JPH08121554A - Planetary gear type transmission - Google Patents

Abstract

PURPOSE: To provide gear shifting of four forward and single reverse in gears of a planetary gear type transmission consisting of a first and a second planetary gears of a double and a single pinion types by providing a first to a third clutches, a first and a second brakes and a first to a third connecting means. CONSTITUTION: A planetary gear type transmission is equipped with a first, a second and a third clutches K1, K2, K3, which can be connected to a pinion carrier C12 of a double pinion type second planetary gear G12, a pinion carrier C11 of a single pinion type first planetary gear G11, and a sun gear S11 to an input shaft E1, and also with a first and a second brakes B1, B2 which can stop the rotation of the pinion carrier C11 of the first planetary gear G11 and the pinion carrier C12 of the second planetary gear G12. It is also equipped with a firs, a second and a third connecting members N11, N12, N13 making rotational connection between a ring gear R11 and the pinion gear C11 of the first planetary gear G11 and the pinion carrier C12 and a sun gear S12 of the second planetary gear G12, and between the ring gear R12 of the second planetary gear G12 and an output shaft E2.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear type transmission used in a multi-stage automatic transmission such as an automobile or a railway vehicle.

[0002]

2. Description of the Related Art An automatic transmission in which a planetary gear type transmission is combined with a torque converter has been put into practical use. The planetary gear type transmission is configured by combining a plurality of planetary gears with a plurality of clutches and brakes, and changing the combination of the on / off of the plurality of clutches and brakes to change the gear ratio (= input speed / output speed). Number) can be switched in multiple ways. The planetary gear device has 1 to 2 stages of pinion gears arranged between an outer ring gear and a central sun gear, and the plurality of pinion gears are constrained by a pinion carrier to perform planetary motion integrally. A one-stage pinion carrier is called a single-pinion carrier type, and a two-stage pinion carrier is called a double-pinion type. Rotating elements (ring gears, pinion carriers, sun gears) of the planetary gear device and a plurality of fastening elements (clutch and brake) are interconnected in an appropriate combination by a shell structure for carrying torque transmission or a one-way clutch. .

A conventional planetary gear type transmission in an automatic transmission for an automobile is capable of switching the gear ratio between four stages of three forward gears and one reverse gear and five stages of four forward gears and one reverse gear, which is the lowest. The gear ratio of 1 was the mainstream, but with the addition of so-called overdrive gears with a gear ratio of 1 or less, there are 5 stages of 4 forwards, 1 reverse and 5 stages of forwards and 1 reverse. Those that can switch the gear ratio have been put into practical use. In the overdrive stage, the engine speed is suppressed, and fuel consumption at high speed is improved. Here, the five forward gear type planetary gear type transmission is usually adopted as a higher-grade vehicle type or a high-grade specification with respect to the four forward gear automatic transmission. Common parts are desired.

An invention aiming at standardization of parts between a forward four-speed type and a forward five-speed type planetary gear type transmission is disclosed in Japanese Patent Laid-Open No. 59-113346. Here, an auxiliary transmission is connected to the output shaft side of a forward four-stage planetary gear type transmission including two sets of planetary gears to form a forward five-stage type planetary gear type transmission. Therefore, most of the components of the forward four-speed planetary gear type transmission can be used as they are even in the forward five-speed type. The sub-transmission device incorporates a set of planetary gear units, a clutch and a brake.

On the other hand, the forward five-stage planetary gear type speed change device disclosed in JP-A-47-19268 and JP-A-50-64660 incorporates three sets of planetary gear devices and has a casing. By removing one or two clutches and brakes inside the body, it is possible to make a forward four-stage planetary gear type transmission. Here, 4 steps forward and 5 steps forward
The external appearance of the stepped type planetary gear type transmission is exactly the same, and the automatic transmission mounting structure on the automobile side can be made common.

[0006]

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention
The planetary gear type transmission shown in Japanese Patent No. 13346 has a larger number of fastening elements (clutch and brake) than a dedicated forward five-stage planetary gear type transmission that does not use an auxiliary transmission. Therefore, during operation, the number of fastening elements that run idle in the non-fastened state increases, friction loss in the automatic transmission increases, and unnecessary heat is generated in the automatic transmission.
It also deteriorates the fuel efficiency of automobiles. In particular, although high-speed gears such as 4th and 5th gears with small gear ratios are commonly used, friction loss is considerably larger than that of a dedicated forward 5-speed planetary gear type transmission, and high speed roads Deterioration of fuel efficiency during high-speed driving is remarkable. Also, compared with the dedicated forward five-speed planetary gear type transmission, the arrangement of hydraulic cylinders for driving the fastening elements, the hydraulic circuit, the shaft structure, the shell structure for torque transmission, and the one-way clutch are arranged. It becomes complicated, and in cooperation with the increase in the number of these parts, the automatic transmission becomes large and the weight also increases. Such an increase in the number of parts also increases the cost of parts of the automatic transmission and the number of assembling steps, and lowers the reliability of the final automatic transmission.

The forward five-stage planetary gear type transmission disclosed in the above-mentioned Japanese Patent Laid-Open No. 50-64660 is equipped with a brake 1
It is possible to easily form a forward four-stage planetary gear type transmission by removing the individual pieces. However, since the number of sets of planetary gears is not reduced, the cost of parts is higher than that of the dedicated forward four-stage planetary gear type transmission, the friction loss of the planetary gears is large, and it is difficult to reduce the size and weight. is there.

The forward five-stage planetary gear type transmission disclosed in the above-mentioned Japanese Patent Laid-Open No. 47-19268 has a brake 1
It is possible to obtain a forward four-stage planetary gear type transmission by removing the individual and one set of planetary gears. However, the gear ratio is 1
Since a shift in a shift stage that exceeds the limit, that is, a so-called underdrive shift stage includes a shift by changing the engagement of two clutches, a shock at the shift is large. Then, in order to reduce the shock, it is necessary to delay the switching operation and to tolerate the extension of the time required for shifting.

According to the present invention, both the forward four-speed type and the five-speed forward type can be configured with the minimum number of parts while maximizing the commonization of parts, and the optimum gear ratio distribution can be achieved for both. It is an object of the present invention to provide a planetary gear type transmission that can secure the above.

[0010]

A planetary gear type transmission according to a first aspect of the present invention is a double pinion type first planetary gear unit and a single pinion type second planetary gear arranged on the rotation axis of an input member and an output member. A planetary gear type transmission having a gear device, wherein a first clutch capable of engaging a pinion carrier of a second planetary gear device with the input member, and a pinion carrier of the first planetary gear device as the input member. A second clutch that can be fastened to the input member, a third clutch that can fasten the sun gear of the first planetary gear device to the input member, and a first brake that can stop the rotation of the pinion carrier of the first planetary gear device. , A second brake capable of stopping the rotation of the pinion carrier of the second planetary gear device, and a rotary communication between the ring gear of the first planetary gear device and the pinion carrier of the second planetary gear device. First connecting means, second connecting means for rotationally connecting the pinion carrier of the first planetary gear device and the sun gear of the second planetary gear device, and rotating between the ring gear of the second planetary gear device and the output member. And a third contact means for contacting.

A planetary gear type transmission according to a second aspect of the present invention is a single pinion type third planetary gear apparatus arranged on the rotation axis line, in addition to the forward four-stage type construction of the first aspect, and a third aspect. A third brake capable of stopping the rotation of the ring gear of the planetary gear device, a pinion carrier of the third planetary gear device, and a second brake.
The forward movement 5 is provided by providing fourth connecting means for rotationally connecting between the pinion carriers of the planetary gear device and fifth connecting means for rotationally connecting between the sun gear of the third planetary gear device and the ring gear of the second planetary gear device. It is a stepped type.

A planetary gear type speed change device according to a third aspect of the present invention is the structure of the first aspect, wherein the first planetary gear device, the second planetary gear device, the first clutch, the second clutch, the third clutch and the first planetary gear device.
It has a sub-housing structure connectable to the main housing structure that houses the brake and the second brake, and the third planetary gear device and the third brake are arranged in the sub-housing structure.

[0013]

According to the planetary gear type transmission of claim 1, two sets of a planetary gear set of a double pinion type and a single pinion type are provided.
The forward four-stage type includes one clutch and two brakes, but can be easily changed to a five-forward type by adding a single pinion type third planetary gear unit and a third brake. A third planetary gear device and a third structure according to the first aspect.
An example of the arrangement and connection of the brakes is given in claim 2. Each of the connecting means may have a mutually fixed structure that transmits bidirectional rotation torque, and may be a one-way clutch that transmits rotation torque in one direction and idles rotational drive in the opposite direction, or a one-way clutch. The clutch may be combined in parallel.

1 in the planetary gear type transmission according to claim 1
At high speed, the rotational output of the first planetary gear device, which is reversely decelerated,
The second planetary gear unit further reverses and decelerates. When the second brake is engaged, both the first planetary gear unit with the ring gear locked and the second planetary gear unit with the pinion carrier locked serve as a reversing reducer. The rotation of the input member is input to the sun gear of the first planetary gear device through the third clutch. In the double pinion type planetary gear device, since the rotation direction of the pinion carrier with respect to the ring gear is opposite to that of the single pinion type, the rotation of the sun gear (input member) is reversed from the pinion carrier of the first planetary gear device. The decelerated rotation is taken out. When this reversely decelerated rotation is input to the sun gear of the second planetary gear device in which the pinion carrier is locked, the double-decreased forward rotation is extracted from the ring gear.

In the second speed, the forward deceleration rotation formed by the first planetary gear device is slightly increased by the second planetary gear device to perform deceleration by subtraction. The first brake is engaged to lock the pinion carrier of the first planetary gear unit and the sun gear of the second planetary gear unit, and the rotation of the input member is connected to the sun gear of the first planetary gear unit. In the double pinion type planetary gear device, the relative rotation direction of the ring gear with respect to the pinion carrier is opposite to that of the single pinion type,
The first planetary gear set serves as a normal speed reducer without reversal, and the second planetary gear set serves as a normal speed increaser without reversal. Therefore, from the ring gear of the first planetary gear device, the forward rotation in which the rotation of the sun gear (input member) is significantly reduced is taken out. Then, from the ring gear of the second planetary gear device, the forward rotation obtained by slightly increasing the "rotation of the ring gear of the first planetary gear device" input to the pinion carrier is extracted.

In the third speed, both the first planetary gear unit and the second planetary gear unit rotate together while the meshed state is locked, and the rotation of the input member is transmitted to the output member in a one-to-one correspondence. When the first clutch is engaged, the rotation of the input member is input to the ring gear of the first planetary gear device via the pinion carrier of the second planetary gear device. When the third clutch is engaged, the rotation of the input member is input to the sun gear of the first planetary gear device. Therefore, the first clutch and the third
When both of the clutches are engaged, relative rotation between the ring gear and the sun gear of the first planetary gear device is eliminated, and the entire first planetary gear device rotates integrally with the input member while maintaining one meshed state.

At 4th speed, the second planetary gear set performs a simple speedup. With respect to the second planetary gear device whose sun gear is locked by the brake B1, the rotation of the input shaft is input from the first clutch to the pinion carrier. From the ring gear of the second planetary gear device, the rotation in which the input of the pinion carrier is accelerated is taken out. This rotation is transmitted to the output member and output.

In reverse, the second planetary gear unit, which has the pinion carrier locked by the second brake, performs reverse rotation deceleration. When the single pinion type second planetary gear device in which the pinion carrier is locked is the sun gear input,
Reversed decelerated rotation is taken out from the ring gear.
The inverted decelerated rotation is transmitted to the output member and output.

In the planetary gear type transmission of claim 2, a "gear having a gear ratio intermediate between the two" is added between the first-gear and second-gear gears according to the structure of claim 1. In the added shift speed, the third planetary gear device functions auxiliary to the deceleration operation of the first speed according to the structure of claim 1. That is, the third planetary gear device in which the ring gear is locked by the third brake outputs the rotation in the forward direction in which the rotation of the sun gear (output shaft) is reduced to the pinion carrier. The rotation of the pinion carrier is returned and input to the ring gear of the first planetary gear device and the pinion carrier of the second planetary gear device. From the ring gear of the second planetary gear device in which the pinion carrier rotates in the forward direction, the rotation speed that is higher than the "first speed" according to the configuration of claim 1 is output.

In a planetary gear type transmission according to a third aspect of the present invention, there is provided a main housing structure in which the four forward gear type planetary gear type transmission according to the first aspect is housed. By connecting the sub-housing structure storing the three brakes, a forward five-stage planetary gear type transmission is constructed.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A planetary gear type transmission according to an embodiment will be described with reference to FIGS. The planetary gear type transmission of the embodiment is combined with a torque converter and an oil pump (not shown) to be assembled into an automatic transmission (automatic transmission) for an automobile. 1 to 5, the configuration of the planetary gear type transmission is represented by a skeleton in which the lower side from the center line is omitted to represent the arrangement and connection state of the components. FIG. 1 is an explanatory diagram of a configuration of a planetary gear type transmission device of an embodiment, FIG. 2 is an explanatory diagram of a forward four-stage planetary gear type transmission device,
3 and 4 are operation diagrams of the planetary gear device at each shift stage,
FIG. 5 is an explanatory diagram of the housing structure. In FIG. 1, (a) shows the skeleton, and (b) shows the engagement state and the gear ratio of the clutch and the brake at each gear. In FIG. 2, (a) shows the skeleton, and (b) shows the engaged state of the clutch and brake at each gear. In FIG. 3, (a) is the first speed, (b)
Shows the operating state of the 2nd speed, and (c) shows the operating state of the 3rd speed. FIG.
In the figure, (a) shows the fourth speed, (b) shows the fifth speed, and (c) shows the reverse operation state.

In FIG. 1 (a), three sets of clutches K1, K2, K from the left on the same rotation axis as the input shaft E1.
Three, three sets of brakes B1, B2, B3, three sets of planetary gear units G11, G12, G13, and an output shaft E2 are arranged. A housing D1 shown by hatching at the top stores these mechanisms, and also has an input shaft E1 and an output shaft E.
2 rotatably supported. In the double pinion type planetary gear device G11, a plurality of sets of two-stage pinion gears P11 and Q11 are arranged and meshed between an outer peripheral ring gear R11 and a central sun gear S11, and a plurality of sets of pinion gears P1 are engaged.
1, Q11 is integrally restrained by the pinion carrier C11. In the single pinion type planetary gear device G12, a plurality of pinion gears P12 are arranged and meshed between an outer peripheral ring gear R12 and a central sun gear S12, and the plurality of pinion gears P12 are integrally restrained by a pinion carrier C12. The single pinion type planetary gear unit G13 is
A plurality of pinion gears P13 are arranged and meshed between the outer ring gear R13 and the central sun gear S13, and the plurality of pinion gears P13 are integrally restrained by the pinion carrier C13.

The clutch K1 is capable of engaging the input shaft E1 with the pinion carrier C12 of the planetary gear unit G12. The clutch K2 connects the input shaft E1 to the planetary gear unit G1.
1 pinion carrier C11 and planetary gear unit G12
Can be fastened to the sun gear S12. Clutch K
3, the input shaft E1 is the sun gear S1 of the planetary gear unit G11.
It can be fastened to 1. The brake B1 is a case D1.
Against the pinion carrier C11 of the planetary gear unit G11
The sun gear S12 of the planetary gear unit G12 can be locked to stop the rotation of the pinion carrier C11 and the sun gear S12. The brake B2 locks the ring gear R11 of the planetary gear unit G11 and the pinion carrier C12 of the planetary gear unit G12 with respect to the housing D1,
The rotations of the ring gear R11 and the pinion carrier C12 can be stopped. The brake B3 locks the ring gear R13 of the planetary gear device G13 with respect to the housing D1,
The rotation of the ring gear R13 can be stopped.

A connecting member N11 is arranged between the ring gear R11 of the planetary gear unit G11 and the pinion carrier C12 of the planetary gear unit G12. The pinion carrier C11 of the planetary gear unit G11 and the sun gear S of the planetary gear unit G12.
The connecting member N12 is arranged between the two. A connecting member N is provided between the sun gear S13 and the output shaft E2 of the planetary gear unit G13.
13 are arranged. Pinion carrier C12 of planetary gear unit G12 and pinion carrier C of planetary gear unit G13
The connecting member N14 is arranged between the members 13. The connecting member N15 is arranged between the ring gear R12 of the planetary gear device G12 and the sun gear S13 of the planetary gear device G13. The connecting members N11, N12, N13, N14, N15 are configured by a shell structure for torque transmission, an axial meshing structure, or a multiple shaft structure, and fix relative rotation to transmit rotational torque in both forward and reverse directions. .

As shown in the table in FIG. 1B, the combination of the clutch K3 and the brake B2 is engaged in the first speed. In second gear, clutch K3 and brake B3
The combination of is concluded. In the third speed, the combination of the clutch K3 and the brake B1 is engaged. In the fourth speed, the combination of the clutches K1 and K3 is engaged. In the fifth speed, the combination of the clutch K1 and the brake B1 is engaged. In reverse, the combination of the clutch K2 and the brake B2 is engaged. The gear ratios at these gears are obtained by using the tooth ratios α1, α2, α3 of the planetary gear units G11, G12, G13 as shown in the right-hand formula. Using this formula, the tooth number ratios α1, α2, α3 are 0.475, 0.
Specific values of the gear ratio when 325 and 0.65 are set are shown in the rightmost column.

In the planetary gear type transmission having five forward gears and one reverse gear shown in FIG. 1A, the planetary gear train G13 and the brake B3 are removed, and a portion A1 surrounded by a broken line is left. It is possible to use a planetary gear type transmission having one gear and one reverse gear. Fig. 2 shows a planetary gear type transmission with four forward gears and one reverse gear.
Shown in In FIG. 2B, the second speed of FIG. 1B related to the planetary gear unit G13 is lost, and the portion surrounded by the broken line in FIG. 1B is a new clutch and brake in each shift stage. It becomes the operation combination of. 1st speed of (b) of FIG.
3rd, 4th, and 5th are the same as 1st and 2nd in (b) of FIG.
Speed, 3rd speed, 4th speed, gear ratios and numerical values (tooth ratio α
1 and α2 are the same).

Next, referring to FIG. 3 and FIG. 4, 5 forward stages,
The operation state of the planetary gear device at each shift speed of one reverse speed will be described. Here, for the clutch and the brake, the solid line is the engaged state and the broken line is the released state. Regarding the planetary gear device and the connecting portions of the respective elements, the state related to the gear shifting operation and connected to the output is shown by a solid line, and the unrelated state is shown by a broken line.

In the first speed shown in FIG. 3A, the planetary gear unit G is used.
11 and the planetary gear unit G12 operate in series to perform two-stage deceleration. The brake B2 locks the ring gear R11 of the planetary gear unit G11 and the pinion carrier C12 of the planetary gear unit G12, while the rotation of the input shaft is input to the sun gear S11 of the planetary gear unit G11 via the clutch K3. The double pinion type planetary gear unit G11 in which the ring gear R11 is stopped functions as an inversion reducer, and outputs the rotation in the opposite direction, which is the rotation of the sun gear S11, to the pinion carrier C11. The single pinion type planetary gear device G12 in which the pinion carrier C12 is stopped also functions as a reversing reducer, and reverses the reverse rotation input from the pinion carrier C11 of the planetary gear device G11 to the sun gear S12 to rotate in the forward direction. In addition, the speed is further reduced by one step and output to the ring gear R12. The output of the ring gear R12 is the sun gear S of the planetary gear unit G13.
It is transmitted to the output shaft via 13.

In the second speed shown in FIG. 3B, the planetary gear device G13 is made to function auxiliary to the planetary gear devices G11 and G12 that function similarly to the first speed. The ring gear R1 described above
Instead of being locked by the brake B2, the 1 and the pinion carrier C12 are input with the return output formed by the planetary gear unit G13. Brake B3 is ring gear R1
The planetary gear device G13 in which No. 3 is stopped decelerates the rotation of the output shaft (the ring gear R12 of the planetary gear device G12) and forms a forward return output. The forward return output decelerates the reverse rotation of the pinion carrier C11 of the planetary gear unit G11, but further accelerates the forward rotation of the ring gear R12 of the planetary gear unit G12. The ring gear R12 of the planetary gear device G12 outputs a rotation speed higher than the first speed.

In the third speed of FIG. 3C, the planetary gear unit G is used.
The rotation decelerated by 11 is accelerated by the planetary gear device 12, and deceleration is performed by subtracting both. While the brake B1 locks the pinion carrier C11 of the planetary gear unit G11 and the sun gear S12 of the planetary gear unit G12, the rotation of the input shaft is input to the sun gear S11 of the planetary gear unit G11 through the clutch K3. Double pinion type planetary gear unit G in which the pinion carrier C11 is stopped
Reference numeral 11 functions as a speed reducer, and outputs the forward rotation, which is the rotation of the sun gear S11, from the ring gear R11.
This forward rotation is input to the pinion carrier C12 of the planetary gear unit G12. The single pinion type planetary gear unit G11 in which the sun gear S12 is stopped functions as a speed increasing gear, and outputs the forward rotation in which the rotation of the pinion carrier C12 is speeded up from the ring gear R12.

In the fourth speed shown in FIG. 4A, the clutch K1,
The rotation of the input shaft is directly transmitted to the output shaft by simultaneously fastening K3 and locking the planetary gear unit G12. The rotation of the input shaft is input from the clutch K1 to the ring gear R11 of the planetary gear device G11 via the pinion carrier C12 of the planetary gear device G12. At the same time, the sun gear S1 of the planetary gear device G11 is passed through the clutch K3.
The rotation of the input shaft is also input to 1. As a result, the planetary gear device G11 loses the relative rotation of the sun gear S11 and the ring gear R11, and the entire planetary gear device G11 (the ring gear R11, the pinion carrier C11, the sun gear S1) is lost.
1) rotates integrally with the input shaft while being locked in one meshed state. Therefore, the rotation of the input shaft is directly transmitted to the output shaft. At this time, in the planetary gear device G12, the relative rotation of the sun gear S12 and the pinion carrier C12 is eliminated, and in the planetary gear device G13, the relative rotation of the sun gear S13 and the pinion carrier C13 is eliminated, so that the planetary gear devices G12 and G13 are eliminated. Whole (ring gears R12, R13, pinion carriers C12, C1
3, the sun gears S12, S13) also rotate together with the input shaft while being locked in one meshed state.

In the fifth speed shown in FIG. 4B, the planetary gear unit G1 in which the sun gear S12 is locked by the brake B1.
2 makes a simple speedup. The planetary gear device G12 accelerates the rotation of the input shaft input from the clutch K1 to the pinion carrier C12 and outputs the increased speed to the ring gear R12. The rotation of the ring gear R12 depends on the rotation of the sun gear S of the planetary gear unit G13.
It is transmitted to the output shaft via 13.

In the reverse of FIG. 4 (c), the planetary gear unit G12, which has the pinion carrier C12 locked by the brake B2, produces an inverted deceleration output. The planetary gear unit G12 in which the pinion carrier C12 is stopped reverses the rotation of the input shaft input to the sun gear S12 through the clutch K2 to rotate in the opposite direction, and decelerates and outputs the ring gear R12.

According to the planetary gear type transmission constructed as described above, the planetary gear unit G13 and the brake B are provided.
Depending on the presence or absence of 3, it is possible to easily change the forward four-speed type and the forward five-speed type of the planetary gear type transmission. Even if the forward five-speed type is used, only three clutches and three brakes are required, and the number of parts does not increase as compared with the conventional planetary gear type transmission dedicated to the forward five-speed type. Further, even when the forward four-speed type is adopted, the "gear ratio having a gear ratio of 1 for integrally rotating the planetary gear device G11" and the "overdrive gear position increased by the planetary gear device G12" remain as they are.
It is possible to avoid deterioration of fuel efficiency during high-speed driving. Further, at the gear ratio of gear ratio 1 that is commonly used during traveling, the planetary gear unit G
Since the meshed state of 11, G12, and G13 is locked, friction and heat generation on the tooth surface are suppressed. Further, since the total number of fastening elements is small, less heat is generated due to idling of non-fastened fastening elements. Therefore, fuel efficiency is improved.

Further, as is apparent from the list of FIG. 1B, in the adjacent gear stages of the 1st speed to the 5th speed, one engagement element is kept common and the other engagement element is switched. The shift operation is executed. Therefore, the gear shifting operation becomes smooth, and the gear shifting operation can be completed in a shorter time than when the two fastening elements are switched in order. Further, since there is no shift operation for switching the two fastening elements at the same time, there is no fear of giving a shock to the mechanism of the automatic transmission or the vehicle body due to the shift operation. Therefore, it is possible to provide an automatic transmission in which the gear shifting operation is smooth and fast and the driver is not aware of the gear shifting operation.

In this embodiment, the planetary gear device G11 is the first planetary gear device of the invention, and the planetary gear device G12 is the second invention of the invention.
The planetary gear unit and the planetary gear unit G13 correspond to the third planetary gear unit of the invention, the connecting member N11 is the first connecting unit of the invention, and the connecting member N12 is the second connecting unit of the invention and the connecting member N.
13, N15 (power transmission path via the sun gear S13 of the planetary gear device G13) correspond to the third connecting means of the invention. The connecting member N14 corresponds to the fourth connecting member of the invention, and the connecting member N15 corresponds to the fifth connecting member of the invention.

At least one of these connecting members and other members for transmitting rotational torque in both forward and reverse directions, for example, the connecting member N15 is replaced with "a one-way clutch and a connecting means having a clutch arranged in parallel". Good. The one-way clutch enables the one-way torque transmission to cut off unnecessary engine braking in the first speed, the second speed, etc. On the other hand, when engine braking is required on a downhill, the clutch is engaged to transmit the torque in both directions. And Also, 3
It is also possible to change the gear ratio of the set of planetary gear units G11, G12, G13 to adjust the distribution of the gear ratios of the gears. In addition, the three brakes and the three clutches are disclosed in JP-A-2-
As shown in FIG. 38 to FIG. 48 of No. 159443, a multi-disc clutch, a band brake, and a structure in which a one-way clutch is combined with these can be arbitrarily selected according to the use and purpose.

FIG. 5 shows an example of the assembly structure of the housing in the planetary gear type transmission of the embodiment. here,
Main housing D1 housing a forward four-stage planetary gear type transmission
The sub-housing D12 is connected to the output shaft E2 side of No. 1 to form a forward five-speed planetary gear type transmission. The main housing D11 is
Planetary gear units G11, G12, clutches K1, K2, K
3, the brakes B1 and B2 are held inside to form a "portion A11 enclosed by a broken line" corresponding to the forward four-stage type mechanism of FIG. On the other hand, the sub-housing D12 is a portion A surrounded by a broken line that includes the planetary gear unit G13 and the brake B3.
Holds 12 mechanisms internally.

Pinion carrier C of the planetary gear unit G12
12 and the connecting member N14 for connecting between the pinion carrier C13 of the planetary gear unit G13 is the pinion carrier C1.
2, a pair of parts each having one end fixed to C13 are connected by an intermediate meshing structure. The connecting member N15 that connects between the sun gear S13 of the planetary gear unit G13 and the ring gear R12 of the planetary gear unit G12 connects the component fixed to the sun gear S13 and the component fixed to the ring gear R12 with an intermediate meshing structure. Composed. These meshing structures are arranged at the connecting position of the main housing D11 and the sub-casing D12, and they are brought close to each other in the axial direction to be meshed with each other, and are released away from each other in the axial direction. Then, at the same time when the sub-housing D12 is connected to the main housing D11, the meshing connection of the respective connecting members is completed.

On the other hand, when the sub-casing D12 is removed to form the forward four-stage type, a rear casing (not shown) that rotatably holds the output shaft E2 is used instead of the sub-casing D12 with respect to the main casing D11. Be connected. The connecting member (corresponding to N13) whose one end is fixed to the output shaft E2 has a structure which meshes with the component of the connecting member N15 which is fixed to the ring gear R12 of the planetary gear unit G12, and when the rear case is connected to the main case D11. , The ring gear R12 of the planetary gear unit G12 meshing with each other
To complete contact with the output shaft E2.

According to the housing structure shown in FIG. 5, the planetary gear units G11 and G12, the clutches K1 to K3, and the brake B are included.
Not only 1 and B2, but also the connection structure between the housing and elements, the maximum common parts are realized between the planetary gear type transmission of four forward gears and five forward gears. And the cost of parts can be reduced. Also, instead of adding individual parts, all the necessary parts are incorporated and the units assembled in the factory are connected, so work such as replacement and repair is simplified, and mistakes in parts and various work mistakes are made. It is unlikely to occur.

By the way, the construction of the embodiment is not limited to the arrangement of parts shown in FIG. 1A, and the arrangement order and relative positional relationship of the three planetary gear units, the three brakes, and the three clutches are not limited to the connecting member. It is possible to freely change it according to the convenience of the casing structure, the connecting member, etc. while maintaining the mutual communication state by the above. At this time, the sun gear, the pinion carrier, and the ring gear of the planetary gear device may be connected to the connecting members by selecting the left and right convenient sides. For example, if the brakes B1 and B2 are collectively arranged on the input shaft side in addition to the clutches K1, K2, and K3, the casing-side support structure for these fastening elements, the member that forms the spline that restrains the friction plate, It is possible to reduce the total number of parts by integrating some parts such as a hydraulic cylinder for driving and a hydraulic circuit in common.

The housing structure for accommodating the modified example of such an embodiment is not limited to the structure shown in FIG. 5, and the order of arrangement of the planetary gear units G11, G12, G13 and the convenience of the connecting structure are prioritized. Then, various changes can be made. For example, in FIG.
Instead of dividing into the main casing D11 and the sub casing D12 as described above, an integral casing common to the forward four-stage type and the forward five-stage type is used, and the planetary gear unit G13 and the brake B3 are not incorporated inside. It may be configured to obtain a forward four-stage type. Further, for example, the arrangement of the planetary gear units G12 and G13 in FIG. 1A is replaced, and the housing D1 is divided into two parts, that is, an input shaft side and an output shaft side.
Alternatively, another sub-housing housing 13 and the brake B3 may be inserted and connected between them.

[0044]

According to the planetary gear type transmission of the present invention,
Forward planetary gear type transmission with 4 forward gears and 1 reverse gear is required to add 5 planetary gear units and 1 brake.
A planetary gear type transmission having one gear and one reverse gear can be obtained. Therefore, it is possible to maximize the commonality of components between the four forward gear type and the five forward gear type planetary gear type transmission, and it is easy to reduce the manufacturing cost and improve the reliability. Even when the forward four-stage type is used, the required number of clutches is three and the number of brakes is only two, and it is not necessary to increase these required numbers as compared with the conventional dedicated four-stage forward type. Also, when the forward four-stage type is used, unnecessary planetary gear devices and brakes are removed,
There is no need to worry about holding useless parts inside, or causing wasted parts to spin and increase loss. Therefore, it becomes easy to reduce the size and weight of the planetary gear type transmission, ensure high transmission efficiency and low fuel consumption, and further reduce the manufacturing cost.

When the casing structure is divided and connected according to the distinction between the forward 4-stage type and the forward 5-stage type, the casing parts can be shared between the forward 4-stage type and the forward 5-stage type. Although it is possible, the forward four-stage type can be used as a lightweight and small planetary gear type transmission having a minimum necessary internal volume.

[Brief description of drawings]

FIG. 1 is an explanatory diagram of a configuration of a planetary gear type transmission according to an embodiment.

FIG. 2 is an explanatory diagram of a configuration of a forward four-stage planetary gear type transmission.

FIG. 3 is an operation diagram of the planetary gear device at each shift stage.

FIG. 4 is an operation diagram of the planetary gear device at each shift stage.

FIG. 5 is an explanatory diagram of a housing structure.

[Explanation of symbols]

 B1, B2, B3 Brake K1, K2, K3 Clutch E1 Input shaft E2 Output shaft D1 Housing D11 Main housing D12 Sub housing C11, C12, C13 Pinion carrier G11, G12, G13 Planetary gear unit N11, N12, N13, N14, N15 Connecting member P11, P12, P13 Pinion gear R11, R12, R13 Ring gear

Claims (3)

[Claims] 1. A planetary gear type transmission having a double-pinion type first planetary gear device and a single-pinion type second planetary gear device, which are arranged on the rotation axes of the input member and the output member. A first clutch capable of engaging the pinion carrier of the two planetary gear device with the input member, a second clutch capable of engaging the pinion carrier of the first planetary gear device with the input member, and a first planetary gear device. Third clutch that can fasten the sun gear to the input member, a first brake that can stop the rotation of the pinion carrier of the first planetary gear device, and a rotation of the pinion carrier of the second planetary gear device. A second brake, a first connecting means for rotationally connecting between a ring gear of the first planetary gear unit and a pinion carrier of the second planetary gear unit, and a pin of the first planetary gear unit. It has a second connecting means for rotationally connecting between the on-carrier and the sun gear of the second planetary gear device, and a third connecting means for rotationally connecting between the ring gear of the second planetary gear device and the output member. A planetary gear type transmission capable of shifting four forward gears and one reverse gear. 2. A planetary gear type transmission having a double-pinion type first planetary gear device and a single-pinion type second planetary gear device, which are arranged on the rotation axes of the input member and the output member. A first clutch capable of engaging the pinion carrier of the two planetary gear device with the input member, a second clutch capable of engaging the pinion carrier of the first planetary gear device with the input member, and a first planetary gear device. Third clutch that can fasten the sun gear to the input member, a first brake that can stop the rotation of the pinion carrier of the first planetary gear device, and a rotation of the pinion carrier of the second planetary gear device. A second brake, a first connecting means for rotationally connecting between a ring gear of the first planetary gear unit and a pinion carrier of the second planetary gear unit, and a pin of the first planetary gear unit. A second connecting means for rotationally connecting between the on-carrier and the sun gear of the second planetary gear device, and a third connecting means for rotationally connecting between the ring gear of the second planetary gear device and the output member; Third single pinion type arranged on the axis of rotation
A planetary gear unit and a third planetary gear unit capable of stopping the rotation of the ring gear.
A brake, a fourth connecting means for rotationally connecting the pinion carrier of the third planetary gear set and the pinion carrier of the second planetary gear set, and a sun gear of the third planetary gear set and a ring gear of the second planetary gear set. A planetary gear type speed change device capable of performing five forward speed shifts and one reverse speed shift, characterized by being provided with a fifth connecting means for rotational communication. 3. A first planetary gear device, a second planetary gear device,
A sub-housing structure connectable to a main housing structure storing the first clutch, the second clutch, the third clutch, the first brake, and the second brake, and the sub-housing structure includes a third planetary gear device. The planetary gear type transmission according to claim 2, further comprising a third brake.