JPH0276952A - Planetary gear type transmission - Google Patents

Abstract

PURPOSE:To facilitate the speed change control by locating a primary and a secondary single pinion type planetary gear on the same axis via a double pinion type planetary gear mechanism and selectively operating a primary to a third clutch and a brake. CONSTITUTION:A primary and a secondary single pinion type planetary gear mechanism 20 and 30 are located on the axis common to that of both an input shaft 10 and an output shaft 12 via a third double pinion type planetary gear mechanism 40. And a primary and a third carrier 28 and 48, a primary ring gear 24, a secondary carrier 38, a third sun gear 42, an output shaft 12, a secondary and a third ring gear 34 and 44 are connected to each other. The engagement of a clutch C1 with a brake B1 offers the first shift state, the engagement of C1 with B3 the third shift state, the engagement of C1 with C2 the fourth shift state, the engagement of C2 with B3 the fifth shift state, the engagement of C3 with B2 the rear first shift state, and the engagement of C3 with B1 the rear second shift state. So by change-over of two speed changing friction engagement devices, the shift to the next position may be facilitated, and the relative revolution speed of each of planetary pinions to the carriers is low so that the durability may be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a freewheel type transmission device incorporated in an automatic transmission used in a vehicle such as an automobile.

[Prior Art] Planetary gear type transmissions incorporated in automatic transmissions used in vehicles such as automobiles have been proposed in various configurations, one of which is a two-set single-binion type transmission. There is a type that combines a planetary gear mechanism with a set of double pinion type planetary gear mechanisms, which achieves five or more forward gears and one or more reverse gears. It is now possible to do so. This type of planetary gear type transmission device is disclosed in, for example, Japanese Patent Application Laid-Open Nos. 51-48062, 1977-1.7767, and 51-1081.
No. 68, JP-A-51-108170, JP-A-51-1
No. 27968.

[Problems to be Solved by the Invention] Generally, in automatic transmissions used in vehicles such as automobiles, the gear ratio of each planetary gear mechanism is appropriate and the outer diameter of each planetary gear mechanism is The rotational speed of the planetary binion relative to the carrier in each planetary gear mechanism should be small from the viewpoint of durability. In addition, the gear ratios of the forward gears from the first gear to the direct gear are set to values close to a geometric series, and in order to balance power performance, fuel efficiency, and quietness, the gear ratios of the forward gears ( (overdrive stage) is required to have an appropriate gear ratio.

An object of the present invention is to provide a planetary gear type transmission with a new structure that satisfies all of the above-mentioned requirements.

[Means for Solving the Problems] According to the present invention, the object as described above is to provide a first single-binion type planetary gear having an input member, an output member, a sun gear, a ring gear, a planetary binion, and a carrier. a second single-binion type planetary gear mechanism having a sun gear, a ring gear, a planetary binion, and a carrier; and a double-pinion type planetary gear mechanism having a sun gear, a ring gear, two planetary binions that mesh with each other, and a carrier. a first clutch that selectively connects the sun gear of the second single-binion planetary gear mechanism and the input member; a carrier of the first single-binion planetary gear mechanism and the input member; a third clutch that selectively connects the sun gear of the first single-binion type planetary gear mechanism and the input member to each other; and a third clutch that selectively connects the sun gear of the first single-binion type planetary gear mechanism and the input member to each other; a first brake that selectively fixes a ring gear of a planetary gear mechanism; a second brake that selectively fixes a carrier of the first single pinion type planetary gear mechanism and a carrier of the double pinion type planetary gear mechanism; , a third brake for selectively fixing the sun gear of the first single-binion type planetary gear mechanism, and a carrier of the first single-binion type planetary gear mechanism and a third brake of the double-pinion type planetary gear mechanism. the carriers are connected to each other, and the ring gear of the first single-binion type planetary gear mechanism, the carrier of the second single-binion type planetary gear mechanism, and the sun gear of the double-pinion type planetary gear mechanism are connected to each other, The ring gear of the second single-binion type planetary gear mechanism and the ring gear of the double-pinion type planetary gear mechanism are connected to each other, and the carrier of the second single-binion type planetary gear mechanism is connected to the output member. This is achieved through a planetary gear transmission.

[Operations and Effects of the Invention] According to the above-described configuration, the tooth ratio of each planetary gear mechanism is appropriate, and the outer diameter of each planetary gear mechanism is not very thick (but the degree of freedom in miniaturization design is increased). , speed changes such as upshifts and downshifts in forward gears are easily performed by switching between two frictional engagement devices for speed change control such as clutches or brakes. The relative rotational speed is low and excellent durability is achieved, and on top of that, the gear ratios of the forward gears from the first gear to the direct gear are set to values close to a geometric series, and the speed increasing gears (overdrive The gear ratio of the two gears is set to an appropriate value, achieving a balance between power performance, fuel efficiency, and quietness.

[Example] The present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 shows one embodiment of a planetary gear type transmission according to the present invention. In Figure 1, 10 indicates the input shaft, 12
20 shows the output shaft, 20 shows the first single pinion type planetary gear mechanism, 30 shows the second single pinion type planetary gear mechanism, and 40 shows the double pinion type planetary gear mechanism. placed on the line.

The input shaft 10 is configured to receive rotational power from a prime mover such as an internal combustion engine (not shown) via a well-known hydraulic torque converter, electromagnetic clutch, or the like.

The first single pinion type planetary gear mechanism 20 includes a sun gear 22, a ring gear 24 concentric with the sun gear 22, a planetary pinion 26 that meshes with the sun gear 22 and the ring gear 24, and a carrier 28 that rotatably supports the planetary pinion 26. It has a single pinion type planetary gear mechanism suitable for boat fishing.

The second single pinion type planetary gear mechanism 30 includes a sun gear 32, a ring gear 34 concentric with the sun gear 32, a planetary pinion 36 that meshes with the sun gear 32 and the ring gear 34, and a carrier 38 that rotatably supports the planetary pinion 36. It has a single pinion type planetary gear mechanism suitable for boat fishing.

The double pinion type planetary gear mechanism 40 includes a sun gear 42, a ring gear 44 concentric with the sun gear 42, and two planetary pinions 46 that mesh with each other, one of which meshes with the sun gear 42 and the other with the ring gear 44.
and 47, and a carrier 48 rotatably carrying two planetary pinions 46 and 47, respectively, -
It has a double pinion type planetary gear mechanism similar to boat fishing.

Carrier 28 of the first single pinion type planetary gear mechanism 20 and carrier 4 of the double pinion type planetary gear mechanism 4O
8 and are connected to each other by a first connecting member 50.

The ring gear 24 of the first single pinion type planetary gear mechanism 20, the carrier 38 of the second single pinion type planetary gear mechanism 30, and the sun gear 42 of the double pinion type planetary gear mechanism 40 are connected to each other by a second connecting member 52. ing.

The link gear 34 of the second single pinion type planetary gear mechanism 30 and the ring gear 44 of the double pinion type planetary gear mechanism 40 are connected to each other by a third connecting member 54.

Note that the first connecting member 50, the second connecting member 52, and the third connecting member 54 do not necessarily need to be constructed as special separate members, and the members that are connected to each other by the connecting member 5052 or 54 are connected. The parts 50, 52, 54 may be directly connected to each other by means of connecting portions, or may be constructed in one piece with each other.

A carrier 38 of the second single pinion planetary gear mechanism 30 is connected to the output shaft 12 .

Further, the planetary gear type transmission according to the present invention includes three clutches, namely, a first clutch C+, a second clutch C2, and a third clutch C3, and three brakes, namely a first brake B.
+, second brake B2, and third brake l.
Ru. These clutches and brakes may be of a multi-plate type.

The first clutch C1 selectively connects the sun gear 32 of the second single pinion type planetary gear mechanism 30 and the input shaft 10 in a torque transmission relationship.

The second clutch C2 selectively transmits torque between the first connecting member 50, that is, the carrier 28 of the first single pinion type planetary gear mechanism 20 and the carrier 48 of the double pinion type planetary gear mechanism and the input shaft 10. It is designed to be connected in a relational relationship.

The third clutch C3 selectively connects the sun gear 22 of the first single pinion type planetary gear mechanism 20 and the input shaft 10 in a torque transmission relationship.

The first brake B1 is configured to selectively connect the third connecting member 54, that is, the ring gears 34 and 44, to the transmission case 60 and selectively fix this.

The second brake B2 is configured to selectively couple the first coupling member 52, ie, the carriers 28 and 48, to the transmission case 60 to selectively fix it.

The third brake l connects the sun gear 22 of the first single pinion type planetary gear mechanism 20 to the transmission case 60.
It is designed to be selectively connected to and selectively set in a fixed state.

In the planetary gear type transmission having the above configuration,
Three clutches CI, C2, C3 and three brakes B
1, B2, and l are engaged and released in a predetermined combination, thereby creating a first gear, a second gear, and a third gear as reduction gears, and a fourth gear as a direct coupling gear. A fifth gear as an overdrive gear and also one or two reverse gears are achieved. Clutches CI, C2, C3 in this case
and brake B1. , B2, & are shown in FIG.

In FIG. 2, O marks indicate engagement, and no marks indicate release. Further, the Δ mark indicates that the engagement may be performed.

The gear ratios in each of the above-mentioned gear stages are shown in FIG. However, ρ1 is the ratio of the number of teeth between the sun gear 22 and the ring gear 24 of the first single-binion type planetary gear mechanism 20, and ρ2
is the ratio of the number of teeth between the sun gear 32 and the ring gear 34 of the second single pinion type planetary gear mechanism 30, and ρ3 is the ratio of the number of teeth between the sun gear 42 and the ring gear 4 of the double pinion type planetary gear mechanism 40.
This is the ratio of the number of teeth to 4. Figure 2 also shows ρ, -0.38
5, ρ2 - 0.395, and ρ3 = 0.557, the real values of the gear ratio of each gear stage are shown.

Next, the operation of each gear stage of the planetary gear type transmission constructed as described above will be explained with reference to FIGS. 3 to 9.

Note that in FIGS. 3 to 9, thick lines indicate rotating elements that actually contribute to torque transmission at each gear stage.

The first gear is set to the sun gear 3 by engagement of the first clutch C1.
2 is connected to the input shaft 10, and the ring gear 34 is fixed by engagement of the first brake BI. At this time, the sun gear 32 becomes the input element and the ring gear 34 becomes the reaction force element, as shown in FIG.
The rotational force applied to the sun gear 32 from the input shaft 10 is transferred from the carrier 38 to the output shaft 1 via the planetary pinion 36.
2. Therefore, the gear ratio of the first gear is (1+ρ2
)/ρ2.

The second gear is set to sun gear 3 by engaging the first clutch C+.
2 is connected to the input shaft 10, and the carrier 48 is fixed by engagement of the second brake B2.

At this time, the sun gear 32 becomes an input element, and the carrier 4
8 is a reaction force element, and as shown in FIG.
A part of it passes through the second connecting member 52 and reaches the sun gear 42, and from there the planetary pinion 46
．． 47, the ring gear 44, the third connecting member 54, the ring gear 34, the carrier 38 via the planetary pinion 36
Return to Therefore, the gear ratio of the second gear is (1-ρ2+ρ3)
/ρ2.

The third gear is set to the sun gear 3 by engagement of the first clutch C1.
2 is connected to the input shaft 10, and the sun gear 22 is fixed by engaging the third brake &.

At this time, sun gear 32 becomes an input element, and sun gear 2
2 is a reaction force element, and as shown in FIG. 24 and sun gear 42, and the rotational force applied to the ring gear 24 is transmitted from the carrier 28 to the first connecting member 50 via the planetary pinion 26.
The rotational force applied to the carrier 48 and the sun gear 42 is transmitted to the carrier 48, and both of them are transmitted to the ring gear 34 via the planetary pinions 46, 47, the ring gear 44, and the third connecting member 54, and further to the planetary pinion 46, 47, the ring gear 44, and the third connecting member 54. It returns to the carrier 38 via the pinion 36 and is transmitted from there to the output shaft 12. Therefore, the gear ratio of the third gear is (ρ2 (1+ρ1)+ρ1 (1-ρ3))/ρ2
(1+ρI).

The fourth gear is a direct-coupling gear, which is achieved by engagement of the first clutch CI and the second clutch C2.

At this time, a rotational force is applied to the sun gear 32 and the first connecting member 50, so that the second single pinion type planetary gear mechanism 30 and the double pinion type planetary gear mechanism 40
are in a locked state, and the rotational force of the input shaft 10 is transmitted through the second single pinion type planetary gear mechanism 30, the second connecting member 52, the third connecting member, and the double pinion type planetary gear mechanism 40 to change gears. It is transmitted to the output shaft 12 without being transmitted. The rotational force transmission relationship when the fourth gear is achieved is shown in FIG.

The fourth gear, which is a direct gear, has three clutches C1 and C.
It is only necessary that two of the clutches 2 and C3 are engaged at the same time, for example, the first clutch C1 and the third clutch C3.
This can also be achieved by engagement with

The fifth speed is achieved by connecting the carrier 28 to the input shaft 10 by engaging the second clutch C2, and fixing the sun gear 22 by engaging the third brake &. At this time, the carrier 28 becomes an input element, the sun gear 22 becomes a reaction force element, and as shown in FIG. The signal is transmitted from the carrier 38 to the output shaft 12 via the second connecting member 52 .

Therefore, the gear ratio of the fifth gear is 1/(1+ρI).

The reverse gear is set to sun gear 2 by engaging the third clutch C3.
2 is connected to the input shaft 10, and the carrier 28 is fixed by engagement of the second brake B2.

At this time, the sun gear 22 becomes an input element, and the carrier 2
8 is a reaction force element, and as shown in FIG. The signal is transmitted to the output shaft 12 via. Therefore, the gear ratio of the reverse gear is -17ρ1.

The reverse gear is also achieved by engaging the third clutch C3 and first brake B1 instead of engaging the third clutch C2 and second brake B2. In this case, the ring gear 44 becomes a reaction force element, and as shown in FIG.
The rotational force applied to the sun gear 22 from O is transmitted to the output shaft 12 from the ring gear 24 via the planetary pinion 26 as described above, and a part of it is transmitted from the carrier 28 via the planetary pinion 26 to the first connecting member. 50
The signal is transmitted to the carrier 48 via the planetary pinion 46, 47, and then to the sun gear 42, where it is transmitted to the output shaft 1.
2. Therefore, the gear ratio of reverse gear in this case is -
(1+ρ1ρ3)/ρwealth (1-ρ3).

FIG. 10 shows another embodiment of the planetary gear type transmission according to the present invention. The only difference between the embodiment shown in FIG. 10 and the embodiment shown in FIG. m1 is the relative positional relationship of each element, and their relative connection relationship is the same.

Therefore, in the embodiment shown in FIG.
7, C2, C3 and brake B! , B2, and bottles are engaged and disengaged in the combination shown in FIG. 2, thereby achieving gears similar to the embodiment described above.

In the planetary gear type transmission according to the present invention, the clutch C
1, C2, C3 and brakes B1, B2, Ba Ha'7
The brakes B+, Bt, and l may be replaced with a single-disc clutch, or may be used in combination with a one-way clutch in series or in parallel, and the brakes B+, Bt, and l may be band-type in addition to multi-plate types. These variations are generally shown diagrammatically in FIG.

Next, the symbols shown in FIG. 11 will be explained.

Explanation of symbols When a one-way clutch is installed in series with a brake or clutch, or in place of them, the fuel efficiency and quietness of the prime mover are improved by canceling the engine braking action, and the shift timing becomes easier to adjust due to the slippage of the one-way clutch. , speed change control becomes easier to perform.

If engine braking is required, another brake or clutch may be provided in parallel to the series connection of the brake or clutch and the one-way clutch.

FIG. 12 shows one specific embodiment of this modification. In this embodiment, a series connection body of clutch C4 and one-way clutch OW C+ is provided in parallel with first clutch CI, and one-way clutch OW C2 is provided in series with first brake BI, and one-way clutch OW C+ is provided in series with brake &. A series connection body with the one-way clutch OW Cs is provided in parallel with the second brake B2, and a series connection body with the brake & and the one-way clutch 0WC4 is provided in parallel with the third brake l.

[Brief explanation of the drawing]

FIG. 1 is a skeleton diagram showing one embodiment of a planetary gear type transmission according to the present invention, and FIG. 2 is a diagram showing the engagement of clutches and brakes at each gear stage of the planetary gear type transmission shown in FIG. FIGS. 3 to 9 are skeleton diagrams showing the operational states of each gear of the planetary gear type transmission shown in FIG. 1, and FIG. 11 is a diagram showing various examples of combinations with a friction engagement device one-way clutch, and FIG. 12 is a planetary gear type transmission according to the present invention. It is a skeleton diagram showing a concrete modification example of. DESCRIPTION OF SYMBOLS 10... Input shaft, 12... Output shaft, 20... First single pinion type planetary gear mechanism, 22... Sun gear. 24...Ring gear, 26...Planetary pinion. 28... Carrier, 30... Second single pinion type planetary gear mechanism, 32... Sun gear 134... Ring gear, 36... Planetary binion, 38...
Carrier, 40...Double pinion type planetary gear mechanism,
42...Sun gear, 44...Ring gear, 46.4
7...Planetary binion, 48...Carrier, 5
0: first connecting member, 52: second connecting member,
Cbi...first clutch, C2...second clutch,
Cs...Third clutch. B1...first brake, B2...second brake,
B3...Third brake patent applicant: Toyota Motor Corporation representative
Patent Attorney Akashi RokiFigure 3Figure 4Figure 10

Claims (1)

[Claims] A first single pinion type planetary gear mechanism having an input member, an output member, a sun gear, a ring gear, a planetary pinion, and a carrier, and a second single pinion type planetary gear mechanism having a sun gear, a ring gear, a planetary pinion, and a carrier. and a double pinion type planetary gear mechanism having two planetary pinions and a carrier that mesh with a sun gear and a ring gear, and selectively coupling the sun gear of the second single pinion type planetary gear mechanism and the input member to each other. a first clutch, a second clutch that selectively connects the carrier of the first single pinion type planetary gear mechanism and the input member to each other, a sun gear of the first single pinion type planetary gear mechanism and the input member a third clutch that selectively connects the first brake to selectively fix the ring gear of the second single-pinion planetary gear mechanism; a carrier of the first single-pinion planetary gear mechanism; a second brake that selectively fixes the carrier of the double pinion type planetary gear mechanism; and a third brake that selectively fixes the sun gear of the first single pinion type planetary gear mechanism; A carrier of the single pinion type planetary gear mechanism and a carrier of the double pinion type planetary gear mechanism are connected to each other, and a ring gear of the first single pinion type planetary gear mechanism and a carrier of the second single pinion type planetary gear mechanism are connected to each other. A sun gear of the double pinion type planetary gear mechanism is connected to each other, a ring gear of the second single pinion type planetary gear mechanism and a ring gear of the double pinion type planetary gear mechanism are connected to each other, and a ring gear of the second single pinion type planetary gear mechanism is connected to each other. A planetary gear type transmission, wherein a carrier of a planetary gear mechanism is connected to the output member.