JPS60205065A - Starting device - Google Patents

Abstract

PURPOSE:To secure such a starting device as being compact in size and excellent in efficiency, by connecting one side input element of a planetary gear mechanism to an output element of a clutch, while the other side input element directly to another output element of a hydraulic power transmission, respectively. CONSTITUTION:In times of neutral and speed shifting, a clutch mechanism 2 inside a starting device 1 is set free whereby a ring gear R1 of a dual planetary gear set 3 is rotated with some play, making a carrier P1 come into zero. And, in time of power transmitting, the clutch mechanism 2 is always engaged in advance. Therefore, excellent fuel consumption capacity like in case of a high gear clutch is attainable and, what is more, connection or disconnection of power comes to be performable so easily owing to disengagement of the clutch 2.

Description

[Detailed description of the invention]

Field E] The present invention is based on the fluid development 88! It is related to d for both starting and moving the position to the right. [Conventional technique 1] The fluid transmission 8 device conventionally used as a promotion device has a spacious and excellent starting performance and can withstand harsh usage conditions (q
Because of its high reliability, it has been used for a long time in medium-sized automatic transmissions and semi-automatic transmissions. However, the fluid transmission device has the following functional vacancies. That is, (1) There is a slip loss because the power transmission is performed by converting the fluid motion into m. (2) Transmission and isolation of motion is a fluid transmission device.

[No is 1
I can't sleep. There are two points. Regarding the disadvantage of (1) above, vehicles using fluid transmission devices [give users the impression that they have poor fuel efficiency and poor acceleration]. Difficult, also has shortcomings (2
), excellent starting performance and damping performance (, [
This has narrowed the scope of application of fluid transmission devices with damping of engine rotation fluctuations. However, it has been limited to transmissions (automatic or semi-automatic transmissions, which are usually used), in which the power can be switched on and off freely. (1
), a direct coupling clutch (imaginary, sub-1 ~ drive mechanism, etc.) was developed, and in response to disadvantage (2), a fluid transmission device and a moving horn 1lIl! disconnection clutch (imaginary) were developed. By the way, in recent years, the cost, power performance, = 1 stroke, and reliability Ap have become important issues for heavy-duty transmissions, and conventional hydraulic 1 It has become clear that the transmission using a novo device and a planetary gear has a fundamental limit (
cost, weight, ]”Nbaku1~Sex @). Therefore, in order to break through these barriers, 7i 11. ) Mesh type transmission (usually called Mayu1Al1~Lance transmission -C
The automation of the fluid transmission system has been examined, and many prototypes have been made. Since r does not cut off the power, it requires a separate first h''m19i11J clutch. Advantages of using a dog-type transmission 1 - 4 By precisely automatically controlling the dry clutch to maximize output (a /j method has been developed to solve this problem, ADL 911
Traditional fluid transmission in terms of complexity, reliability and starting performance! P.I.
It can be said that it is inferior to J. [Object of the Invention] The object of the present invention is to solve the problem of the previous rlL! The object of the present invention is to provide a starting device that solves the two drawbacks, has a wide range of application, is highly reliable, highly efficient, and can be obtained in the most compact form. [Structure of the Invention] The optical system of the present invention includes an input shaft, an output shaft coaxially disposed with the input shaft, and a CC fluid initialization device 6 disposed between the input shaft and the output shaft. A club installed between the input shaft and the output shaft in parallel with the fluid transmission device.
mechanism, a play disposed between the output shaft, the output element of the fluid control device, and the output element of the clutch! i
33 of the said meeting 11 and middle mechanism.
One of the two elements, the human-powered 91 rope, is connected to the clutch machine (
14, the other input element is directly connected to the output element of the fluid transmission device, and the output element is connected to the output shaft. [Effects of the Invention] In addition to the above configuration, the starting device of the present invention has the following effects. b) The power can be engaged and disengaged by turning ON/OFF the Kuratu °J mechanism in the optical system, and it can also be applied to a constant mesh gear transmission.口）The split drive system allows the engine to move faster; the efficiency is J, and the fuel efficiency is excellent. c) All 81 functions are placed in the shell of the fluid transmission device, and the assembly is excellent in 21 units and 1~. -) In particular, if you use an idler W gear machine (14, -L planetary gear L), the rotation direction of the ring gear at the time of clap-OFF is 74. When the directions are the same, the relative rotational speed becomes smaller and the engagement of the comb f-ON -OF Il', ', i becomes smaller.J, since the relative rotational speed difference is small, the crack yk4k is caused by f1. Since the clutch for the 8-force i1MIIJi and the clutch for the MIIJi are not required individually, it is compact and only requires 21 strokes. Then, the Jrua, IJ III system attached to the starting device is converted to Combat 1. The first embodiment of the Start I! device of the invention is incorporated into a constant-mesh type mountain transmission with five forward speeds and one reverse speed. 1 is an optical gear: a, 100 is a constant-mesh type gear ■1 The transmission (hereinafter referred to as gear transmission), 200 is a differential mechanism. In this embodiment, the inverter 1 includes a planetary gear mechanism 3, a pump shell 13 is welded to the end of a cover 12, and a pump shell 13 is welded to the end of a cover 12, and blades are assembled in the shell 13. fJ rear I pump impeller 14 and planetary gear mechanism 3
and a turbine launch connected to an output shaft 15 disposed coaxially with the input shaft 11 via a planetary key puller/rear 20, and disposed between the mount cover 12 and the pump impeller 14. 16, and a stay 9 connected to the fixed part 18 of the gear transmission via the -/J direction nail 11.
It consists of 19. In front of the clutch Hi42 LL, the torque converter is provided in parallel in the front cover 12, and the inner periphery of the friction retaining surface 21 formed on the inner surface of the front cover 12 is the 111 star tooth IJJ lit 4143 and the planet. 1 to 1 is connected to the output shaft 15 via the spear 720,
It consists of a clutch disc 23 having a damper 22 disposed between the front cover 12 and the turbine launch 1G. As shown in FIG. 2, the planetary gears 1 and 3 are dual planetary gear sets 1~, and the planetary gear mechanism (hereinafter referred to as dual planetary gear sets 1~) 3 is connected to one input. The other input element is a ring gear R1, which is removably connected to the torque converter via the clutch structure 2, and a turbine launch 1 of the torque converter, which is the other input element.
6, a ring gear S1 formed on the Zang gear shaft 31a, which is connected to the output shaft 15 via a planet carrier 20, and a ring gear S1 formed on the Zang gear shaft 31a, which is an output element and is connected to the output shaft 15 via a planet carrier 20, and It consists of planetary binions Ppl and Pp2 supported by. Gear shift l! 100 is the output shaft 15 of the optical advance lock 1, and is composed of an input shaft (15) of the gear transmission 100, and an output shaft 105 arranged in parallel with the human power shaft (1!i), Furthermore, a gear transmission l1100 is provided with J3 in a gear transmission case (not shown) and is connected to an input shaft (15) for first speed and second speed.
Speed and I drive gears 111, 112 and 4
18 are integrally provided, and drive gears 113, 114, and 115 of third speed, fourth speed J5, and fifth speed are rotatably fitted to the output shaft 105, and each of the drive gears 111, 112, 113 is connected to the output shaft 105. , 114 and 11
Driven gears 121, 122, 12 of 1st gear, 2nd gear, 3rd gear, 4th gear J3, and 5th gear that always mesh with each other.
3, 124 a3 and 125 are integrally or rotatably fitted together. Also, the adjacent 211i1 driven 1 near 121,
122 is engaged and disengaged by first and second speed shift forks (not shown), and is connected to a sleeve 126a and a synchronizer hub 1.
26b. Clutch hub 126c, Onibi gear spline 126d
The dog clutch 126 for switching between the first and second speeds is selectively connected to the output shaft 105, and the dry 1st gear '113
, 114 are similarly connected to and disengaged from the third and fourth gear shifts (not shown), and include a sleeve 117a, a synchronizer hub 117b, a clutch hub 117C, and a gear spline 117d. selectively coupled to the input shaft (15) with a dog clutch 117,
The sleeve 129a and the synchronizer hub 129b are engaged and disengaged by a 5th speed shift lever (not shown). The fifth speed switching dog clutch 129, which is equipped with a clutch hub 129C and a gear spline 129d, is selectively coupled to the input horn shaft (15), and is further connected via a reverse drive gear 418 and an idler gear 419. A driven gear 428 that meshes with each other is provided. Further, a gear 164 is provided in the drive section of the output shaft 105, which meshes with the differential input gear 201, which is the input gear of the differential mechanism 200, and rotates to the differential case 205 integrally connected to the differential input gear 201. It consists of a freely connected differential small gear 202 and a differential man gear 203 meshed with the external small gear 202, and the power of the output shaft 105 is transmitted to the differential small V gear 202 and the differential large gear 203. It is further transmitted to the drive shaft via the axle 204. The operation of the present invention will be explained based on FIGS. 1 to 3. Neutral and odd 3! ! ! At this time, by releasing the clutch mechanism 2 in the starting device 1, the ring of the dual bushine gear LT 3, 1a1<1, is rotated freely, and the output of the Kirelia P1 is set to O. In addition, the clutch mechanism 2 is always engaged when transmitting power. By doing this, the 1+ force is transferred to the hydraulic path of the pump impeller 14 → fluid → turbine lamp 1G path,
There are two mechanical paths in between: pump impeller 14 -> crack I-1 set M2 -> ring gear R1 Red Road, which are combined and output at Kitria P1. Therefore, the transmission efficiency of this starting device 1 is excellent as shown in tA in FIG. 3 (B is the transmission efficiency of only the conventional fluid transmission device). For this reason, it is possible to achieve excellent fuel efficiency similar to the direct coupling clutch (11 Tsukuno'Tsubukuratsu J) mechanism, and at the same time, the engagement and disengagement (ON) of the clutch mechanism 2 can be achieved.
, 0FF), power can be easily connected. Here, use dual planetary gears 1 to 3 in the clt1 star gear mechanism.In this case, set the free rotation direction of the cludge mechanism 2OFFII temple ring gear 'R1 and the rotation direction of the pump impeller 14 in the same horn direction. This is to reduce the engagement shock caused by ON-OFF of the clutch device 41ii2 and at the same time increase the durability of the clutch mechanism 2.The following are other embodiments of the present invention. 1.t in Figures 4 to 8.
I will explain further. FIG. 4 is a second practical example of the present invention in which the starting axis is perpendicular. In this embodiment, a 7-unit coupling (hereinafter referred to as "coupling") F is used for the fluid transmission, and the coupling F is the end of the flap L1 fixed to the input shaft 11 to the cover 12. The stage number is marked inside the pump shell.1. : The pump blade 31, the turbine blade 32 provided opposite to the pump blade 31, and the dual planetary gear set 3 are one input element, and are connected via the clutch mechanism 2 (to the pump blade 31). The ring gear R2 is removably connected, and -1-tria P2, which is another human power element and is directly connected to the turbine blade 32,
It is an output quality system, and consists of a sun gear S2 directly connected to the output shaft 15, and planetary pinions Pp1 and pp2 rotatably supported by the -1 and spear 7P2. FIG. 5 shows a third embodiment of the starting IHEF of the present invention. Hereinafter, the equivalents are the same as those in 6 of the second embodiment.
is one input element, such as the Clara F (Kirlia P3, which is detachably connected to the pump blade 31 via the fiction 2), and the other input element is the 1 non-gear, which is directly connected to the turbine blade 32. A ring gear S3 formed on the shaft 31a, a ring gear R3 which is an output shaft and is directly connected to the output shaft 15, and a ring gear A which is rotatably supported on the shaft 71]3. pl, Pp
It consists of 2. FIG. 6 shows a fourth embodiment of the starting device of the present invention. In this embodiment, the dual planetary gear set 3 is -h
The ring gear j'+b31 is a human power element and is detachably connected to the pump blade 31 via the clutch i structure 2.
A]yng gear S4 and other input elements are connected directly to the turbine blades 32! , 'link gear [4], output 91 thread, and consists of a kitria P4 directly connected to the output shaft 15, and planetary binions Ppl and Pp2 rotatably supported by the 4-toria P4. 7th MeiG, Kimitsu 1! y of l]? , this is the fifth example of Shinkomori. In this embodiment, the digital planetary gear set 1-3 is one manual element, and includes a kitria P5 which is detachably connected to the C pump route 31 via the clutch doctor 4M2.
The ring gear R5 which is the other input horn element and is directly connected to the turbine blade 32; the Zang gear 7S which is the output element and which is directly connected to the output shaft 15;
- From planetary pinions Ppl and Pp2 rotatably supported by the rear []5. FIG. 8 shows a sixth embodiment of the starting device of the present invention. In this embodiment, the dual planetary gear set 3 is -7
The pump blade 31 is detachably connected to the pump blade 31 via the crudging mechanism 2, and the pump blade 31 is connected to the pump blade 31 via the clutch mechanism 2.
a sun gear S6 formed in a, a kitria P6 which is another human power element and is directly connected to the targon runner 1G, an output element which is directly connected to the output shaft 15 and an I-ring gear R6, and the above-mentioned Kitoria P6 rotates white and supports E (,
) consists of planetary pinions Pp1, Pp2, etc. 4. Simple 111-1 Explanation of the same song Figure 1 is a skeletal diagram of a constant-mesh type south-center transmission incorporating the first embodiment of the starting device of the present invention, and Figure 2 is a schematic diagram of a planetary gear. 3 is a graph showing the power transmission efficiency of the first embodiment of the R-advance 1ζ1 of the present invention, FIG. 4 is a skeletal diagram of the second embodiment of the starting device of the present invention, and FIG. Figure 1 is a skeleton diagram of the fourth embodiment of the starting device of the present invention, Figure 7 is a skeleton diagram of the fifth embodiment of the launching device of the present invention, Fig. 8 is a skeleton diagram of a sixth embodiment of the starting device of the present invention. In the figure: 1... Starting device 2... Clutch 11 structure 3
...@Seiji 11 Mechanism (Dual Planetary 1 Bit) 11...Input shaft 14...Pump impeller 1
5... Output shaft 16... Turbine runner 19...
Stator 31...Pump blade 32...Turbine blade F...Free'ite coupling P
I, R2, R3, R4,1)! +, R6...ki I
? Rear [)pl,]] p2... Planetary pinion R+, R2, R3, R4, R5, R699, Ring gear Sl, S2, S3, S4, S5, S6... Ring gear T... Torque converter agent Kenji Ishiguro / 21st No.j

Claims (1)

[Scope of Claims] 1) An input shaft, an output shaft disposed coaxially with the input shaft, a fluid transmission device disposed between the input shaft and the output shaft, and the input shaft and the output shaft. a clutch i structure provided between the shaft and the fluid transmission device in parallel; and 11 star teeth arranged between the output shaft, the output element of the fluid transmission device, and the output element of the clutch. 11! one input element of the planetary tooth width mechanism is connected to an output element of the cludge mechanism, the other helical chord is directly connected to an output element of the fluid transmission device, and the output element is Starting device connected to the output shaft n02) The 1M gear mechanism is a Deco Albra net gear set! - Start-up according to claim 1, characterized in that: -! ! i@. 3) l) The starting device according to claim 1, wherein the output shaft of i1 is an input shaft of a constant-mesh type south-center transmission.