -2ne to 0. Varies in range.

In addition, in the differential gear 73', the rotational speed nv of the rotational power from the variable speed mechanism is multiplied by 172, and the rotational speed ne of the remaining rotational power from the power source 1 is increased by 1.
After multiplying by 72, both are added.

However, a negative sign here indicates that the direction of rotation is reversed.

That is, in the above equation (2), α=1/2. β=1
/2, and if γl''-2172=0 is also considered, the above-mentioned (
Equation 7) is satisfied, and the speed change range in the normal rotation range and the speed change range in the reverse rotation range are equal.

Further, the output shaft of the fixed 8-volume hydraulic motor 11 may be configured to rotate at twice the rotation speed of the drive shaft of the variable-capacity hydraulic pump 10, and in that case, in the j13 embodiment described above, The gear ratio of the large gear 8 and the small tooth -Q10 is set to 1:1, and in the fourth embodiment described above, the gear ratio of the large gear 8 and the small tooth -Q10 is set to 1:1.
The gear ratio of the input gear 16 and the input gear 16 is set to 1.

In addition, in place of the constant velocity reversing rock 4' and clear liquid pressure variable speed fivI5 of the second embodiment, the constant velocity reversing depression 4'' of the fourth embodiment is used.
A hydrostatic transmission mechanism 5' may also be provided.

In addition, in the above-mentioned 3.4th embodiment of the present invention, the gear ratio between the bevel gear 17 and the planetary bevel teeth 11118, the bevel gear 1
9 and the planetary bevel gear 18, the above-mentioned a and β can be changed.

In addition, in the power split type continuously variable transmission as each embodiment of the present invention described above, instead of the hydrostatic pressure type transmission mechanism 5, 5',
A continuously variable transmission mechanism such as a belt type or cone type may also be used.

Further, the speed change range of the variable speed Isokei may be set to any value from a normal rotation range to a reverse rotation range.

〔Effect of the invention〕

As detailed above, according to the power split type continuously variable transmission of the present invention, there is a variable speed mechanism to which part of the rotational power from the power source is transmitted, and a rotational power output from the variable speed mechanism. and a rotational power addition mechanism that receives the remaining rotational power from the power source and adds both, and the variable speed 8 corresponds to the rotational speed of the rotational power transmitted from the power source. ! The ratio of the rotational speed of the rotational power output from the mechanism is set to vary from 7° to γ2,
Above rotational power addition 8! The mechanism is configured to multiply the rotational speed of the rotational power of the variable speed mechanism by 0 and the rotational speed of the remaining rotational power from the power source by 5, and then add the two, ．． γ2. It has a simple structure that satisfies the following conditional expression including a and β, α(A, +12)+2β=0, and has the characteristic that the speed change range in the forward rotation range and the speed change range in the reverse rotation range are equal. Therefore, when the power split type continuously variable transmission is used in a vehicle, the drivability of the vehicle is improved, and the power split type continuously variable transmission can be used as a linear actuator for control. By doing so, it becomes possible to perform even more accurate and reliable RFit control.

[Brief explanation of drawings]

FIG. 1 shows a power split type continuously variable transmission as a first embodiment of the present invention, FIG. 1(a) is its block diagram, and FIG. 1(b) is a schematic side view of the t1 curve. Figure 1 (c
) is a schematic diagram of the main parts of the Ume type, and FIG. 2 shows a power split type continuously variable transmission as a second embodiment of the present invention, and FIG. 2(a) is a block diagram thereof. , 1(b) is a wedge-type side configuration diagram thereof, and FIG. 3 shows a power split type continuously variable transmission as a tlS3 embodiment of the present invention.
FIG. 3(a) is a block diagram thereof, FIG. 3(b) is a side configuration diagram of the same type, and FIG. 4 shows a power split type continuously variable transmission as a fourth embodiment of the present invention. So, Figure 4(a)
is a block diagram thereof, FIG. 4(b) is a schematic side configuration diagram thereof, and FIG. ttS5 is a block diagram showing a conventional power split type continuously variable transmission. 1. Power source, 3. I-layer surface ItL rock structure as a rotational power addition mechanism, 3'. Differential gear as a rotational power addition mechanism, 4. Double speed reversal mechanism constituting a variable speed mechanism, 4'.・Constant speed normal rotation rock structure that constitutes the variable speed mechanism, 4
#... A constant velocity reversing machine that makes up the variable speed mechanism h4, 5.5゛... Hydrostatic pressure type shift that makes up the variable speed mechanism 1g! Structure, 8.
・Large gear, 8″...Gear, 9...Small gear, 9'...Tooth 1
[, 1o... variable volume fi hydraulic pump, 11... fixed chamber f
fL hydraulic motor, 12...Swash plate, 13.13'...Idler, 14...Liquid pipe, 15...Gear, 15'...Large gear, 16...Input gear, 17...Bevel gear , 18... Planetary bevel gear, 19... Bevel gear, 20... Output gear, 2
1...tISi input shaft, 21'...second input shaft, 2
2... Member (carrier), 23... Gear, 24... Load, 25... Pt5l sun gear, 26... Second sun gear, 27... First pinion gear, 28... Second pinion gear, 29: Constant speed normal rotation mechanism that constitutes the variable speed mechanism; 30: Double speed reversal mechanism that constitutes the variable speed mechanism. Sub-Agent Patent Attorney Yoshihiko Iinuma Figure 1 (b)

Claims (1)

[Scope of Claims] A variable speed mechanism to which part of the rotational power from a power source is transmitted; and a variable speed mechanism to which the rotational power output from the variable speed mechanism and the remaining rotational power from the power source are transmitted. and a rotational power addition mechanism that adds the rotational power, and the ratio of the rotational speed of the rotational power output from the variable speed mechanism to the rotational speed of the rotational power transmitted from the power source to the variable speed mechanism is from γ_1 to γ.
The rotational power addition mechanism multiplies the rotational speed of the rotational power from the variable speed mechanism by α and the rotational speed of the remaining rotational power from the power source by β. A power split type continuously variable transmission characterized in that the power split type continuously variable transmission is configured so that the following conditional expression including the above-mentioned γ_1, γ_2, α, and β is satisfied. α(γ_1+γ_2)+2β=0