JP3950201B2 - Gear transmission for automatic transmission - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention is a gear transmission for an automatic transmission that can realize five forward speeds by three sets of single-pinion type planetary gears, and can realize four forward speeds by removing one set of planetary gears and sharing most of the speed change elements. Belongs to the technical field.
[0002]
[Prior art]
As conventional gear transmissions for automatic transmissions, devices listed below are known.
[0003]
  (1) 3N71B / 4N71B type automatic transmission28As shown in Fig. 2, two sets of single pinion type planetary gears achieve three forward speeds, and a single pinion type planetary gear is added on the input side of two sets of planetary gears to achieve four forward stages.29As shown in the table, the single-pinion type planetary gear having the same gear ratio is used to achieve the forward four-speed reverse one-speed gear stage including the fourth overdrive speed.
[0004]
  (2) Automatic transmission described in Japanese Patent Application Laid-Open No. 7-4478.30As shown in Fig. 3, three sets of single pinion type planetary gears are combined with a total of eight clutch / brake, one-way clutch and other engagement / release elements.31As shown in the fastening operation table, the forward shift stage including the fifth speed of overdrive and the reverse stage of two reverse stages are achieved. Note that the gear ratio of the three sets of planetary gears is different between the 330 type and the 580 type.
[0005]
  (3) Automatic transmission described in JP-A-1-24285432As shown in Fig. 4, four forward stages are realized by two sets of single pinion type planetary gears, and a single pinion type planetary gear is added on the output side of the two sets of planetary gears to achieve five forward stages.33As shown in the engagement operation table, the forward shift stage including the fifth forward speed and the reverse stage including the fifth speed of the overdrive is achieved by a high degree of freedom in setting the gear ratio.
[0006]
[Problems to be solved by the invention]
However, each of the above-mentioned conventional devices has advantages and problems as listed below.
[0007]
  (1) Figure28In the first conventional example shown in FIG. 3, since considerable components are shared by the forward 3 stages and the 4 stages in order to achieve the three forward stages and the four forward stages, a considerable economic effect can be obtained when manufacturing on an actual production line. The big, especially the figure28This is very effective in sharing at the basic stage of design as shown in the skeleton diagram.
[0008]
However, this first conventional example realizes three forward stages by two sets of single pinion planetary gears, and adds a single pinion planetary gear to the input side of the two sets of planetary gears to achieve four forward stages. In this way, it is not possible to meet the demand for a five-stage forward drive for high driving performance.
[0009]
  (2) Figure30The second conventional example shown in FIG. 5 can realize five forward speeds by three sets of single pinion type planetary gears.
[0010]
However, a combination of three single pinion type planetary gears and a total of eight engagement / release elements dedicated to the five forward speeds, the four forward speeds are realized by eliminating one planetary gear. Can not.
[0011]
In addition, if the gear ratio is not less than 0.8 at the fifth speed of overdrive and the gear ratio is forcibly set to less than 0.8 at the fifth speed, for example, the gear ratio at the time of reverse is not suitable. There is nothing that is practically suitable, for example, or the gear ratio between gears is not suitable.
[0012]
That is, the target gear ratio varies depending on the vehicle on which the target gear ratio is mounted. Therefore, if it cannot cope with this, it is not adopted, and the degree of freedom in setting the gear ratio is particularly important as one element of attractive product competitiveness. The normal overdrive gear ratio is generally around 0.7 in the industry, and the fact that the 5th gear ratio cannot achieve 0.7 is fatal for marketing to many vehicle manufacturers. It becomes.
[0013]
  (3) Figure32The third conventional example shown in FIG. 3 realizes a skeleton having a common forward 4th / 5th stage and a high degree of freedom in gear ratio.
[0014]
However, since the input member is always connected to the sun gear and power is input, the planetary gear is increased in size, and it cannot be achieved whether the automatic transmission is small or light.
[0015]
In other words, the ring gear is the best input to the planetary gear, and the sun gear is the worst. This is because, under the same driving load condition, the required strength of the gear ratio is determined in relation to the distance between the sun gear whose power is close to the rotation center and the ring gear far from the rotation center, and the ring gear input is far more advantageous. It is. Therefore, in the case of sun gear input, it is necessary to increase the gear tooth surface strength than in the case of ring gear input, and the sun gear outer diameter is increased. In the end, the entire planetary gear must be large. This is especially a problem when the gear ratio at the first speed and reverse is large.
[0016]
As mentioned above, each of the three known technologies introduced here has disadvantages, and studies were conducted to create a solution that can solve these problems. It goes without saying that creating this from many constraints is extremely difficult because of the gist of enormous man-hours and know-how. In other words, the important constraints are
1) Achieving 5 forward speeds with 3 sets of single pinion planetary gears and 4 forward speeds by removing 1 set of planetary gears.
[0017]
2) Although it is desirable for all of the four forward speeds and the five forward speeds, it is a ring gear input at least at the time of underdrive and reverse at the five forward speeds, and it is easy to achieve a reduction in size and weight.
[0018]
3) A value close to the target gear ratio including overdrive can be achieved.
[0019]
It is in.
[0020]
In consideration of these, the improvement study was advanced and the one suitable for practical use was created. The problem to be solved by the present invention is to realize the five forward stages and the four forward stages while sharing the components. Another object of the present invention is to provide a gear transmission for an automatic transmission that can achieve a reduction in size and weight by a ring gear input configuration and a value close to a target gear ratio including overdrive. .
[0021]
[Means for Solving the Problems]
  (Solution 1)
  A gear transmission for an automatic transmission according to Solution 1 (Claim 1) of the above-described problem, a single pinion type first planetary gear having a first sun gear, a first ring gear, and a first carrier;
  A single pinion type second planetary gear having a second sun gear, a second ring gear, and a second carrier;
  A single pinion type third planetary gear having a third sun gear, a third ring gear, and a third carrier;
  A first brake for selectively stopping rotation of the first sun gear;
  A second brake for integrally connecting the first carrier and the second ring gear by a first connecting member and selectively stopping rotation of the first connecting member;
  An input member integrally connected to the first ring gear;
  A first clutch for selectively connecting the input member and the first connecting member;
  A third brake for integrally connecting the second carrier and the third ring gear by a second connecting member, and selectively stopping rotation of the second connecting member;
  A second clutch for selectively connecting the input member and the second connecting member;
  A third clutch for selectively connecting the second sun gear and the third sun gear;
  A fourth brake for selectively stopping the rotation of the third sun gear;
  An output member coupled to the third carrier;
  When the third clutch, the first brake, and the fourth brake are engaged, the first speed gear stage is established, and when the first clutch, the third clutch, and the fourth brake are engaged, the second speed gear stage, A third gear is established when one clutch, the second clutch, and the fourth brake are engaged, and a fourth gear is established when the first clutch, the second clutch, and the third clutch are engaged, and the second clutch. And engagement of the third clutch and the second brakeAnd release of other clutches and brakesThe reverse gear is at least one of the fifth gear, the engagement between the third clutch and the first brake and the third brake, or the engagement between the first clutch, the third clutch and the third brake. Shift control means for obtaining a stage;
  It is characterized by having.
[0023]
  (Solutions2) Solution to the above problem2(Claims2) Is a single pinion type first planetary gear having a first sun gear, a first ring gear and a first carrier, and a single pinion type second planetary gear having a second sun gear, a second ring gear and a second carrier; A single pinion type third planetary gear having a third sun gear, a third ring gear, and a third carrier;SaidA first brake for selectively stopping rotation of the first sun gear;SaidWith the first carrierSaidThe second ring gear is connected integrally with the first connecting member,TheA first clutch for selectively connecting the first connecting member and the input member;SaidInput member andSaidA second clutch for selectively connecting the first ring gear;SaidWith the second carrierSaidThe third ring gear is connected integrally with the second connecting member, andTheA second brake for selectively stopping rotation of the second connecting member;SaidWith the first ring gearSaidA third clutch for selectively connecting the second connecting member;SaidWith the second sun gearSaidA fourth clutch for selectively connecting the third sun gear;SaidA third brake for selectively stopping the rotation of the third sun gear;SaidAn output member coupled to the third carrier;When the second clutch, the fourth clutch, the first brake, and the third brake are engaged, the first speed gear stage, the first clutch, the second clutch, the fourth clutch, and the third brake When engaged, the second gear is engaged, and when the first clutch, the second clutch, the third clutch, and the third brake are engaged, the third gear, the first clutch, the second clutch, and the third are engaged. When the clutch and the fourth clutch are engaged, a fourth speed is established, and when the first clutch, the third clutch, the fourth clutch, and the first brake are engaged, a fifth speed is established, and the second clutch is provided. A reverse gear is set at least one of engagement of the fourth clutch, the first brake, and the second brake, or engagement of the first clutch, the second clutch, the fourth clutch, and the second brake. ThatShift control means.
[0029]
  (Solution 3)
  Means for solving the above problem 3 (Claim 3) is a single pinion type first planetary gear having a first sun gear, a first ring gear, and a first carrier;
  A single pinion type second planetary gear having a second sun gear, a second ring gear, and a second carrier;
  A single pinion type third planetary gear having a third sun gear, a third ring gear, and a third carrier;
  A first brake for selectively stopping rotation of the first sun gear;
  A first clutch for integrally connecting the first carrier and the second sun gear by a first connecting member, and selectively connecting the first connecting member and the input member;
  A second clutch for selectively connecting the first ring gear and the input member;
  A second brake for integrally connecting the second carrier and the third ring gear by a second connecting member and selectively stopping rotation of the second connecting member;
  A third clutch for selectively connecting the first ring gear and the second ring gear or the third carrier;
  A fourth clutch for selectively connecting the second ring gear and the third carrier or the first ring gear;
  A third brake for selectively stopping the rotation of the third sun gear;
  An output member coupled to the third carrier;
  By engaging the second clutch, the fourth clutch, the first brake, and the third brake, the first gear, and by engaging the first clutch, the second clutch, the fourth clutch, and the third brake. The second speed gear stage, the first clutch, the second clutch, the third clutch, and the third brake are engaged, and the third speed gear stage, the first clutch, the second clutch, the third clutch, and the When the fourth clutch is engaged, the fourth speed gear stage is established, and when the first clutch, the third clutch, the fourth clutch, and the first brake are engaged, the fifth speed gear stage, the second clutch, and the fourth clutch are provided. A reverse gear stage at least one of engagement of the first brake and the second brake or engagement of the first clutch, the second clutch, the fourth clutch, and the second brake.Shift control means for obtaining
  It is characterized by having.
[0031]
DETAILED DESCRIPTION OF THE INVENTION
(Embodiment 1) Embodiment 1 claims1It is the gear transmission for automatic transmissions corresponding to invention described in 1).
[0032]
[Example of 5 steps forward]
FIG. 1 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of five forward gears. In FIG. 1, G1, G2, G3 are planetary gears, M1, M2 are connecting members, C1, C2, C3 are clutches, B1, B2, B3, B4 and B5 are brakes, F1 and F2 are one-way clutches, IN is an input shaft (input member), and OUT is an output shaft (output member).
[0033]
The first planetary gear G1 is a single pinion type planetary gear having a first sun gear S1, a first ring gear R1, and a first carrier P1 that holds a pinion gear that meshes with both gears S1 and R1.
[0034]
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier P2 holding a pinion gear meshing with both the gears S2 and R2.
[0035]
The third planetary gear G3 is a single pinion type planetary gear having a third sun gear S3, a third ring gear R3, and a third carrier P3 holding a pinion gear meshing with both the gears S3 and R3.
[0036]
The first brake B1 selectively stops the rotation of the first sun gear S1. A fifth brake B5 and a first one-way clutch F1 are provided in parallel with the first brake B1 so that the 1-2 shift is a one-way clutch shift (hereinafter referred to as OWC shift).
[0037]
The first carrier P1 and the second ring gear R2 are integrally connected by a first connecting member M1, and a second brake B2 for selectively stopping the rotation of the first connecting member M1 is provided. .
[0038]
The input shaft IN is integrally connected to the first ring gear R1.
[0039]
The first clutch C1 selectively connects the input shaft IN and the first connecting member M1.
[0040]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a third brake B3 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0041]
The second clutch C2 selectively connects the input shaft IN and the second connecting member M2.
[0042]
The third clutch C3 selectively connects the second sun gear S2 and the third sun gear S3. A second one-way clutch F2 is provided in parallel with the third clutch C3 so that the 2-3 shift is an OWC shift.
[0043]
The fourth brake B4 selectively stops the rotation of the third sun gear S3.
[0044]
The output shaft OUT is connected to the third carrier P3.
[0045]
Each of the clutches C1, C2, C3 and the brakes B1, B2, B3, B4, B5 has an unillustrated shift hydraulic control device (hydraulic control type, electronic control type, Hydraulic + electronic control type) is connected.
[0046]
A shift operation for obtaining a shift stage of five forward steps, one reverse step, or five forward steps and two reverse steps including an overdrive shift step will be described with reference to the engagement operation table shown in FIG.
[0047]
In the neutral range (N range), the third clutch C3 and the first brake B1 are engaged.
[0048]
The first speed in the D range is obtained by engaging the third clutch C3, the first brake B1, the fourth brake B4, and the fifth brake B5, and the second speed in the D range is the first, fifth brake B1, It is obtained by releasing B5 and engaging the first clutch C1, and the D range third speed is obtained by releasing the third clutch C3 at the second speed and engaging the second clutch C2, and the D range fourth speed. Is obtained by releasing the fourth brake B4 at the third speed and engaging the third clutch C3, and the fifth speed in the D range releases the first clutch C1 at the fourth speed and engages the second brake B2. It is obtained by doing.
[0049]
The reverse speed 1 is obtained by engaging the third clutch C3, the first brake B1, the third brake B3, and the fifth brake B5, and the reverse speed 2 is the first clutch C1, the third clutch C3, and the third brake. It is obtained by fastening B3.
[0050]
Both the one-way clutches F1 and F2 are mechanically operated at the first speed and the reverse speed 1, and the second one-way clutch F2 is mechanically operated at the second speed and the reverse speed 2.
[0051]
Here, as an example of the gear ratio setting, the gear ratio ρ of the first planetary gear G1₁ = 0.50 (= Z_S1/ Z_R1), Gear ratio ρ of second planetary gear G2₂ = 0.60 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.40 (= Z_S3/ Z_R3), 1st speed = 3.36, 2nd speed = 2.24, 3rd speed = 1.40, 4th speed = 1.00, 5th speed = 0.68, reverse speed 1 = 3 A gear ratio of .15, reverse speed 2 = 2.10 was obtained.
[0052]
[Example of 4 forward stages]
FIG. 3 is a skeleton diagram showing a gear transmission for an automatic transmission according to a forward four-stage example. In FIG. 3, G2 and G3 are planetary gears, M2 is a connecting member, C1, C2, C3 are clutches, B2, B3, B4 and B6 are brakes, F2 and F3 are one-way clutches, IN is an input shaft (input member), and OUT is an output shaft (output member).
[0053]
This forward four-stage example eliminates the first planetary gear G1 and the first brake B1 from the forward five-stage example shown in FIG. 1, and excludes the second planetary gear G2, the third planetary gear G3, and the first brake B1. , C2, C3, B2, B3, and B4 are examples in which four forward stages are achieved.
[0054]
The first clutch C1 selectively connects the input shaft IN and the second ring gear R2.
[0055]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a third brake B3 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0056]
The second clutch C2 selectively connects the input shaft IN and the second connecting member M2.
[0057]
The third clutch C3 selectively connects the second sun gear S2 and the third sun gear S3. A second one-way clutch F2 is provided in parallel with the third clutch C3 so that the 1-2 shift is an OWC shift.
[0058]
The fourth brake B4 selectively stops the rotation of the third sun gear S3. A third one-way clutch F3 and a sixth brake B6 are provided in parallel with the fourth brake B4 so that the 2-3 shift is an OWC shift.
[0059]
The output shaft OUT is connected to the third carrier P3.
[0060]
The clutches C1, C2, C3 and the brakes B2, B3, B4, B6 are provided with a shift hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure +) that generates an engagement pressure and a release pressure at each shift speed. Electronic control type) is connected.
[0061]
According to the engagement operation table shown in FIG. 4, the control law for engaging the first clutch C <b> 1 to realize the ring gear input at the first, second, third and reverse gears is used, and the forward four-stage reverse 1 The shift operation for obtaining the shift speed will be described.
[0062]
In the neutral range (N range), the third clutch C3 and the fourth brake B4 are engaged.
[0063]
The D range first speed is obtained by engaging the first clutch C1, the third clutch C3, the fourth brake B4, and the sixth brake B6, and the D range second speed releases the third clutch C3 at the first speed and releases the third clutch C3. 2 range C-3 is obtained by releasing the 4th and 6th brakes B4, B6 at the 2nd speed and engaging the 3rd clutch C3. This is obtained by releasing the first clutch C1 at the third speed and engaging the second brake B2.
[0064]
The reverse speed is obtained by engaging the first clutch C1, the third clutch C3, and the third brake B3.
[0065]
At the first speed, the one-way clutches F2 and F3 are mechanically operated, at the second speed, the third one-way clutch F3 is mechanically operated, and at the reverse speed, the second one-way clutch F2 is mechanically operated.
[0066]
Here, as an example of the gear ratio setting, the gear ratio ρ of the second planetary gear G2₂ = 0.70 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.50 (= Z_S3/ Z_R3), The gear ratios of 1st speed = 2.55, 2nd speed = 1.50, 3rd speed = 1.00, 4th speed = 0.68, reverse speed = 2.10 were obtained. .
[0067]
[Layout change example]
FIG. 5 is a skeleton diagram showing a gear transmission for an automatic transmission according to a layout change example of five forward speeds, and FIG. 6 is a skeleton diagram showing a gear transmission for an automatic transmission according to a layout change example of four forward speeds.
[0068]
In this layout change example, the second planetary gear G2 and the third planetary gear G3 are interchanged in the forward five-stage example of FIG. 1 and the forward four-stage example of FIG. B3 and B4 are arranged outside the second planetary gear G2 to facilitate the layout design and oil path design of the transmission mechanism.
[0069]
[Example of adding OWC]
In the above examples of the fifth forward speed and the fourth forward speed example, additional examples of the one-way clutches F1, F2, and F3 have been shown in order to obtain the OWC shift at the first speed or the second speed, but the control is simplified. Therefore, additional one-way clutches can be added to or removed from these OWC addition examples, one-way clutches can be added and brakes can be added to enable engine braking on the coasting side, and one-way clutches can be added to add one-way clutches. A clutch can be added or determined as needed (FIG. 7).
[0070]
However, claims1As long as it has the structure described in (1), the connection form of the elements in each planetary gear may be always connected or selectively connected via an engaging means such as a clutch.
[0073]
[Other changes]
Rather than selectively connecting the first carrier P1 of the first planetary gear G1 and the input shaft IN via the first clutch C1, even if the input shaft IN and the first sun gear S1 are selectively connected, The same effect as that of the first aspect of the invention can be obtained. However, in general, it is determined that the connection method described in claim 1 is good.
[0074]
The four-stage operation has been described by removing the first planetary gear G1 from the skeleton at the fifth stage, but can also be realized by removing the first brake B1 while leaving the first planetary gear G1 as it is. This matter can be determined according to various circumstances as appropriate.
[0075]
Next, the effect will be described.
[0076]
In the first embodiment, the forward five stages and the four forward stages are realized while sharing the constituent elements (although some specifications need to be changed, the second planetary gear G2, the third planetary gear G3, and many clutches / Sharing of basic parts such as brakes) and realization of small size and light weight by ring gear input configuration (ring gear input at all speeds in forward 5 speeds and gear speeds except 4th speed in forward 4 speeds) Thus, it is possible to provide a gear transmission for an automatic transmission that achieves a value close to the target gear ratio including overdrive (overdrive gear ratio of 0.8 or less).
[0077]
In addition, other parts such as a transmission case and a shaft can be shared by designing the first planetary gear part to be added on to the four-stage part from the beginning.
[0078]
  (Embodiment 2) Embodiment 2 claims2It is the gear transmission for automatic transmissions corresponding to invention described in 1).
[0079]
  [Example of 5 steps forward]8FIG. 5 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of five forward speeds.8, G1, G2, G3 are planetary gears, M1, M2 are connecting members, C1, C2, C3, C4 are clutches, B1, B2, B3 are brakes, F1, F2 are one-way clutches, and IN is an input shaft (input member). ), OUT is an output shaft (output member).
[0080]
The first planetary gear G1 is a single pinion type planetary gear having a first sun gear S1, a first ring gear R1, and a first carrier P1 that holds a pinion gear that meshes with both gears S1 and R1.
[0081]
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier P2 holding a pinion gear meshing with both the gears S2 and R2.
[0082]
The third planetary gear G3 is a single pinion type planetary gear having a third sun gear S3, a third ring gear R3, and a third carrier P3 holding a pinion gear meshing with both the gears S3 and R3.
[0083]
The first brake B1 selectively stops the rotation of the first sun gear S1. A fifth brake B5 and a first one-way clutch F1 are provided in parallel with the first brake B1 so that the 1-2 shift is a one-way clutch shift (hereinafter referred to as OWC shift).
[0084]
The first carrier P1 and the second ring gear R2 are integrally connected by a first connecting member M1, and a first clutch C1 for selectively connecting the first connecting member M1 and the input shaft IN is provided. ing.
[0085]
The second clutch C2 selectively connects the input shaft IN and the first ring gear R1.
[0086]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a second brake B2 for selectively stopping the rotation of the second connecting member M2 is provided.
[0087]
The third clutch C3 selectively connects the first ring gear R1 and the second connecting member M2.
[0088]
The fourth clutch C4 selectively connects the second sun gear S2 and the third sun gear S3. A second one-way clutch F2 is provided in parallel with the fourth clutch C4 so that the 2-3 shift is an OWC shift.
[0089]
The third brake B3 selectively stops the rotation of the third sun gear S3.
[0090]
The output shaft OUT is connected to the third carrier P3.
[0091]
The clutches C1, C2, C3, and C4 and the brakes B1, B2, and B3 have a shift hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure +) that generates an engagement pressure and a release pressure at each shift speed. Electronic control type) is connected.
[0092]
  Figure9Using the control law for engaging the second clutch C2 in order to realize the ring gear input at the first speed, second speed, third speed, fourth speed and reverse 1 and reverse 2 shift speeds according to the engagement operation table shown in FIG. Next, a description will be given of a shift operation for obtaining a shift stage of five forward steps, one reverse step, or five forward steps and two reverse steps including an overdrive shift step.
[0093]
In the neutral range (N range), the fourth clutch C4 and the first brake B1 are engaged.
[0094]
The D range first speed is obtained by engaging the second clutch C2, the fourth clutch C4, the first brake B1 and the third brake B3. The D range second speed releases the first brake B1 at the first speed and releases the first brake B1. It is obtained by engaging 1 clutch C1, and D range 3rd speed is obtained by releasing 4th clutch C4 in 2nd speed and engaging 3rd clutch C3, D range 4th speed is 3rd speed Is obtained by releasing the third brake B3 and engaging the fourth clutch C4, and the D range 5th speed is obtained by releasing the second clutch C2 at the 4th speed and engaging the first brake B1. .
[0095]
The reverse speed 1 is obtained by engaging the second clutch C2, the fourth clutch C4, the first brake B1, and the second brake B2, and the reverse speed 2 is the first clutch C1, the second clutch C2, and the fourth clutch. It is obtained by engaging C4 and the second brake B2.
[0096]
Both the one-way clutches F1 and F2 are mechanically operated at the first speed and the reverse speed 1, and the second one-way clutch F2 is mechanically operated at the second speed and the reverse speed 2.
[0097]
Here, as an example of the gear ratio setting, the gear ratio ρ of the first planetary gear G1₁ = 0.30 (= Z_S1/ Z_R1), Gear ratio ρ of second planetary gear G2₂ = 0.70 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.50 (= Z_S3/ Z_R3), 1st speed = 3.32, 2nd speed = 2.55, 3rd speed = 1.50, 4th speed = 1.00, 5th speed = 0.69, reverse speed 1 = 2 A gear ratio of .73 and reverse speed 2 = 2.10 was obtained.
[0098]
  [Example of 4 forward stages]10FIG. 3 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of four forward stages.10, G2 and G3 are planetary gears, M2 is a connecting member, C1, C2 and C4 are clutches, B2, B3, B4 and B5 are brakes, F2 and F3 are one-way clutches, IN is an input shaft (input member), and OUT is An output shaft (output member).
[0099]
  This forward four-stage example is shown in the figure8The first planetary gear G1, the first brake B1, and the third clutch C3 are abolished, and the second planetary gear G2, the third planetary gear G3, and the transmission elements C1, C2, C4, B2, and B3 are removed from the five forward speed examples shown in FIG. This is an example of utilizing four steps forward.
[0100]
The first clutch C1 selectively connects the input shaft IN and the second ring gear R2.
[0101]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a second brake B2 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0102]
The second clutch C2 selectively connects the input shaft IN and the second connecting member M2.
[0103]
The fourth clutch C4 selectively connects the second sun gear S2 and the third sun gear S3. A second one-way clutch F2 is provided in parallel with the third clutch C3 so that the 1-2 shift is an OWC shift.
[0104]
The third brake B3 selectively stops the rotation of the third sun gear S3. A third one-way clutch F3 and a fifth brake B5 are provided in parallel with the third brake B3 so that the 2-3 shift is an OWC shift.
[0105]
The fourth brake B4 selectively stops the rotation of the third ring gear R3.
The output shaft OUT is connected to the third carrier P3.
[0106]
The clutches C1, C2, C4 and the brakes B2, B3, B4, B5 have a transmission hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure +) that generates an engagement pressure and a release pressure at each gear stage. Electronic control type) is connected.
[0107]
  Figure11By using a control law for engaging the first clutch C1 in order to realize the ring gear input at the first, second, third and reverse gears according to the engagement operation table shown in FIG. The shift operation for obtaining the shift stage will be described.
[0108]
In the neutral range (N range), the fourth clutch C4 and the third brake B3 are engaged.
[0109]
The D range first speed is obtained by engaging the first clutch C1, the fourth clutch C4, the third brake B3, and the fifth brake B5, and the D range second speed releases the fourth clutch C4 at the first speed and releases the fourth clutch C4. 2 range C-3 is obtained by releasing the 3rd and 5th brakes B3 and B5 at the 2nd speed and engaging the 4th clutch C4. This is obtained by releasing the first clutch C1 at the third speed and engaging the fourth brake B4.
[0110]
The reverse speed is obtained by engaging the first clutch C1, the fourth clutch C4, and the second brake B2.
[0111]
At the first speed, the one-way clutches F2 and F3 are mechanically operated, at the second speed, the third one-way clutch F3 is mechanically operated, and at the reverse speed, the second one-way clutch F2 is mechanically operated.
[0112]
Here, as an example of the gear ratio setting, the gear ratio ρ of the second planetary gear G2₂ = 0.70 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.50 (= Z_S3/ Z_R3), The gear ratios of 1st speed = 2.55, 2nd speed = 1.50, 3rd speed = 1.00, 4th speed = 0.68, reverse speed = 2.10 were obtained. .
[0113]
  [Layout change example]12FIG. 5 is a skeleton diagram showing a gear transmission for an automatic transmission according to a layout change example of five forward speeds.13These are the skeleton figures which show the gear transmission for automatic transmissions by the layout change example of 4 steps | paragraphs of advance.
[0114]
  This layout change example8Figure and example of 5 steps forward10The second planetary gear G2 and the third planetary gear G3 are exchanged in the forward four-stage example, and thereby the second and third brakes B2 and B3 are arranged outside the second planetary gear G2 to change the speed. It facilitates mechanism layout design and oil passage design.
[0115]
[Example of adding OWC]
In the above examples of the fifth forward speed and the fourth forward speed example, additional examples of the one-way clutches F1, F2, and F3 have been shown in order to obtain the OWC shift at the first speed or the second speed, but the control is simplified. Therefore, additional one-way clutches can be added to or removed from these OWC addition examples, one-way clutches can be added and brakes can be added to enable engine braking on the coasting side, and one-way clutches can be added to add one-way clutches. A clutch can be added or determined as needed (FIG. 7).
[0116]
  However, claims2As long as it has the structure described in (1), the connection form of the elements in each planetary gear may be always connected or selectively connected via an engaging means such as a clutch.
[0119]
[Other changes]
The four-stage operation has been described by removing the first planetary gear G1 from the skeleton at the fifth stage, but the first planetary gear G1 is left as it is and the first clutch C1 is removed, and the input shaft IN and the first carrier P1 are removed. It can also be realized by connecting these together. This matter can be determined according to various circumstances as appropriate.
[0120]
Next, the effect will be described.
[0121]
In the second embodiment, the forward five stages and the four forward stages are realized while sharing the components (although some specifications need to be changed, the second planetary gear G2, the third planetary gear G3, and many clutches / Realization of small size and light weight by the ring gear input configuration (sharing for basic parts such as brakes) (ring gears at gear speeds excluding 5th speed at 5 forward speeds and 4th speeds at 4 forward speeds) It is possible to provide a gear transmission for an automatic transmission that achieves both (input) and realization of a value close to the target gear ratio including overdrive (overdrive gear ratio of 0.8 or less).
[0122]
In addition, other parts such as a transmission case and a shaft can be shared by designing the first planetary gear part to be added on to the four-stage part from the beginning.
[0123]
(Reference example 1)Reference Example 1 will be described.
[0124]
  [Example of 5 steps forward]14FIG. 5 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of five forward speeds.14G1, G2, G3 are planetary gears, M1, M2 are connecting members, C1, C2, C3 are clutches, B1, B2, B3, B4, B5 are brakes, F1, F2 are one-way clutches, and IN is an input shaft ( Input member), OUT is an output shaft (output member).
[0125]
The first planetary gear G1 is a single pinion type planetary gear having a first sun gear S1, a first ring gear R1, and a first carrier P1 that holds a pinion gear that meshes with both gears S1 and R1.
[0126]
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier P2 holding a pinion gear meshing with both the gears S2 and R2.
[0127]
The third planetary gear G3 is a single pinion type planetary gear having a third sun gear S3, a third ring gear R3, and a third carrier P3 holding a pinion gear meshing with both the gears S3 and R3.
[0128]
The first brake B1 selectively stops the rotation of the first sun gear S1. A fifth brake B5 and a first one-way clutch F1 are provided in parallel with the first brake B1 so that the 1-2 shift is a one-way clutch shift (hereinafter referred to as OWC shift).
[0129]
The first carrier P1 and the second sun gear S2 are integrally connected by a first connecting member M1, and a second brake B2 for selectively stopping the rotation of the first connecting member M1 is provided. .
[0130]
The input shaft IN is integrally connected to the first ring gear R1.
[0131]
The first clutch C1 selectively connects the input shaft IN and the first connecting member M1.
[0132]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a third brake B3 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0133]
The second clutch C2 selectively connects the input shaft IN and the second connecting member M2.
[0134]
The third clutch C3 selectively connects the second ring gear R2 and the third carrier P3. A second one-way clutch F2 is provided in parallel with the third clutch C3 so that the 2-3 shift is an OWC shift.
[0135]
The fourth brake B4 selectively stops the rotation of the third sun gear S3.
[0136]
The output shaft OUT is connected to the third carrier P3.
[0137]
Each of the clutches C1, C2, C3 and the brakes B1, B2, B3, B4, B5 has an unillustrated shift hydraulic control device (hydraulic control type, electronic control type, Hydraulic + electronic control type) is connected.
[0138]
  Figure19A shifting operation for obtaining a shift stage of 5 forwards, 1 reverse, or 5 forwards, 2 reverses including the overdrive shift stage will be described with reference to the engagement operation table shown in FIG.
[0139]
In the neutral range (N range), the third clutch C3 and the first brake B1 are engaged.
[0140]
The first speed in the D range is obtained by engaging the third clutch C3, the first brake B1, the fourth brake B4, and the fifth brake B5, and the second speed in the D range is the first, fifth brake B1, It is obtained by releasing B5 and engaging the first clutch C1, and the D range third speed is obtained by releasing the third clutch C3 at the second speed and engaging the second clutch C2, and the D range fourth speed. Is obtained by releasing the fourth brake B4 at the third speed and engaging the third clutch C3, and the fifth speed in the D range releases the first clutch C1 at the fourth speed and engages the second brake B2. It is obtained by doing.
[0141]
The reverse speed 1 is obtained by engaging the third clutch C3, the first brake B1, the third brake B3, and the fifth brake B5, and the reverse speed 2 is the first clutch C1, the third clutch C3, and the third brake. It is obtained by fastening B3.
[0142]
Both the one-way clutches F1 and F2 are mechanically operated at the first speed and the reverse speed 1, and the second one-way clutch F2 is mechanically operated at the second speed and the reverse speed 2.
[0143]
Here, as an example of the gear ratio setting, the gear ratio ρ of the first planetary gear G1₁ = 0.50 (= Z_S1/ Z_R1), Gear ratio ρ of second planetary gear G2₂ = 0.45 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.40 (= Z_S3/ Z_R3), 1st speed = 3.43, 2nd speed = 2.29, 3rd speed = 1.40, 4th speed = 1.00, 5th speed = 0.69, reverse speed 1 = 3 A gear ratio of .33, reverse speed 2 = 2.22 was obtained.
[0144]
  [Example of 4 forward stages]16FIG. 3 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of four forward stages.16, G2 and G3 are planetary gears, M2 is a connecting member, C1, C2 and C3 are clutches, B2, B3, B4 and B6 are brakes, F2 and F3 are one-way clutches, IN is an input shaft (input member), and OUT is An output shaft (output member).
[0145]
This forward four-stage example eliminates the first planetary gear G1 and the first brake B1 from the forward five-stage example shown in FIG. 1, and excludes the second planetary gear G2, the third planetary gear G3, and the first brake B1. , C2, C3, B2, B3, and B4 are examples in which four forward stages are achieved.
[0146]
The second brake B2 selectively stops the rotation of the second sun gear S2.
[0147]
The first clutch C1 selectively connects the second sun gear S2 and the input shaft IN.
[0148]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a third brake B3 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0149]
The second clutch C2 selectively connects the input shaft IN and the second connecting member M2.
[0150]
The third clutch C3 selectively connects the second ring gear R2 and the third carrier P3. A second one-way clutch F2 is provided in parallel with the third clutch C3 so that the 1-2 shift is an OWC shift.
[0151]
The fourth brake B4 selectively stops the rotation of the third sun gear S3. A third one-way clutch F3 and a sixth brake B6 are provided in parallel with the fourth brake B4 so that the 2-3 shift is an OWC shift.
[0152]
The output shaft OUT is connected to the third carrier P3.
[0153]
The clutches C1, C2, C3 and the brakes B2, B3, B4, B6 are provided with a shift hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure +) that generates an engagement pressure and a release pressure at each shift speed. Electronic control type) is connected.
[0154]
  Figure17The shift operation for obtaining the four shift stages and the one reverse shift stage will be described with reference to the fastening operation table shown in FIG.
[0155]
In the neutral range (N range), the third clutch C3 and the fourth brake B4 are engaged.
[0156]
The D range first speed is obtained by engaging the first clutch C1, the third clutch C3, the fourth brake B4, and the sixth brake B6, and the D range second speed releases the third clutch C3 at the first speed and releases the third clutch C3. 2 range C-3 is obtained by releasing the 4th and 6th brakes B4, B6 at the 2nd speed and engaging the 3rd clutch C3. This is obtained by releasing the first clutch C1 at the third speed and engaging the second brake B2.
[0157]
The reverse speed is obtained by engaging the first clutch C1, the third clutch C3, and the third brake B3.
[0158]
At the first speed, the one-way clutches F2 and F3 are mechanically operated, at the second speed, the third one-way clutch F3 is mechanically operated, and at the reverse speed, the second one-way clutch F2 is mechanically operated.
[0159]
Here, as an example of the gear ratio setting, the gear ratio ρ of the second planetary gear G2₂ = 0.45 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.55 (= Z_S3/ Z_R3), The gear ratios of 1st speed = 2.77, 2nd speed = 1.55, 3rd speed = 1.00, 4th speed = 0.69, reverse speed = 2.22 were obtained. .
[0160]
[Example of adding OWC]
In the above examples of the fifth forward speed and the fourth forward speed example, additional examples of the one-way clutches F1, F2, and F3 have been shown in order to obtain the OWC shift at the first speed or the second speed, but the control is simplified. Therefore, additional one-way clutches can be added to or removed from these OWC addition examples, one-way clutches can be added and brakes can be added to enable engine braking on the coasting side, and one-way clutches can be added to add one-way clutches. A clutch can be added or determined as needed (FIG. 7).
[0164]
  [Other Modifications] The first carrier P1 of the first planetary gear G1 and the input shaft IN are not selectively connected via the first clutch C1,18As shown in FIG. 3, the input shaft IN and the first sun gear S1 can be selectively connected via the first clutch C1.19As shown in FIG. 4, the first ring gear R1 and the first sun gear can be selectively connected via the first clutch C1 without being connected to the input shaft IN.Reference example 1Is almost the same effect.
[0165]
The four-stage operation has been described by removing the first planetary gear G1 from the skeleton at the fifth stage, but can also be realized by removing the first brake B1 while leaving the first planetary gear G1 as it is. This matter can be determined according to various circumstances as appropriate.
[0166]
Next, the effect will be described.
[0167]
  Reference example 1Then, while realizing the common use of components, realization of 5 forward speeds and 4 forward speeds (although some specifications need to be changed, basics such as 2nd planetary gear G2 and 3rd planetary gear G3 and many clutches and brakes, etc.) Shared parts), ring gear input configuration to achieve small size and light weight (ring gear input at all gears at 5 forward speeds), and realization of values close to the target gear ratio including overdrive (overload) A gear transmission for an automatic transmission that achieves a drive gear ratio of 0.8 or less can be provided.
[0168]
In addition, other parts such as a transmission case and a shaft can be shared by designing the first planetary gear part to be added on to the four-stage part from the beginning.
[0169]
(Reference example 2)Reference Example 2 will be described.
[0170]
  [Example of 5 steps forward]20FIG. 5 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of five forward speeds.20, G1, G2, G3 are planetary gears, M1, M2 are connecting members, C1, C2, C3, C4 are clutches, B1, B2, B3 are brakes, F1, F2 are one-way clutches, and IN is an input shaft (input member). ), OUT is an output shaft (output member).
[0171]
The first planetary gear G1 is a single pinion type planetary gear having a first sun gear S1, a first ring gear R1, and a first carrier P1 that holds a pinion gear that meshes with both gears S1 and R1.
[0172]
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier P2 holding a pinion gear meshing with both the gears S2 and R2.
[0173]
The third planetary gear G3 is a single pinion type planetary gear having a third sun gear S3, a third ring gear R3, and a third carrier P3 holding a pinion gear meshing with both the gears S3 and R3.
[0174]
The first brake B1 selectively stops the rotation of the first sun gear S1. A first one-way clutch F1 is provided in parallel with the first brake B1 so that the 1-2 shift is a one-way clutch shift.
[0175]
The first carrier P1 and the second sun gear S2 are integrally connected by a first connecting member M1, and a first clutch C1 for selectively connecting the first connecting member M1 and the input shaft IN is provided. ing.
[0176]
The second clutch C2 selectively connects the first ring gear R1 and the input shaft IN.
[0177]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a second brake B2 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0178]
The third clutch C3 selectively connects the second connecting member M2 and the first ring gear R1.
[0179]
The fourth clutch C4 selectively connects the second ring gear R2 and the third carrier P3. A second one-way clutch F2 is provided in parallel with the fourth clutch C4 so that the 2-3 shift is an OWC shift.
[0180]
The third brake B3 selectively stops the rotation of the third sun gear S3.
[0181]
The output shaft OUT is connected to the third carrier P3.
[0182]
The clutches C1, C2, C3, and C4 and the brakes B1, B2, and B3 have a shift hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure +) that generates an engagement pressure and a release pressure at each shift speed. Electronic control type) is connected.
[0183]
  Figure21By using the control law for engaging the second clutch C2 to realize the ring gear input at the first speed, second speed, third speed, fourth speed and the reverse speed 1 and reverse speed 2 according to the engagement operation table shown in FIG. Next, a description will be given of a shift operation for obtaining a shift stage including five forward speeds, one reverse stage, or five forward stages and two reverse stages including an overdrive shift stage.
[0184]
In the neutral range (N range), the fourth clutch C4 and the first brake B1 are engaged.
[0185]
The D range first speed is obtained by engaging the second clutch C2, the fourth clutch C4, the first brake B1 and the third brake B3. The D range second speed releases the first brake B1 at the first speed and releases the first brake B1. It is obtained by engaging 1 clutch C1, and D range 3rd speed is obtained by releasing 4th clutch C4 in 2nd speed and engaging 3rd clutch C3, D range 4th speed is 3rd speed Is obtained by releasing the third brake B3 and engaging the fourth clutch C4, and the D range 5th speed is obtained by releasing the second clutch C2 at the 4th speed and engaging the first brake B1. .
[0186]
The reverse speed 1 is obtained by engaging the second clutch C2, the fourth clutch C4, the first brake B1, and the second brake B2, and the reverse speed 2 is the first clutch C1, the second clutch C2, and the fourth clutch. It is obtained by engaging C4 and the second brake B2.
[0187]
Both the one-way clutches F1 and F2 are mechanically operated at the first speed and the reverse speed 1, and the second one-way clutch F2 is mechanically operated at the second speed and the reverse speed 2.
[0188]
Here, as an example of the gear ratio setting, the gear ratio ρ of the first planetary gear G1₁ = 0.35 (= Z_S1/ Z_R1), Gear ratio ρ of second planetary gear G2₂ = 0.40 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.40 (= Z_S3/ Z_R3), 1st speed = 3.24, 2nd speed = 2.40, 3rd speed = 1.40, 4th speed = 1.00, 5th speed = 0.67, reverse speed 1 = 3 A gear ratio of .38, reverse speed 2 = 2.50 was obtained.
[0189]
  [Example of 4 forward stages]22FIG. 28 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of four forward gears. In FIG. 28, G2 and G3 are planetary gears, M2 is a connecting member, C1, C2 and C4 are clutches, B2, B3, B5 B6 is a brake, F2 and F3 are one-way clutches, IN is an input shaft (input member), and OUT is an output shaft (output member).
[0190]
  This forward four-stage example is shown in the figure20The first planetary gear G1 and the first brake B1 are abolished and the transmission elements C1, C2, C4, B2, and B3 excluding the second planetary gear G2, the third planetary gear G3, and the first brake B1 from the five forward speed examples shown in FIG. This is an example of making the forward four-stage by utilizing
[0191]
The first clutch C1 selectively connects the input shaft IN and the second sun gear S2.
[0192]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a second brake B2 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0193]
The second clutch C2 selectively connects the input shaft IN and the second connecting member M2.
[0194]
The fourth clutch C4 selectively connects the second ring gear R2 and the third carrier P3. A second one-way clutch F2 is provided in parallel with the fourth clutch C4 so that the 1-2 shift is an OWC shift.
[0195]
The third brake B3 selectively stops the rotation of the third sun gear S3. A third one-way clutch F3 and a sixth brake B6 are provided in parallel with the third brake B3 so that the 2-3 shift is an OWC shift.
[0196]
The fifth brake B5 selectively stops the rotation of the second sun gear S2.
[0197]
The output shaft OUT is connected to the third carrier P3.
[0198]
The clutches C1, C2, C4 and the brakes B2, B3, B5, B6 have a transmission hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure +) that generates an engagement pressure and a release pressure at each gear stage. Electronic control type) is connected.
[0199]
  FIG.The shift operation for obtaining the four shift stages and the one reverse shift stage will be described with reference to the fastening operation table shown in FIG.
[0200]
In the neutral range (N range), the fourth clutch C4 and the third brake B3 are engaged.
[0201]
The D range first speed is obtained by engaging the first clutch C1, the fourth clutch C4, the third brake B3, and the sixth brake B6, and the D range second speed releases the fourth clutch C4 at the first speed and releases the fourth clutch C4. 2 range C-3 is obtained by releasing the 3rd and 6th brakes B3 and B6 at the 2nd speed and engaging the 4th clutch C4. This is obtained by releasing the first clutch C1 at the third speed and engaging the fifth brake B5.
[0202]
The reverse speed is obtained by engaging the first clutch C1, the fourth clutch C4, and the second brake B2.
[0203]
At the first speed, the one-way clutches F2 and F3 are mechanically operated, at the second speed, the third one-way clutch F3 is mechanically operated, and at the reverse speed, the second one-way clutch F2 is mechanically operated.
[0204]
Here, as an example of the gear ratio setting, the gear ratio ρ of the second planetary gear G2₂ = 0.45 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.55 (= Z_S3/ Z_R3), The gear ratios of 1st speed = 2.77, 2nd speed = 1.55, 3rd speed = 1.00, 4th speed = 0.69, reverse speed = 2.22 were obtained. .
[0205]
[Example of adding OWC]
In the above examples of the fifth forward speed and the fourth forward speed example, additional examples of the one-way clutches F1, F2, and F3 have been shown in order to obtain the OWC shift at the first speed or the second speed, but the control is simplified. Therefore, additional one-way clutches can be added to or removed from these OWC addition examples, one-way clutches can be added and brakes can be added to enable engine braking on the coasting side, and one-way clutches can be added to add one-way clutches. A clutch can be added or determined as needed (FIG. 7).
[0209]
[Other changes]
The four-stage operation has been described by removing the first planetary gear G1 from the skeleton at the fifth stage, but can also be realized by removing the first clutch C1 while leaving the first planetary gear G1 as it is. This matter can be determined according to various circumstances as appropriate.
[0210]
Next, the effect will be described.
[0211]
  Reference example 2Then, while realizing the common use of components, realization of 5 forward speeds and 4 forward speeds (although some specifications need to be changed, basics such as 2nd planetary gear G2 and 3rd planetary gear G3 and many clutches and brakes, etc.) Shared part), a ring gear input configuration to achieve a small size and light weight (ring gear input at the gear speed except the fifth speed at the fifth forward speed), and a value close to the target gear ratio including overdrive An automatic transmission gear transmission that achieves the realization (overdrive gear ratio of 0.8 or less) can be provided.
[0212]
In addition, other parts such as a transmission case and a shaft can be shared by designing the first planetary gear part to be added on to the four-stage part from the beginning.
[0213]
  (Embodiment3) Embodiment3Claims3It is the gear transmission for automatic transmissions corresponding to invention described in 1).
[0214]
  [Example of 5 steps forward]24FIG. 5 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of five forward speeds.24, G1, G2, G3 are planetary gears, M1, M2 are connecting members, C1, C2, C3, C4 are clutches, B1, B2, B3 are brakes, F1, F2 are one-way clutches, and IN is an input shaft (input member). ), OUT is an output shaft (output member).
[0215]
The first planetary gear G1 is a single pinion type planetary gear having a first sun gear S1, a first ring gear R1, and a first carrier P1 that holds a pinion gear that meshes with both gears S1 and R1.
[0216]
The second planetary gear G2 is a single pinion type planetary gear having a second sun gear S2, a second ring gear R2, and a second carrier P2 holding a pinion gear meshing with both the gears S2 and R2.
[0217]
The third planetary gear G3 is a single pinion type planetary gear having a third sun gear S3, a third ring gear R3, and a third carrier P3 holding a pinion gear meshing with both the gears S3 and R3.
[0218]
The first brake B1 selectively stops the rotation of the first sun gear S1. A first one-way clutch F1 is provided in parallel with the first brake B1 so that the 1-2 shift is a one-way clutch shift.
[0219]
The first carrier P1 and the second sun gear S2 are integrally connected by a first connecting member M1, and a first clutch C1 for selectively connecting the first connecting member M1 and the input shaft IN is provided. ing.
[0220]
The second clutch C2 selectively connects the first ring gear R1 and the input shaft IN.
[0221]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a second brake B2 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0222]
The third clutch C3 selectively connects the first ring gear R1 and the second ring gear R2.
[0223]
The fourth clutch C4 selectively connects the second ring gear R2 and the third carrier P3. A second one-way clutch F2 is provided in parallel with the fourth clutch C4 so that the 2-3 shift is an OWC shift.
[0224]
The third brake B3 selectively stops the rotation of the third sun gear S3.
[0225]
The output shaft OUT is connected to the third carrier P3.
[0226]
The clutches C1, C2, C3, and C4 and the brakes B1, B2, and B3 have a shift hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure +) that generates an engagement pressure and a release pressure at each shift speed. Electronic control type) is connected.
[0227]
  Figure25By using the control law for engaging the second clutch C2 to realize the ring gear input at the first speed, second speed, third speed, fourth speed and the reverse speed 1 and reverse speed 2 according to the engagement operation table shown in FIG. Next, a description will be given of a shift operation for obtaining a shift stage including five forward speeds, one reverse stage, or five forward stages and two reverse stages including an overdrive shift stage.
[0228]
In the neutral range (N range), the fourth clutch C4 and the first brake B1 are engaged.
[0229]
The D range first speed is obtained by engaging the second clutch C2, the fourth clutch C4, the first brake B1 and the third brake B3. The D range second speed releases the first brake B1 at the first speed and releases the first brake B1. It is obtained by engaging 1 clutch C1, and D range 3rd speed is obtained by releasing 4th clutch C4 in 2nd speed and engaging 3rd clutch C3, D range 4th speed is 3rd speed Is obtained by releasing the third brake B3 and engaging the fourth clutch C4, and the D range 5th speed is obtained by releasing the second clutch C2 at the 4th speed and engaging the first brake B1. .
[0230]
The reverse speed 1 is obtained by engaging the second clutch C2, the fourth clutch C4, the first brake B1, and the second brake B2, and the reverse speed 2 is the first clutch C1, the second clutch C2, and the fourth clutch. It is obtained by engaging C4 and the second brake B2.
[0231]
Both the one-way clutches F1 and F2 are mechanically operated at the first speed and the reverse speed 1, and the second one-way clutch F2 is mechanically operated at the second speed and the reverse speed 2.
[0232]
Here, as an example of the gear ratio setting, the gear ratio ρ of the first planetary gear G1₁ = 0.45 (= Z_S1/ Z_R1), Gear ratio ρ of second planetary gear G2₂ = 0.60 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.50 (= Z_S3/ Z_R3), 1st speed = 3.38, 2nd speed = 2.33, 3rd speed = 1.50, 4th speed = 1.00, 5th speed = 0.69, reverse speed 1 = 2 A gear ratio of .42, reverse speed 2 = 1.67 was obtained.
[0233]
  [Example of 4 forward stages]26FIG. 3 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of four forward stages.26, G2 and G3 are planetary gears, M2 is a connecting member, C1, C4 and C5 are clutches, B2, B3, B4 and B5 are brakes, F2 and F3 are one-way clutches, IN is an input shaft (input member), and OUT is An output shaft (output member).
[0234]
  This forward four-stage example is shown in the figure24The first planetary gear G1 and the first brake B1 are abolished from the five forward speed examples shown in FIG. 4, and the speed change elements C1, C4, B2, and B3 are used except for the second planetary gear G2, the third planetary gear G3, and the first brake B1. This is an example in which four forward stages are achieved.
[0235]
The first clutch C1 selectively connects the input shaft IN and the second sun gear S2.
[0236]
The second carrier P2 and the third ring gear R3 are integrally connected by a second connecting member M2, and a second brake B2 for selectively stopping the rotation of the second connecting member M2 is provided. .
[0237]
The fourth clutch C4 selectively connects the second ring gear R2 and the third carrier P3. A second one-way clutch F2 is provided in parallel with the fourth clutch C4 so that the 1-2 shift is an OWC shift.
[0238]
The fifth clutch C5 selectively connects the input shaft IN and the second ring gear R2.
[0239]
The third brake B3 selectively stops the rotation of the third sun gear S3. A third one-way clutch F3 and a fifth brake B5 are provided in parallel with the third brake B3 so that the 2-3 shift is an OWC shift.
[0240]
The fourth brake B4 selectively stops the rotation of the second sun gear S2.
[0241]
The output shaft OUT is connected to the third carrier P3.
[0242]
The clutches C1, C4, C5 and the brakes B2, B3, B4, B5 have a shift hydraulic pressure control device (hydraulic control type, electronic control type, hydraulic pressure + Electronic control type) is connected.
[0243]
  Figure27The shift operation for obtaining the four shift stages and the one reverse shift stage will be described with reference to the fastening operation table shown in FIG.
[0244]
In the neutral range (N range), the fourth clutch C4 and the third brake B3 are engaged.
[0245]
The D range first speed is obtained by engaging the first clutch C1, the fourth clutch C4, the third brake B3, and the fifth brake B5, and the D range second speed releases the fourth clutch C4 at the first speed and releases the fourth clutch C4. It is obtained by engaging the fifth clutch C5, and the third speed in the D range is obtained by releasing the third and fifth brakes B3 and B5 in the second speed and engaging the fourth clutch C4. This is obtained by releasing the first clutch C1 at the third speed and engaging the fourth brake B4.
[0246]
The reverse speed is obtained by engaging the first clutch C1, the fourth clutch C4, and the second brake B2.
[0247]
At the first speed, the one-way clutches F2 and F3 are mechanically operated, at the second speed, the third one-way clutch F3 is mechanically operated, and at the reverse speed, the second one-way clutch F2 is mechanically operated.
[0248]
Here, as an example of the gear ratio setting, the gear ratio ρ of the second planetary gear G2₂ = 0.45 (= Z_S2/ Z_R2), Gear ratio ρ of third planetary gear G3_Three = 0.60 (= Z_S3/ Z_R3), The gear ratio of the first speed = 2.93, the second speed = 1.60, the third speed = 1.00, the fourth speed = 0.69, and the reverse speed = 2.22 was obtained. .
[0249]
[Example of adding OWC]
In the above examples of the fifth forward speed and the fourth forward speed example, additional examples of the one-way clutches F1, F2, and F3 have been shown in order to obtain the OWC shift at the first speed or the second speed, but the control is simplified. Therefore, additional one-way clutches can be added to or removed from these OWC addition examples, one-way clutches can be added and brakes can be added to enable engine braking on the coasting side, and one-way clutches can be added to add one-way clutches. A clutch can be added or determined as needed (FIG. 7).
[0250]
  However, claims3As long as it has the structure described in (1), the connection form of the elements in each planetary gear may be always connected or selectively connected via an engaging means such as a clutch.
[0251]
[Other changes]
The four-stage operation has been described by removing the first planetary gear G1 from the skeleton at the fifth stage, but can also be realized by removing the first clutch C1 while leaving the first planetary gear G1 as it is. This matter can be determined according to various circumstances as appropriate.
[0252]
Next, the effect will be described.
[0253]
  Embodiment3Then, while realizing the common use of components, realization of 5 forward speeds and 4 forward speeds (although some specifications need to be changed, basics such as 2nd planetary gear G2 and 3rd planetary gear G3 and many clutches and brakes, etc.) Shared part), a ring gear input configuration to achieve a small size and light weight (ring gear input at the gear speed except the fifth speed at the fifth forward speed), and a value close to the target gear ratio including overdrive An automatic transmission gear transmission that achieves the realization (overdrive gear ratio of 0.8 or less) can be provided.
[0254]
In addition, other parts such as a transmission case and a shaft can be shared by designing the first planetary gear part to be added on to the four-stage part from the beginning.
[0255]
【The invention's effect】
  Claim1, 2, 3In the gear transmission for an automatic transmission described above, a configuration including four single-pinion type planetary gears, a shift element using a clutch and a brake, and a shift control means for obtaining five forward speeds is provided. To achieve the five forward speeds while sharing the components, and to achieve a reduction in size and weight by the ring gear input configuration at least in the underdrive gear stage, and the target gear including the fifth overdrive gear stage It is possible to provide a gear transmission for an automatic transmission that achieves the realization of a value close to the ratio.
[Brief description of the drawings]
FIG. 1 is a skeleton diagram showing a gear transmission for an automatic transmission according to a five-stage forward example of Embodiment 1. FIG.
FIG. 2 is a diagram illustrating a fastening operation table of each speed change element in the gear transmission for an automatic transmission according to the fifth forward example of the first embodiment.
FIG. 3 is a skeleton diagram showing a gear transmission for an automatic transmission according to a four-stage forward example of the first embodiment.
4 is a diagram showing a fastening operation table of each speed change element in the gear transmission for an automatic transmission according to the forward four-stage example of Embodiment 1. FIG.
FIG. 5 is a skeleton diagram showing a gear transmission for an automatic transmission according to a layout change example of five forward speeds according to the first embodiment;
6 is a skeleton diagram showing a gear transmission for an automatic transmission according to a layout change example of four forward stages according to the first embodiment. FIG.
FIG. 7 is a diagram showing a specific example of a brake / clutch when the OWC additional configuration of the gear transmission for an automatic transmission according to the first embodiment is adopted.
[Figure8FIG. 10 is a skeleton diagram showing a gear transmission for an automatic transmission according to a fifth forward example of the second embodiment.
[Figure9FIG. 10 is a diagram showing a fastening operation table of each speed change element in the gear transmission for an automatic transmission according to the fifth forward example of the second embodiment.
[Figure10FIG. 11 is a skeleton diagram showing a gear transmission for an automatic transmission according to a four-stage forward example of the second embodiment.
[Figure11FIG. 12 is a diagram showing a fastening operation table of each speed change element in the gear transmission for an automatic transmission according to the fourth forward example of the second embodiment.
[Figure12FIG. 12 is a skeleton diagram showing a gear transmission for an automatic transmission according to a layout change example of a forward five-stage of the second embodiment.
[Figure13FIG. 12 is a skeleton diagram showing a gear transmission for an automatic transmission according to an example of a layout change of four forward stages according to the second embodiment.
[Figure14]Reference example 1It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of 5 steps of forward.
[Figure15]Reference example 1It is a figure which shows the fastening operation | movement table | surface of each transmission element in the gear transmission for automatic transmissions by the example of 5 steps of forward.
[Figure16]Reference example 1It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of 4 steps of forward.
[Figure17]Reference example 1It is a figure which shows the fastening operation | movement table | surface of each transmission element in the gear transmission for automatic transmissions by the example of 4 steps of forward.
[Figure18]Reference example 1It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of the installation position change of the 1st clutch in five forward speeds.
[Figure19]Reference example 1It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of the installation position change of the 1st clutch in five forward speeds.
[Figure20]Reference example 2It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of 5 steps of forward.
[Figure21]Reference example 2It is a figure which shows the fastening operation | movement table | surface of each transmission element in the gear transmission for automatic transmissions by the example of 5 steps of forward.
[Figure22]Reference example 2It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of 4 steps of forward.
[Figure23]Reference example 2It is a figure which shows the fastening operation | movement table | surface of each transmission element in the gear transmission for automatic transmissions by the example of 4 steps of forward.
[Figure24Embodiment3It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of 5 steps of forward.
[Figure25Embodiment3It is a figure which shows the fastening operation | movement table | surface of each transmission element in the gear transmission for automatic transmissions by the example of 5 steps of forward.
[Figure26Embodiment3It is a skeleton figure which shows the gear transmission for automatic transmissions by the example of 4 steps of forward.
[Figure27Embodiment3It is a figure which shows the fastening operation | movement table | surface of each transmission element in the gear transmission for automatic transmissions by the example of 4 steps of forward.
[Figure28FIG. 9 is a skeleton diagram showing a gear transmission for an automatic transmission according to a conventional example 1;
[Figure29FIG. 10 is a diagram showing a fastening operation table of each speed change element in the gear transmission for an automatic transmission according to the conventional example 1;
[Figure30FIG. 10 is a skeleton diagram showing a gear transmission for an automatic transmission according to a conventional example 2;
[Figure31FIG. 11 is a diagram showing a fastening operation table of each speed change element in the gear transmission for an automatic transmission according to the second conventional example.
[Figure32FIG. 10 is a skeleton diagram showing a gear transmission for an automatic transmission according to Conventional Example 3;
[Figure33FIG. 12 is a diagram showing a fastening operation table of each speed change element in the gear transmission for an automatic transmission according to the conventional example 3;
[Explanation of symbols]
G1 1st planetary gear
S1 1st sun gear
P1 first carrier
R1 1st ring gear
G2 Second planetary gear
S2 Second sun gear
P2 Second carrier
R2 Second ring gear
G3 3rd planetary gear
S3 3rd sun gear
P3 3rd carrier
R3 3rd ring gear
M1 first connecting member
M2 second linked member
C1 1st clutch
C2 Second clutch
C3 3rd clutch
C4 4th clutch
C5 5th clutch
B1 First brake
B2 Second brake
B3 3rd brake
B4 4th brake
B5 5th brake
B6 6th brake
IN input shaft
OUT output shaft
F1 1st one-way clutch
F2 2nd one-way clutch
F3 3rd one-way clutch

Claims (3)

A single pinion type first planetary gear having a first sun gear, a first ring gear, and a first carrier;
A single pinion type second planetary gear having a second sun gear, a second ring gear, and a second carrier;
A single pinion type third planetary gear having a third sun gear, a third ring gear, and a third carrier;
A first brake for selectively stopping rotation of the first sun gear;
A second brake for integrally connecting the first carrier and the second ring gear by a first connecting member and selectively stopping rotation of the first connecting member;
An input member integrally connected to the first ring gear;
A first clutch for selectively connecting the input member and the first connecting member;
A third brake for integrally connecting the second carrier and the third ring gear by a second connecting member, and selectively stopping rotation of the second connecting member;
A second clutch for selectively connecting the input member and the second connecting member;
A third clutch for selectively connecting the second sun gear and the third sun gear;
A fourth brake for selectively stopping the rotation of the third sun gear;
An output member coupled to the third carrier;
When the third clutch, the first brake, and the fourth brake are engaged, the first speed gear stage is established, and when the first clutch, the third clutch, and the fourth brake are engaged, the second speed gear stage, A third gear is established when one clutch, the second clutch, and the fourth brake are engaged, and a fourth gear is established when the first clutch, the second clutch, and the third clutch are engaged, and the second clutch. And the engagement of the third clutch and the second brake and the release of the other clutches and brakes , the fifth gear, the engagement of the third clutch, the first brake and the third brake, or the Shift control means for obtaining a reverse gear in at least one of engagement of the first clutch, the third clutch, and the third brake;
A gear transmission for an automatic transmission, comprising: A single pinion type first planetary gear having a first sun gear, a first ring gear, and a first carrier;
A single pinion type second planetary gear having a second sun gear, a second ring gear, and a second carrier;
A single pinion type third planetary gear having a third sun gear, a third ring gear, and a third carrier;
A first brake for selectively stopping rotation of the first sun gear;
A first clutch for integrally connecting the first carrier and the second ring gear by a first connecting member, and selectively connecting the first connecting member and the input member;
A second clutch for selectively connecting the input member and the first ring gear;
A second brake for integrally connecting the second carrier and the third ring gear by a second connecting member and selectively stopping rotation of the second connecting member;
A third clutch for selectively connecting the first ring gear and the second connecting member;
A fourth clutch for selectively connecting the second sun gear and the third sun gear;
A third brake for selectively stopping the rotation of the third sun gear;
An output member coupled to the third carrier;
When the second clutch, the fourth clutch, the first brake, and the third brake are engaged, the first speed gear stage, the first clutch, the second clutch, the fourth clutch, and the third brake When engaged, the second gear is engaged, and when the first clutch, the second clutch, the third clutch, and the third brake are engaged, the third gear, the first clutch, the second clutch, and the third are engaged. When the clutch and the fourth clutch are engaged, the fourth speed gear stage is established, and when the first clutch, the third clutch, the fourth clutch, and the first brake are engaged, the fifth speed gear stage and the second clutch are provided. A reverse gear is set at least one of engagement of the fourth clutch, the first brake, and the second brake, or engagement of the first clutch, the second clutch, the fourth clutch, and the second brake. And shift control means that,
A gear transmission for an automatic transmission, comprising: A single pinion type first planetary gear having a first sun gear, a first ring gear, and a first carrier;
A single pinion type second planetary gear having a second sun gear, a second ring gear, and a second carrier;
A single pinion type third planetary gear having a third sun gear, a third ring gear, and a third carrier;
A first brake for selectively stopping rotation of the first sun gear;
A first clutch for integrally connecting the first carrier and the second sun gear by a first connecting member, and selectively connecting the first connecting member and the input member;
A second clutch for selectively connecting the first ring gear and the input member;
A second brake for integrally connecting the second carrier and the third ring gear by a second connecting member and selectively stopping rotation of the second connecting member;
A third clutch for selectively connecting the first ring gear and the second ring gear or the third carrier;
A fourth clutch for selectively connecting the second ring gear and the third carrier or the first ring gear;
A third brake for selectively stopping the rotation of the third sun gear;
An output member coupled to the third carrier;
By engaging the second clutch, the fourth clutch, the first brake, and the third brake, the first gear, and by engaging the first clutch, the second clutch, the fourth clutch, and the third brake. The second speed gear stage, the first clutch, the second clutch, the third clutch, and the third brake are engaged, and the third speed gear stage, the first clutch, the second clutch, the third clutch, and the When the fourth clutch is engaged, the fourth speed gear stage is established, and when the first clutch, the third clutch, the fourth clutch, and the first brake are engaged, the fifth speed gear stage, the second clutch, and the fourth clutch are provided. wherein the first brake second brake engagement, or the shift control hand to obtain a backward gear stage in the first clutch and at least one of the fastening of the said second clutch and said fourth clutch second brake And,
A gear transmission for an automatic transmission, comprising:

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