WO2000004300A1

WO2000004300A1 - Torque converter for automatic transmission

Info

Publication number: WO2000004300A1
Application number: PCT/KR1999/000226
Authority: WO
Inventors: Woong Bae Oh; Jong Kun Lim
Original assignee: Woong Bae Oh; Jong Kun Lim
Priority date: 1998-07-16
Filing date: 1999-05-08
Publication date: 2000-01-27

Abstract

Disclosed is a torque converter for an automatic transmission, mounted between an output shaft of an engine and an input shaft of the automatic transmission for transferring engine power to the automatic transmission. The torque converter comprises a rotary housing connected to the input shaft of the automatic transmission and formed with a gear room having a main gear room in which a main gear connected to the output shaft of the engine is mounted and at least one auxiliary gear room which is arranged at a side of the main gear room and in which at least one auxiliary gear meshing with the main gear is mounted, the rotary housing having first and second space portions arranged at upper and lower parts of the gear room, respectively, between the main gear room and the auxiliary gear room, the first and second space portions being communicated with each other through a fluid flowing passage; and fluid control means disposed in the fluid flowing passage of the rotary housing and having a fluid control valve and a control section for controlling operation of the fluid control valve.

Description

TORQUE CONVERTER FOR AUTOMATIC TRANSMISSION

Technical Field

The present invention relates to a torque converter, and more particularly, the present invention relates to a torque converter which can be actuated using fluid pressure to prevent fuel from being wasted due to fuel loss as generated in a conventional torque converter thereby improving fuel air ratio, can also prevent fuel from being wasted due to fuel loss resulting from idle rotation for creating vortex flow upon initial actuation of the conventional torque converter, and can accomplish torque conversion corresponding to engine power to render a rapid gear shift while an automobile runs.

Background Art Generally, a torque converter which is mounted between an output shaft of an engine and an input shaft of an automatic transmission, functions to control power transfer from the engine to the automatic transmission by using rotating force and vortex flow of fluid and to change output torque when transferring engine power to the automatic transmission.

Here, a conventional torque converter used in an automatic transmission will be concretely described. Referring to FIG. 31, there is shown a partially broken- away perspective view illustrating a torque converter of the related art. A torque converter largely comprises a pump impeller 5011 which receives rotating force of an engine output shaft, a stator 5013 which reverses fluid flow to serve by itself as a load, a turbine runner 5012 which is connected to an input shaft of an automatic transmission, and a converter cover 5014 which is welded to the pump impeller 5011.

In more detail, the pump impeller 5011 and the converter cover 5014 function to convert mechanical rotation into fluid flow and transfer converted fluid flow to the turbine runner 5012, while being rotated together with the engine output shaft.

The turbine runner 5012 is mounted to the converter cover 5014 such that it is opposite to the pump impeller 5011. The turbine runner 5012 is rotated in the same direction as the pump impeller 5011 by fluid flow generated in the pump impeller 5011 and has at its center portion a rotating shaft which is connected to the input shaft of the automatic transmission. The stator 5013 is positioned between the pump impeller 5011 and the turbine runner 5012. The stator 5013 functions to cause fluid flow generated in the pump impeller 5011 to be recirculated to the pump impeller 5011 after hitting and rotating blades of the turbine runner 5012, thereby serving as a load when the pump impeller 5011 is rotated.

However, the torque converter of the related art, constructed as mentioned above, suffers from defects in that since a load (vortex flow loss) is generated in the stator mounted in the torque converter when the torque converter is actuated, torque which is larger than that desired to be obtained at the transmission, must be inputted from an engine, whereby fuel amount supplied to the engine is increased and fuel air ratio is deteriorated.

Further, since fluid flow (rotation and vortex flow) is generated in the torque converter at an initial actuation stage of the torque converter, fuel is wasted due to initial idle rotation of the engine output shaft.

Moreover, due to the fact that the torque converter uses fluid flow, since it is difficult to change torque in a precisely controlled manner while the torque converter is actuated, a gear shift which reveals ideal properties, cannot be obtained in the automatic transmission.

In addition, since the torque converter of the related art is rotated at high speed, the pump impeller, stator, turbine runner and converter cover which constitute the torque converter, can be easily broken.

Disclosure of the Invention

Accordingly, the present invention has been made in an effort to solve the problems occurring in the related art, and a primary object of the present invention is to provide a torque converter for an automatic transmission which can be actuated using fluid pressure while being mounted between an output shaft of an engine and an input shaft of an automatic transmission, thereby to prevent fuel from being wasted due to vortex flow loss as generated in a conventional torque converter.

Another object of the present invention is to provide a torque converter for an automatic transmission in which a rotary housing is rotated using pressure of fluid filled in a gear room upon initial actuation of the torque converter (in the case that power of an engine is transferred to the automatic transmission) , thereby to prevent fuel from being wasted due to idle rotation of a power input shaft. Another object of the present invention is to provide a torque converter for an automatic transmission which uses fluid pressure when transferring engine power, to accomplish torque conversion corresponding to engine output, while it is actuated, thereby to render a gear shift which reveals ideal properties, while an automobile runs .

Another object of the present invention is to provide a torque converter for an automatic transmission which uses fluid pressure when transferring engine power, to minimize mechanical abrasion due to fluid collision as generated in a conventional torque converter, thereby to prevent the torque converter from being broken and capability thereof from being deteriorated.

Another object of the present invention is to provide a torque converter for an automatic transmission which smooths fluid flow by its actuation when opening or closing fluid, to prevent excessive pressure from being applied to a gear and a housing.

Another object of the present invention is to provide a torque converter for an automatic transmission in which a separate pressure regulating section for offsetting pressure variation while being actuated is provided in the course of a fluid flowing passage, thereby to minimize vibration and oscillation during rotation of a gear.

Still another object of the present invention is to provide a torque converter for an automatic transmission which is interlocked with an accelerator, thereby to enable a gear shift to be implemented when the accelerator is not operated.

Yet still another object of the present invention is to provide a torque converter for an automatic transmission in which fluid pressure in a gear room is adjusted within respective gears, thereby to prevent the torque converter from being broken or mis-actuated due to a load.

In order to achieve the above object, according to the present invention, there is provided a torque converter for an automatic transmission, mounted between an output shaft of an engine and an input shaft of the automatic transmission for transferring engine power to the automatic transmission, the torque converter comprising: a rotary housing connected to the input shaft of the automatic transmission and formed with a gear room having a main gear room in which a main gear connected to the output shaft of the engine is mounted and at least one auxiliary gear room which is arranged at a side of the main gear room and in which at least one auxiliary gear meshing with the main gear is mounted, the rotary housing having first and second space portions arranged at upper and lower parts of the gear room, respectively, between the main gear room and the auxiliary gear room, the first and second space portions being communicated with each other through a fluid flowing passage; and fluid control means disposed in the fluid flowing passage of the rotary housing and having a fluid control valve and a control section for controlling operation of the fluid control valve .

Brief Description of the Drawings

The above objects, and other features and advantages of the present invention will become more apparent after a reading of the following detailed description when taken in conjunction with the drawings, in which: FIG. 1 is a schematic view illustrating a mounting state of a torque converter according to the present invention;

FIG. 2 is a front cross-sectional view illustrating the torque converter according to the present invention; FIG. 3 is a side cross-sectional view taken along the line III-III of FIG. 2;

FIG. 4 is a side cross-sectional view illustrating a torque converter in accordance with a first embodiment of the present invention;

FIG. 5 is a front cross-sectional view taken along the line V-V of FIG. 4;

FIG. 6 is a schematic view illustrating a mounting state of a torque converter in accordance with a second embodiment of the present invention;

FIG. 7 is a front cross-sectional view illustrating the torque converter in accordance with the second embodiment of the present invention;

FIG. 8 is a side cross-sectional view taken along the line VIII-VIII of FIG. 7;

FIG. 9 is a side cross-sectional view taken along the line IX-IX of FIG. 7;

FIG. 10 is a perspective view illustrating fluid control means in accordance with the second embodiment of the present invention;

FIG. 11 is a front cross-sectional view illustrating a state wherein a spool in accordance with the second embodiment of the present invention is fully moved backward;

FIG. 12 is a front cross-sectional view illustrating a state wherein the spool in accordance with the second embodiment of the present invention is fully moved forward;

FIG. 13 is a front cross-sectional view illustrating a state wherein the spool in accordance with the second embodiment of the present invention is in a middle position;

FIG. 14 is a side cross-sectional view illustrating a rotary housing in accordance with another embodiment of the present invention;

FIG. 15 is a schematic view illustrating a mounting state of a torque converter in accordance with a third embodiment of the present invention; FIG. 16 is a side cross-sectional view taken along the line XVI-XVI of FIG. 15;

FIG. 17 is a cross-sectional view taken along the line XVII-XVII of FIG. 16;

FIG. 18 is a cross-sectional view taken along the line XVIII-XVIII of FIG. 16;

FIG. 19 is of views illustrating a fluid control section in accordance with the third embodiment of the present invention, wherein FIG. 19A is a partially broken- away perspective view and FIG. 19B is a perspective view illustrating connection states of fluid flowing ways;

FIG. 20 is a perspective view illustrating a rotating cam constituting the fluid control section in accordance with the third embodiment of the present invention;

FIG. 21 is an enlarged cross-sectional view illustrating a pressure regulating section in accordance with the third embodiment of the present invention;

FIG. 22 is a structural diagram illustrating an interlocking relationship between the torque converter in accordance with the third embodiment of the present invention and an accelerator;

FIG. 23 is of side cross-sectional views illustrating gears in accordance with another embodiment of the present invention, wherein FIG. 23A depicts a main gear and FIG. 23B depicts an auxiliary gear;

FIG. 24 is a schematic view illustrating a valve control section in accordance with another embodiment of the present invention;

FIG. 25 is a side elevation view illustrating a pressure regulating section in accordance with another embodiment of the present invention;

FIG. 26 is a schematic view illustrating a pressure regulating section in accordance with still another embodiment of the present invention;

FIG. 27 is a front cross-sectional view illustrating a torque converter in accordance with a fourth embodiment of the present invention; FIG. 28 is a side cross-sectional view taken along the line XXVIII-XXVIII of FIG. 27;

FIG. 29 is a front cross-sectional view illustrating a torque converter in accordance with a fifth embodiment of the present invention; FIG. 30 is a side cross-sectional view taken along the line XXX-XXX of FIG. 29; and

FIG. 31 is a partially broken-away perspective view illustrating a torque converter of the related art.

Best Mode for Carrying Out the Invention Reference will now be made in greater detail to a preferred embodiment of the invention, an example of which is illustrated in the accompanying drawings. Wherever possible, the same reference numerals will be used throughout the drawings and the description to refer to the same or like parts.

Referring to FIG. 1, there is shown a schematic view illustrating a mounting state of a torque converter according to the present invention. A torque converter 1 of the present invention is mounted between an output shaft 21 of an engine 2 and an input shaft 31 of an automatic transmission 3 and functions to control power transfer from the engine 2 to the automatic transmission 3.

FIG. 2 is a front cross-sectional view illustrating the torque converter according to the present invention; and FIG. 3 is a side cross-sectional view taken along the line III-III of FIG. 2. A construction of the torque converter 1 will be described herembelow.

The torque converter 1 includes a rotary housing 1001 and fluid control means 1002. The rotary housing 1001 is connected to the input shaft 31 of the automatic transmission 3 such that it receives power from the engine 2 and transfers the power to the automatic transmission 3 after the changing torque of received power. The rotary housing 1001 is formed with a gear room 1011. The gear room 1011 comprises a ma gear room 1111 in which a ma gear 1012 connected to the output shaft 21 of the engine 2 is mounted and an auxiliary gear room 1112 which is arranged at a side of the mam gear room 1111 and m which an auxiliary gear 1013 is mounted. The rotary housing 1001 has first and second space portions 1113 and 1114 which are arranged at upper and lower parts of the gear room 1011, respectively, between the ma gear room 1111 and the auxiliary gear room 1112. The first and second space portions 1113 and 1114 are communicated w th each other through a fluid flowing passage 1014. The fluid control means 1002 is disposed m the fluid flowing passage 1014 of the rotary housing 1001 and has a fluid control valve 1021 and a control section 1022 for controlling operation of the fluid control valve 1021.

The input shaft 31 of the automatic transmission 3 is aligned with the output shaft 21 of the engine 2 on the same axis, in the rearward of the main gear room 1111 which is formed in the rotary housing 1001, thereby preventing the input shaft 31 from being eccentrically rotated when power is transferred between the output shaft 21 of the engine 2 and the input shaft 31 of the automatic transmission 3.

The fluid control means 1002 functions to interrupt or adjust fluid flow through the fluid flowing passage 1014 which is defined in the rotary housing 1001. The fluid control valve 1021 is disposed in the middle of the fluid flowing passage 1014, and is controlled through the control section 1022 which calculates torque variation corresponding to engine output during actuation of the automatic transmission 3.

Lost fluid replenishing means 1015 for replenishing fluid which is lost due to abrasion or heat generated upon rotation of the main gear 1012 and the auxiliary gear 1013, is disposed in the course of the fluid flowing passage 1014. The lost fluid replenishing means 1015 includes a fluid tank 1151 which has an air hole 1151a, and a fluid inlet pipe 1152 which is connected to the fluid flowing passage 1014 and has a check valve 1152a installed therein.

Hereinafter, operations of the torque converter, constructed as mentioned above, will be described in detail with respect to the case that the engine 2 is idly rotated, the case that engine power is perfectly transferred to the automatic transmission 3, and the case that power transferred to the automatic transmission 3 is varied.

First, in the case that the engine 2 is idly rotated, a condition in which the output shaft 21 of the engine 2 is rotated and the input shaft 31 of the automatic transmission 3 is stopped must be satisfied. Accordingly, if the control section 1022 constituting the fluid control means 1002 fully opens the fluid control valve 1021 connected to it after recognizing a neutral position of a transmission gear shift lever, because fluid flows through the fluid flowing passage 1014 which communicates the first and second space portions 1113 and 1114 of the gear room 1011 with each other, the auxiliary gear 1013 is idly rotated in view of the fact that fluid flows between teeth of the auxiliary gear 1013 when the main gear 1012 connected to the output shaft 21 of the engine 2 is rotated.

Therefore, the output shaft 21 of the engine 2 which is connected to the main gear 1012, is rotated, and the input shaft 31 of the automatic transmission 3 is maintained in a stopped state. In other words, input torque of the automatic transmission 3 equals zero.

On the contrary, if engine power is perfectly transferred to the automatic transmission 3, a condition in which torque of output power of the engine 2 equals to torque of input power of the automatic transmission 3 must be satisfied. Accordingly, if the control section 1022 constituting the fluid control means 1002 fully closes the fluid control valve 1021 connected to it after recognizing a perfect power transfer situation, flow of fluid which is filled in the gear room 1011 of the rotary housing 1001 is stopped. In other words, a state wherein the main gear 1012 and the auxiliary gear 1013 are integrally and rigidly connected with each other by fluid is maintained. At this time, if the main gear 1012 which is connected to the output shaft 21 of the engine 2 is rotated in a forward direction, because fluid which is filled in the gear room 1011 rigidly connects the main gear 1012 and the auxiliary gear 1013 with each other, the auxiliary gear 1013 revolves about the main gear 1012, and the rotary housing 1001 is rotated at the same rpm as the main gear 1012. According to this, on the assumption that fluid loss is neglected, it is possible to perfectly transfer power of the output shaft 21 of the engine 2 to the input shaft 31 of the automatic transmission 3.

On the other hand, if engine power is transferred to the automatic transmission 3 while being varied, a condition in which torque of output power of the engine 2 is larger than torque of input power of the automatic transmission 3 must be satisfied. Accordingly, if the control section 1022 constituting the fluid control means 1002 opens to half the fluid control valve 1021 connected to it after recognizing a variable power transfer situation, fluid flow which passes through the fluid flowing passage 1014 is reduced to half. In other words, one portion of fluid which is filled in the gear room 1011 is maintained in the gear room 1011 and the other portion of the fluid which is filled in the gear room 1011 is circulated along the fluid flowing passage 1014.

At this time, if the main gear 1012 which is connected to the output shaft 21 of the engine 2 is rotated in a forward direction, because fluid which is filled in the gear room 1011 flows at velocity which corresponds to that at an intermediate state between a fully opened state and a fully closed state, the rotary housing 1001 is rotated at half the rpm of the main gear 1012 in the forward direction when compared to the main gear 1012, in view of the fact that the auxiliary gear 1013 is rotated half a turn while the main gear 1012 is rotated a full turn. In other words, due to the fact that when the main gear 1012 is rotated a full turn in the forward direction, fluid pressure which biases teeth of the auxiliary gear 1013 is reduced to half, the rotary housing 1001 is rotated half a turn in the forward direction .

Therefore, in the case that torque of power generated by the output shaft 21 of the engine 2 is transferred to the input shaft 31 of the automatic transmission 3 after being finely adjusted, by adjusting the opening degree of the fluid flowing passage 1014 through the control section 1022 constituting the fluid control means 1002, torque of the output shaft 21 of the engine 2 can be transferred to the input shaft 31 of the automatic transmission 3 in a state wherein torque thereof is varied.

FIG. 4 is a side cross-sectional view illustrating a torque converter in accordance with a first embodiment of the present invention; and FIG. 5 is a front cross- sectional view taken along the line V-V of FIG. 4. A construction of the torque converter according to the present embodiment will be described hereinbelow.

In a torque converter of this embodiment, a rotary housing 1003 is formed with a gear room 1031. The gear room 1031 has a main gear room 1311 and first and second auxiliary gear rooms 1312 and 1313 which are located at both sides of the main gear room 1311, respectively. A main gear 1032 which is connected to the output shaft of the engine is mounted in the main gear room 1311, and first and second auxiliary gears 1033 and 1034 are mounted in the first and second auxiliary gear rooms 1312 and 1313 at both sides of the main gear 1032, respectively. The rotary housing 1003 has first and second space portions 1321 and 1322 which are arranged at upper and lower parts of the gear room 1031 between the main gear 1032 and the respective first and second auxiliary gears 1033 and 1034. Fluid flowing passages 1035 are diagonally defined between the first and second space portions 1321 and 1322.

Accordingly, fluid which is filled in the gear room 1031 is circulated through the first and second space portions 1321 and 1322 and the fluid flowing passages 1035 which communicate the first and second space portions 1321 and 1322 with each other.

A spool mounting hole 1351 is defined in the rotary housing 1003 such that it extends through the fluid flowing passages 1035. Fluid control means 1004 is mounted in the spool mounting hole 1351. The fluid control means 1004 comprises a spool 1041 which possesses at a front part thereof a fluid flowing groove 1411 for controlling fluid flow while being moved forward and backward, and a control section 1042 for controlling forward and backward movement of the spool 1041. Accordingly, fluid which circulates along the fluid flowing passages 1035 is opened or closed, or its fluid flow is adjusted, by the forward and backward movement of the spool 1041 which constitutes the fluid control means 1004. Therefore, in the torque converter of this embodiment, constructed as mentioned above, by controlling flow of fluid which is filled in the gear room 1031, it is possible to simultaneously perform a function to transfer power of the output shaft of the engine to the input shaft of the automatic transmission or to cease the power transfer and a function to transfer torque of output power of the engine to the automatic transmission after changing it.

FIG. 6 is a schematic view illustrating a mounting state of a torque converter in accordance with a second embodiment of the present invention, FIG. 7 is a front cross-sectional view illustrating the torque converter in accordance with the second embodiment of the present invention, FIG. 8 is a side cross-sectional view taken along the line VIII-VIII of FIG. 7, and FIG. 9 is a side cross-sectional view taken along the line IX-IX of FIG. 7. A construction of the torque converter according to the present embodiment will be described hereinbelow.

A torque converter of the present embodiment includes a rotary housing 2001, fluid control means 2002, transmission connection means 2003 and spool control means 2004. The torque converter is mounted between an output shaft 21 of an engine 2 and an input shaft 31 of an automatic transmission 3 for transferring engine power to the automatic transmission 3. The rotary housing 2001 is formed with a gear room 2011 in which a main gear 2012 and first and second auxiliary gears 2013 and 2014 (see FIG. 8) are mounted for receiving power of the engine 2 and transferring the received power to the automatic transmission 3 after changing torque thereof. The fluid control means 2002 is mounted in the rotary housing 2001 for controlling fluid flow, and includes a spool 2021, a rotational shaft 2022 and a rotary plate 2023. The transmission connection means 2003 is positioned in the rearward of the spool 2021 which constitutes the fluid control means 2002. The transmission connection means 2003 has a front end which is integrally connected to the rotary housing 2001 and a rear end which is connected to the input shaft 31 of the automatic transmission 3. The transmission connection means 2003 includes a pair of connection shafts 2031 which are formed with a fluid inlet passage 2311 and a fluid outlet passage 2312 for supplying and discharging fluid into and from the rotary housing 2001, respectively. The spool control means 2004 has a forward and backward moving section 2042 for controlling stroke movement of the rotary plate 2023 which constitutes the fluid control means 2002, and a control section 2041 for controlling operation of the forward and backward moving section 2042.

Specifically, the rotary housing 2001 is formed with the gear room 2011. The gear room 2011 has a main gear room 2111 which has a fluid chamber 2111a formed inward and rearward thereof and in which the main gear 2012 connected to the output shaft 21 (see FIG. 6) of the engine 2 (see FIG. 6) is mounted, and first and second auxiliary gear rooms 2112 and 2113 which are arranged at both sides of the main gear room 2111, respectively, and in which the first and second auxiliary gears 2013 and 2014 are mounted at both sides of the main gear 2012, respectively.

First through fourth space portions 2114a, 2114b, 2114c and 2114d through which fluid is sucked and discharged, are defined at upper and lower parts of the main gear room 2111 and the first and second gear rooms 2112 and 2113. The first and second space portions 2114a and 2114b are formed at upper and lower parts between the main gear room 2111 and the first auxiliary gear room 2112, and the third and fourth space portions 2114c and 2114d are formed at upper and lower parts between the main gear room 2111 and the second auxiliary gear room 2113. As described above, the fluid chamber 2111a is formed rearward of the main gear room 2111. A lost fluid replenishing means 2015 is provided in the fluid chamber 2111a in a diagonal direction which extends at the angle of 45°. The lost fluid replenishing means 2015 has, as best shown in FIG. 9, a safety valve 2151 which comprises a through hole 2151a, a push bolt 2151b, a spring 2151c and a valve packing 2151d. The lost fluid replenishing means 2015 further has a replenishing fluid supply hole 2152 which is formed in the forward of the through hole 2151a and is communicated with the first through fourth space portions 2114a, 2114b, 2114c and 2114d.

A spool mounting hole 2121 into which the spool 2021 constituting the fluid control means 2002 is inserted to be moved forward and backward, is formed at a center part of the main gear 2012 which is mounted in the main gear room 2111. A plurality of fluid flowing slots 2122 through which outside fluid is supplied into the gear room 2011 and inside fluid is discharged forwardly of the spool 2021, are formed around the spool mounting hole 2121. A plurality of cooling fins 2016 for lowering temperature inside the gear room 2011 during actuation of the torque converter are mounted onto a circumferential outer surface of the rotary housing 2001.

The fluid control means 2002 functions, as best shown in FIG. 10, to control fluid flowing through the plurality of fluid flowing slots 2122 from the center part of the main gear 2012, and has the spool 2021, the rotational shaft 2022 which is connected to the spool 2021 and the rotary plate 2023 which is secured to a rear end of the rotational shaft 2022.

In addition, a circumferential outer surface of the spool 2021 is formed with a plurality of prominences 2211 for opening and closing the plurality of fluid flowing slots 2122, respectively, which are formed in the main gear 2012, and a plurality of horizontal fluid flowing grooves 2212 through which fluid flowing inward through the fluid inlet passage 2311 formed in the transmission connection means 2003 is supplied into the gear room 2011, with the plurality of prominences 2211 and the plurality of horizontal fluid flowing grooves 2212 alternately formed. Further, the rotary plate 2023 which is mounted to the rear end of the rotational shaft 2022 is connected to a front part of the forward and backward moving section 2042 which constitutes the spool control means 2004, to be integrally moved therewith forward and backward. A pair of inserting portions 2231 into which the pair of connection shafts 2031 constituting the transmission connection means 2003 can be inserted, are formed over and under a center part of the rotating plate 2023, respectively. The transmission connection means 2003 is, as best shown in FIG. 7, positioned in the rearward of the spool 2021 constituting the fluid control means 2002. The front end of the transmission connection means 2003 has the pair of connection shafts 2031 which are integrally connected to the rotary housing 2001. The upper connection shaft 2031 is formed with the fluid inlet passage 2311 for supplying fluid into the plurality of fluid flowing grooves 2212 of the spool 2021 which is centrally inserted into the main gear 2012. The lower connection shaft 2031 is formed with the fluid outlet passage 2312 for discharging fluid which is filled in the fluid chamber 2111a of the main gear room 2111.

Moreover, a spool backward movement space portion 2313 is defined forwardly and inwardly of the pair of connection shafts 2031 to allow the spool 2021 to be moved backward. Further, the spool control means 2004 is, as shown in FIG. 7, mounted to a proper position on the automatic transmission 3 to limit stroke movement of the rotary plate 2023 constituting the fluid control means 2002. The forward and backward moving section 2042 which comprises a holder 2422 for holding the rotary plate 2023 and a rod for connecting the holder 2422 and the control section 2041 with each other, is mounted forwardly of the control section 2041.

Hereinafter, operations of the torque converter according to the present embodiment of the present invention, constructed as mentioned above, will be described in detail with respect to the case that the engine 2 is idly rotated, the case that engine power is perfectly transferred to the automatic transmission 3, and the case that power transferred to the automatic transmission 3 is varied.

First, in the case that the engine 2 is idly rotated, a condition in which the output shaft 21 of the engine 2 is rotated and the input shaft 31 of the automatic transmission 3 is stopped, must be satisfied (see FIGs . 3 and 6) . Accordingly, if the control section 2041 which is mounted to the automatic transmission 3 moves backward the forward and backward moving section 2042 which is positioned in the forward of the control section 2041, after recognizing a neutral position of a transmission gear shift lever, the rotary plate 2023 constituting the fluid control means 2002 is moved backward by the forward and backward moving section 2042, and at the same time, as the spool 2021 which is connected to the rotary plate 2023 is moved backward, the plurality of fluid flowing slots 2122 which pass through the inner part of the main gear 2012 are wholly opened.

At this time, when considering an interlocked relationship between the main gear 2012 and the rotary housing 2001 in the case that the engine 2 is idly rotated, if the spool 2021 mounted to the center part of the main gear 2012 as described above is moved backward, the plurality of fluid flowing slots 2122 which are radially formed in the main gear 2012, are maintained in a fully opened state. According to this, fluid inside the gear room 2011 flows forwardly of the spool 2021 to be discharged through the fluid outlet passage 2312, and fluid flowed into the rotary housing 2001 through the fluid inlet passage 2311 flows into the gear room 2011 through the plurality of fluid flowing slots 2122, whereby pressure in the first through fourth space portions 2114a, 2114b, 2114c and 2114d which are formed at upper and lower parts of the gear room 2011 and at both sides of the main gear 2012 is balanced. Accordingly, when the main gear 2012 is rotated, the first and second auxiliary gears 2012 and 2013 are idly rotated at their original positions, whereby the rotary housing 2001 is maintained in a stopped state .

Therefore, the output shaft 21 of the engine 2 which is connected to the main gear 2012, is rotated, and the input shaft 31 of the automatic transmission 3 is maintained in a stopped state. In other words, input torque of the automatic transmission 3 equals zero. On the contrary, if engine power is perfectly transferred to the automatic transmission 3, a condition in which torque of output power of the engine 2 equals to torque of input power of the automatic transmission 3, must be satisfied (see FIGs . 7 and 12). Accordingly, if the control section 2041 which is mounted to the automatic transmission 3 moves forward the forward and backward moving section 2042 which is positioned in the forward of the control section 2041, after recognizing a perfect power transfer situation, the rotary plate 2023 constituting the fluid control means 2002 is moved forward by the forward and backward moving section 2042, and at the same time, as the spool 2021 which is connected to the rotary plate 2023 is integrally moved forward, the plurality of fluid flowing slots 2122 which pass through the inner part of the main gear 2012 are wholly closed.

At this time, if the main gear 2012 which is connected to the output shaft 21 of the engine 2 is rotated in a forward direction in a state wherein fluid is filled in the closed gear room 2011, pressure is raised in the first and fourth space portions 2114a and 2114d which are formed at upper and lower parts of the gear room 2011 and at both sides of the main gear room 2111, and pressure is lowered in the second and third space portions 2114b and 2114c to be maintained in a fluid stand-by state. Due to the fact that the first and second auxiliary gears 2013 and 2014 revolve about the main gear 2012, the rotary housing 2001 is rotated at the same rpm as the main gear 2012 in the forward direction. In other words, the main gear 2012 performs a function of a sun gear, and the first and second auxiliary gears 2013 and 2014 perform functions of planetary gears. Accordingly, when the main gear 2012 is rotated a full turn in the forward direction, the rotary housing 2001 is also rotated a full turn in the forward direction. Consequently, on the assumption that fluid loss is neglected, it is possible to perfectly transfer power of the output shaft 21 of the engine 2 to the input shaft 31 of the automatic transmission 3.

On the other hand, as described above, as the torque converter of the present invention is actuated, fluid flow is lost in the gear room 2011 due to abrasion or heat which is generated when the gears are rotated. Accordingly, by replenishing fluid through the lost fluid replenishing means 2015 mounted to the fluid chamber 2111a of the main gear room 2111, performance deterioration and breakage of the rotary housing due to shut-off of fluid supply into the gear room 2011 can be prevented. To be more detailed, as shown in FIG. 9, if fluid flow is lost in the gear room 2011, as internal pressure of the gear room 2011 is lowered and pressure differential is created between the gear room 2011 and the fluid chamber 2111a, the valve packing 2151d constituting the safety valve 2151 is moved backward, and fluid which is filled in the fluid chamber 2111a is supplied into the gear room 2011 after passing through the through hole 2151a and the replenishing fluid supply hole 2152. Thereafter, pressure is balanced between the gear room 2011 and the fluid chamber 2111a, and according to this, the valve packing 2151d constituting the safety valve 2151 is caused to close again the through hole 2151a by elastic force of the spring 2151c.

Further, if engine power is transferred to the automatic transmission 3 while being varied in its torque, a condition in which torque of output power of the engine 2 is larger than torque of input power of the automatic transmission 3, must be satisfied (see FIGs. 7 and 13). Accordingly, if the control section 2041 which is mounted to the automatic transmission 3 moves to a middle position (hereinafter, descriptions will be concentrated to a state wherein the spool is moved to a true middle position) the forward and backward moving section 2042 which is positioned in the forward of the control section 2041, after recognizing a variable power transfer situation, as the spool 2021 is moved to the middle of the spool mounting hole 2121, the plurality of fluid flowing slots 2122 which pass through the main gear 2012 are opened to half.

If the spool 2021 which is mounted in the center part of the main gear 2012 is positioned in the middle of the spool mounting hole 2121 as described above, since the plurality of fluid flowing slots 2122 which are radially formed in the main gear 2012 are opened to half, one portion of fluid in the gear room 2011 is maintained in the gear room 2011, and the other portion of fluid in the gear room 2011 is discharged forwardly of the spool 2021 after passing through the plurality of fluid flowing slots 2122. At the same time, outside fluid flows into the gear room 2011 through the plurality of fluid flowing slots 2122 of the main gear 2012. At this time, if the main gear 2012 which is connected to the output shaft 21 of the engine 2 is rotated in a forward direction, pressure in the first and fourth space portions 2114a and 2114d which are formed at upper and lower parts of the gear room 2011 and at both sides of the main gear room 2111 is raised to half when compared to a fully closed state by the spool 2021, and on the contrary, pressure in the second and third space portions 2114b and 2114c is lowered to half when compared to the fully closed state by the spool 2021, whereby the first and second auxiliary gears 2013 and 2014 rotate a full turn and revolve a full turn about the main gear 2012. Due to the fact that the fluid pressure is lowered as described above, the rotary housing 2001 is rotated at half the rpm in the forward direction when compared to the rpm of the main gear 2012.

In other words, since the main gear 2012 performs a function of a sun gear and the first and second auxiliary gears perform functions of planetary gears, if the main gear 2012 is rotated a full turn in the forward direction, while first and second auxiliary gears 2013 and 2014 revolve a full turn in a reverse direction, the rotary housing 2001 is rotated only half a turn in the forward direction due to the fact that fluid pressure which biases teeth of the first and second auxiliary gears 2013 and 2014, is lowered to half.

Therefore, in the case that torque of power generated by the output shaft 21 of the engine 2 is transferred to the input shaft 31 of the automatic transmission 3 after being finely adjusted, by adjusting the moving distance of the spool 2021 constituting the fluid control means 2002 through the control section 2041 mounted to the automatic transmission 3, torque of the output shaft 21 of the engine 2 can be transferred to the input shaft 31 of the automatic transmission 3 in a state wherein it is varied. FIG. 14 is a side cross-sectional view illustrating a rotary housing in accordance with another embodiment of the present invention. A rotary housing 2007 is formed with a vane room 2071 which has an elliptical configuration and in which a vane 2072 is mounted. A spool mounting hole 2721 is formed in a center part of the vane 2072 such that the spool 2021 constituting the fluid control means 2002 is inserted therein such that it can be moved forward and backward. The plurality of fluid flowing slots 2122 are radially formed around the spool mounting hole 2721 such that outside fluid can be supplied into the vane room 2071 therethrough or fluid inside the vane room 2071 can be discharged therethrough forwardly of the spool 2021. Especially, due to the fact that a plurality of partition plates 2721 are fastened to the circumferential outer surface of the vane 2072 to scrape an elliptical inner surface of the vane room 2071 while being oscillated by supplied fluid flow and discharged fluid flow, in a state wherein the vane room 2071 is filled with fluid, as the rotary housing 2007 is rotated, the vane 2072 is rotated at the same time.

Accordingly, as described above, operations of the rotary housing 2007 constructed as mentioned above can be performed to transfer power of the engine 2 to the automatic transmission 3 by forward and backward movement of the spool 2021 which is mounted at the center part of the vane 2072.

FIG. 15 is a schematic view illustrating a mounting state of a torque converter in accordance with a third embodiment of the present invention. A torque converter according to this embodiment of the present invention is mounted between an output shaft 3011 of an engine 3001 and an input shaft 3021 of an automatic transmission 3002 for transferring engine power to the automatic transmission

3002. This will be concretely described below. FIG. 16 is a side cross-sectional view taken along the line XVI-XVI of FIG. 15; and FIG. 17 is a cross- sectional view taken along the line XVII-XVII of FIG. 16. A construction of the torque converter according to the present embodiment will be described hereinbelow. The torque converter of this embodiment includes a rotary housing 3003, a main gear 3004 and first and second auxiliary gears 3041 and 3042. The rotary housing 3003 is formed at a central and inward part thereof with a main gear room 3031 and at both sides of the main gear room 3031 with first and second auxiliary gear rooms 3032 and 3033. The main gear 3004 is mounted in the main gear room 3031 and connected to the output shaft 3011 of the engine 3001. The first and second auxiliary gears 3041 and 3042 are mounted in the first and second auxiliary gear rooms 3032 and 3033, respectively, to rotate and revolve about the main gear 3004, thereby to rotate the rotary housing

3003. First through fourth fluid passing holes 3043, 3044, 3045 and 3046 are formed at upper and lower parts of boundary regions between the main gear room 3031 and the respective first and second auxiliary gear rooms 3032 and 3033 of the rotary housing 3003. A pair of fluid flowing ways 3005 are defined between the first and second fluid passing holes 3043 and 3044 and between the third and fourth fluid passing holes 3045 and 3046, respectively. A valve control section 3006 has a movable magnetic ring 3061 which is fitted around a circumferential outer surface of the rotary housing 3003 to be moved horizontally and is formed at a circumferential inner surface thereof with a horizontally extending rack 3611. The valve control section 3006 further has a coil ring 3062 which is mounted around a circumferential outer surface of the movable magnetic ring 3061 and connected to a power source for controlling operation of the movable magnetic ring 3061. A fluid control section 3007 and a pressure regulating section 3008 are disposed in the course of each fluid flowing way 3005. The fluid control section 3007 is opened and closed by the movable magnetic ring 3061 and is equipped with a cam valve 3071. The pressure regulating section 3008 functions to offset rise in fluid pressure.

Especially, as shown in FIG. 17, at least one compression coil spring 3013 is mounted between a side surface of the movable magnetic ring 3061 and a side surface of a ring gear 3012 which projects from the engine 3001, for returning the movable magnetic ring 3061 to its original position. A press piece 3341 which is biased by a spring, is disposed in a rear part of each auxiliary gear room 3032 or 3033, a fluid remaining room 3034 is defined at a side of each auxiliary gear room 3032 or 3033, and a fluid passage 3342 is connected to the fluid remaining room 3034 to move the press piece 3341 forward and backward. If the torque converter is stopped, the press piece 3341 is moved backward to prevent torque from being generated in the rotary housing 3003, and if the torque converter is actuated, the press piece 3341 is moved forward to be brought into contact with the auxiliary gear 3032 or 3033 thereby to ensure ideal operations thereof.

The torque converter of this embodiment will be described in more detail below.

As shown in FIGs. 19 and 20, the fluid control section 3007 comprises a pinion 3072 and the cam valve 3071. The pinion 3072 is positioned at a side of the fluid control section 3007 and is rotated while being meshed with the horizontally extending rack 3611 which is provided in the movable magnetic ring 3061. The cam valve 3071 is mounted to a center shaft of the pinion 3072 and is positioned inside a housing 3074. The cam valve 3071 includes a pair of rotating cams 3731 which are arranged such that they are opposite to each other. Center portions of the pair of rotating cams 3731 are connected with each other by a bracket 3732. A fluid passing space 3733 is defined between the pair of rotating cams 3731. Each rotating cam 3731 is formed with a pair of fluid passing grooves 3734 which are opposed to each other. A cam inclined surface 3735 is formed at a side wall of each fluid passing groove 3734 such that it is inclined inward. The cam inclined surface 3735 functions to lower fluid sucking velocity and fluid discharging velocity. The housing 3074 is formed with a pair of first fluid passing apertures 3741 which are communicated with the fluid passing space 3733 and are opposite to each other. At positions which correspond to mounting positions of the pair of rotating cams 3731, the housing 3074 is formed with two pairs of second fluid passing apertures 3742 so that two pairs are opposed to each other and two apertures of each pair are opposite to each other. The fluid flowing way 3005 is connected to the pair of first fluid passing apertures 3741. The fluid flowing way 3005 is also simultaneously connected to the two pairs of second fluid passing apertures 3742. The pressure regulating section 3008 comprises, as best shown in FIG. 21, a pressure regulating chamber 3081 which is formed adjacent the fluid flowing way 3005 such that it is communicated with the fluid flowing way 3005, and an air bladder member 3082 which is received in the pressure regulating chamber 3081.

Hereinafter, operations of the torque converter according to the present embodiment, constructed as mentioned above, will be described in detail. First, in the case that the engine 3001 is idly rotated, a condition in which the output shaft 3011 of the engine 3001 is rotated and the input shaft 3021 of the automatic transmission 3002 is stopped, must be satisfied. Accordingly, if a torque converter control section does not apply current to the coil ring 3062 after recognizing a neutral position of a transmission gear shift lever, the movable magnetic ring 3061 which is disposed on an inner surface of the coil ring 3062 is maintained in its original position, and the cam valve 3071 which is operatively connected to the movable magnetic ring 3061 is fully opened. Therefore, as fluid passes through the fluid flowing way 3005 of the gear room, the first and second auxiliary gears 3041 and 3042 are idly rotated in view of the fact that fluid flows between teeth of the first and second auxiliary gears 3041 and 3042 when the main gear 3004 connected to the output shaft 3011 of the engine 3001 is rotated.

Therefore, the output shaft 3011 of the engine 3001 which is connected to the main gear 3004, is rotated, and the input shaft 3021 of the automatic transmission 3002 is maintained in a stopped state. In other words, input torque of the automatic transmission 3002 equals zero. When considering the case that engine power is transferred to the automatic transmission 3002, if the torque converter control section applies current to the coil ring 3062 after recognizing a perfect power transfer situation, the movable magnetic ring 3061 which is disposed on an inner surface of the coil ring 3062 is moved to a side, and as the pair of rotating cams 3731 of the cam valve 3071 which is operatively connected to the movable magnetic ring 3061 are rotated, the pair of first fluid passing apertures 3741 which are formed in the housing 3074 are fully or partly closed. Accordingly, torque generated in the output shaft 3011 of the engine 3001 is transferred to the input shaft 3021 of the automatic transmission 3002. At this time, as fluid flows through the pair of first fluid passing apertures 3741 which are formed in the middle of the housing 3073, to be filled into the fluid passing space 3733 and the pair of fluid passing grooves 3734 which are formed in each rotating cam 3731 constituting the cam valve 3071 are opened, the cam inclined surface 3735 which is formed at the side wall of each fluid passing groove 3734 is rotated to smoothly discharge fluid without an abrupt pressure change.

Further, in the case that fluid pressure is abruptly elevated in a state wherein fluid flows or is stopped, the air bladder member 3082 which is received in the pressure regulating chamber 3081 of the pressure regulating section 3008 disposed adjacent the fluid flowing way 3005 is pressed to allow a portion of fluid to flow into the pressure regulating chamber 3081, whereby it is possible to prevent the torque converter from being broken.

On the other hand, FIG. 22 is a structural diagram illustrating an interlocking relationship between the torque converter in accordance with the third embodiment of the present invention and an accelerator. The torque converter further includes a torque converter control section 3009 which is connected to the coil ring 3062 constituting the valve control section 3006 through a variable resistor 3091 which is in turn connected to an accelerator 3092, so that power supply level is adjusted depending upon a degree to which the accelerator 3092 is pressed by the foot of a driver. If the accelerator 3092 is not pressed, current is not supplied to the coil ring 3062, whereby the fluid control section 3007 which is disposed in the fluid flowing way 3005 is maintained in the closed state. Accordingly, in the case that the accelerator 3092 is not pressed, a transmission gear shift can be made due to the fact that fluid flows through the fluid flowing way 3005.

FIG. 23 is of side cross-sectional views illustrating gears in accordance with another embodiment of the present invention, wherein FIG. 23A depicts a main gear and FIG. 23B depicts an auxiliary gear. A plurality of holes 3471 in each of which a ball 3472 and a spring 3473 are mounted, are respectively formed between teeth of the main gear 3004 or between teeth of the auxiliary gears 3041 and 3042. A fluid passage 3474 which connects the plurality of holes 3471, is formed in the radially inward of the plurality of holes 3471.

Therefore, in the case that a fluid load is generated at teeth of the main gear 3004 and/or the auxiliary gears 3041 and 3042, the plurality of holes 3471 are opened by operations of the balls 3472 and the springs 3473, whereby pressure in the gear rooms 3031, 3032 and 3033 is balanced while fluid passes through the fluid passage 3474 which is formed in each of the gears 3004, 3041 and 3042.

In addition, FIG. 24 is a schematic view illustrating a valve control section in accordance with another embodiment of the present invention. The valve control section 3006 comprises a cylinder 3063 which is provided at one end thereof; a piston 3064 which is disposed in the cylinder 3063 and has a rod 3641 mounted thereto, the rod 3641 being connected at one end thereof to the horizontally extending rack 3611; and a housing 3065 positioned at the other end of the rod 3641 and having a spool 3651 mounted therein, the spool 3651 being moved forward and backward by a solenoid 3066, are connected to the housing 3065 via a spring 3652 and formed at a middle portion thereof with first and second circumferential grooves 3653 and 3654, with the first and second circumferential grooves 3653 and 3654 communicated with the cylinder 3063 via first and second fluid paths 3655 and 3656, respectively, the housing 3065 being formed, at portions except those where the first and second circumferential grooves 3653 and 3654 are formed, with an inlet fluid path 3657 through which fluid is sucked and a pair of outlet fluid paths 3658 which are located at both sides of the inlet fluid path 3657 and through which fluid is discharged.

Accordingly, the housing 3065 controls the horizontally extending rack 3611 while being moved by operations of the solenoid 3066. At this time, a smooth operation of the horizontally extending rack 3611 is ensured by the fact that outside fluid flows into the spool 3651 and inside fluid is discharged to the outside through the spool 3651.

FIG. 25 is a side elevation view illustrating a pressure regulating section in accordance with another embodiment of the present invention. The pressure regulating section 3008 comprises a forward direction check valve 3831 and a backward direction check valve 3832. A pair of fluid paths 3083 are formed at upper and lower parts of the gear room between the main gear 3004 and each auxiliary gear 3041 or 3042 such that they are aligned parallel. The forward direction check valve 3831 and the backward direction check valve 3832 are mounted in two parallel fluid paths 3083, respectively, such that they are arranged in an opposite direction from each other, to achieve pressure balance when pressure differential is created in the gear room.

FIG. 26 is a schematic view illustrating a pressure regulating section in accordance with still another embodiment of the present invention. The pressure regulating section 3008 comprises a spool 3084 which is moved leftward and rightward when pressure differential is created in the gear room and which is formed at its middle portion with a passing groove 3841 and at one end with a pair of left and right locking grooves 3842 and 3843. The spool 3084 is mounted in the fluid flowing way 3005. The fluid flowing way 3005 defines adjacent a center part of the passing groove 3841 a first fluid path 3844 which is connected to the main gear room 3031 and at a point opposed to the first fluid path 3844 second and third fluid paths 3845 and 3846 which are connected to the first and second auxiliary gear rooms 3032 and 3033, respectively.

Accordingly, if pressure differential is created in the gear room, the spool 3084 is moved to open the first fluid path 3844. By this, fluid passing through the first fluid path 3844 flows through the second and third fluid paths 3845 and 3846 into the first and second auxiliary gear rooms 3032 and 3033, to achieve pressure balance through the entire gear room.

FIG. 27 is a front cross-sectional view illustrating a torque converter in accordance with a fourth embodiment of the present invention, and FIG. 28 is a side cross- sectional view taken along the line XXVIII-XXVIII of FIG. 27.

The torque converter of this embodiment comprises a rotary housing 4001 and fluid control means 4002. 1_e rotary housing 4001 is integrally connected to an input shaft 4061 of an automatic transmission 3 (see FIG. 1) such that it receives power from an output shaft 4051 of an engine 2 (see FIG. 1) and transfers the power to the input shaft 4061 of the automatic transmission 3 after the changing torque of received power. The rotary housing 4001 is formed with a main gear room 4011 in which a main gear 4111 connected to the output shaft 4051 of the engine 2 is inwardly mounted, a pair of auxiliary gear rooms 4012 which are defined at both sides of the main gear room 4011 and in which a pair of auxiliary gears 4121 are mounted, respectively, and first and second fluid chambers 4013 and 4014 which are defined above and below the main gear room 4011, respectively, and are filled with fluid. The first and second fluid chambers 4013 and 4014 have shaft inserting holes 4131 and 4141 which are defined at a rear part thereof and fluid flowing passages 4132 and 4142 which are defined at upper and lower parts thereof, respectively. The fluid control means 4002 has first and second spools 4021 and 4022 which are inserted into the first and second fluid chambers 4013 and 4014 of the rotary housing 4001 and have at front parts thereof first and second fluid amount adjusting shafts 4211 and 4221, respectively, first and second connection shafts 4023 which extend into the rotary housing 4001 and connected to rear parts of the first and second spools 4021 and 4022, respectively, and a rotary plate 4024 which is connected to rear ends of the first and second connection shafts 4023 and moved forward and backward under a control of a control section 4025.

Especially, the input shaft 4061 of the automatic transmission 3 is fastened to an outward and rearward portion of the rotary housing 4001 such that it is aligned with the output shaft 4051 of the engine 2 on the same axis .

The first and second spools 4021 and 4022 constituting the fluid control means 4002 are formed inwardly thereof with curved surfaces which are similar to curved surfaces formed in the main gear room 4011 in which the main gear 4111 is mounted, so as not to impose any influence on rotation of the main gear 4111 when the first and second spools 4021 and 4022 are moved forward.

The first and second fluid amount adjusting shafts 4211 and 4221 are mounted so that fluid filled in the first and second fluid chambers 4013 and 4014 is balanced in its amount when the first and second spools 4021 and 4022 are moved forward and backward. The first and second fluid amount adjusting shafts 4211 and 4221 perform a function of a guide.

Lost fluid replenishing means 4015 is mounted in the fluid flowing passage 4132 which is formed at the upper part of the first fluid chamber 4013, for replenishing fluid which is lost due to abrasion or heat generated upon rotation of the main gear 4111 and the pair of auxiliary gears 4121. The lost fluid replenishing means 4015 comprises a fluid tank 4151 having an air hole 4151a, and a fluid inlet pipe 4152 connected to the first fluid chamber 4013 and having a check valve 4152a installed therein.

First, in the case that the engine 2 is idly rotated, a condition in which the output shaft 4051 of the engine 2 is rotated and the input shaft 4061 of the automatic transmission 3 is stopped must be satisfied (see FIGs. 27 and 28). Accordingly, if the control section 4025 constituting the fluid control means 4002 fully moves backward the rotary plate 4024 which is connected to the control section 4025 after recognizing a neutral position of a transmission gear shift lever, the first and second spools 4021 and 4022 which are connected to the pair of connection shafts 4023, are fully moved backward in the first and second fluid chambers 4013 and 4014, respectively, and at the same time, the main gear room 4011 is fully opened. By this, fluid which is filled in the first and second fluid chambers 4013 and 4014 is concentrated forward, and the auxiliary gears 4121 are idly rotated in view of the fact that fluid flows between teeth of the auxiliary gear 4121 when the main gear 4111 connected to the output shaft 4051 of the engine 2 is rotated.

Therefore, the output shaft 4051 of the engine 2 which is connected to the main gear 4111, is rotated, and the input shaft 4061 of the automatic transmission 3 is maintained in a stopped state. In other words, input torque of the automatic transmission 3 equals zero.

On the contrary, if engine power is perfectly transferred to the automatic transmission 3, a condition in which torque of output power of the engine 2 equals to torque of input power of the automatic transmission 3 must be satisfied (see FIGs . 23 and 24). Accordingly, if the control section 4025 constituting the fluid control means 4002 fully moves forward the rotary plate 4024 which is connected to the control section 4025, the first and second spools 4021 and 4022 which are connected to the pair of connection shafts 4023, are fully moved forward in the first and second fluid chambers 4013 and 4014, respectively, and at the same time, the main gear room 4011 is fully closed. By this, fluid which is filled in the first and second fluid chambers 4013 and 4014 is concentrated rearward of the first and second spools 4021 and 4022 through the fluid flowing passages 4132 and 4142 which are defined at upper and lower parts of the first and second fluid chambers 4013 and 4014, and at the same time, flow of fluid which is filled in the main gear room 4011 and the auxiliary gear rooms 4012 is stopped. In other words, a state wherein the main gear 4111 and the auxiliary gears 4121 are integrally and rigidly connected with each other by fluid is maintained.

At this time, if the main gear 4111 which is connected to the output shaft 4051 of the engine 2 is rotated in a forward direction, because fluid which is filled in the gear rooms 4011 and 4012 rigidly connects the main gear 4111 and the auxiliary gears 4121 with each other, the auxiliary gear 4121 revolves about the main gear 4111, and the rotary housing 4001 is rotated at the same rpm as the main gear 4111. According to this, on the assumption that fluid loss is neglected, it is possible to perfectly transfer power of the output shaft 4051 of the engine 2 to the input shaft 4061 of the automatic transmission 3.

On the other hand, if engine power is transferred to the automatic transmission 3 while being varied, a condition in which torque of output power of the engine 2 is larger than torque of input power of the automatic transmission 3 must be satisfied (see FIGs . 27 and 28). Accordingly, if the control section 4025 constituting the fluid control means 4002 moves to a middle position the rotary plate 4024 which is connected to the control section 4025, after recognizing a variable power transfer situation, fluid flow which passes through the fluid flowing passages 4132 and 4142 is reduced to half, and at the same time, the main gear room 4011 is opened to half. In other words, one portion of fluid which is filled in the gear rooms 4011 and 4012 is maintained in the gear rooms 4011 and 4012 and the other portion of the fluid which is filled in the gear rooms 4011 and 4012 flows through the fluid flowing passages 4013 and 4014 rearwardly of the first and second spools 4021 and 4022. At this time, if the main gear 4111 which is connected to the output shaft 4051 of the engine 2 is rotated in a forward direction, because fluid which is filled in the gear rooms 4011 and 4012 flows at velocity which corresponds to that at an intermediate state between a fully opened state and a fully closed state of the first and second fluid chambers 4021 and 4022, the auxiliary gear 4121 is rotated half a turn while the main gear 4111 is rotated a full turn. In other words, due to the fact that when the main gear 4111 is rotated a full turn in the forward direction, fluid pressure which biases teeth of the auxiliary gear 4121 is reduced to half, the rotary housing 4001 is rotated half a turn in the forward direction.

Therefore, in the case that torque of power generated by the output shaft 4151 of the engine 2 is transferred to the input shaft 4161 of the automatic transmission 3 after being finely adjusted, by adjusting the opening degree of the first and second fluid chambers 4021 and 4022 through the control section 4025 constituting the fluid control means 4002, torque of the output shaft 4051 of the engine 2 can be transferred to the input shaft 4061 of the automatic transmission 3 in a state wherein torque thereof is varied.

FIG. 29 is a front cross-sectional view illustrating a torque converter in accordance with a fifth embodiment of the present invention; and FIG. 30 is a side cross- sectional view taken along the line XXX-XXX of FIG. 29. The torque converter of this embodiment comprises a rotary housing 4003 and fluid control means 4004. rotary housing 4003 is integrally connected to an input shaft 4061 of an automatic transmission 3 such that it receives power from an output shaft 4051 of an engine 2 and transfers the power to the input shaft 4061 of the automatic transmission 3 after the changing torque of received power. The rotary housing 4003 is formed with a main gear room 4031 in which a main gear 4311 connected to the output shaft 4051 of the engine 2 is centrally and inwardly mounted, a pair of auxiliary gear rooms 4032 which are defined at both sides of the main gear room 4031 and in which a pair of auxiliary gears 4321 are mounted, respectively, and a circular fluid chamber 4033 which is arranged in the rearward of the main gear room 4031 and filled with fluid, with a pair of fluid flowing passages 4331 defined above and below the circular fluid chamber 4033, respectively. The fluid control means 4004 has a circular spool 4041 which is inserted into the circular fluid chamber 4033 of the rotary housing 4003, a pair of connection members 4042 which extend through the fluid flowing passages 4331, respectively, and are connected to a rear part of the circular spool 4041, a pair of forward and backward moving shafts 4043 which extend through the rotary housing 4003 and are connected to the pair of connection members 4042, respectively, and a rotary plate 4044 which is fixed to rear ends of the pair of forward and backward moving shafts 4043 and is connected to a control section 4045.

Especially, width LI of the pair of connection members 4042 which connect the circular spool 4041 and the pair of forward and backward moving shafts 4043 is larger than width L2 of the fluid flowing passages 4332 which are defined at upper and lower parts of the circular fluid chamber 4033.

First, in the case that the engine 2 is idly rotated, a condition in which the output shaft 4051 of the engine 2 is rotated and the input shaft 4061 of the automatic transmission 3 is stopped must be satisfied (see FIGs. 29 and 30). Accordingly, if the control section 4045 constituting the fluid control means 4004 fully moves backward the rotary plate 4044 which is connected to the control section 4045 after recognizing a neutral position of a transmission gear shift lever, the circular spool 4041 which is connected to the pair of forward and backward moving shafts 4043, is fully moved backward in the circular fluid chamber 4033, and at the same time, the rearward of main gear room 4031 is fully opened. By this, fluid which is filled in the circular fluid chamber 4033 is concentrated forward of the circular spool 4041, and the auxiliary gears 4321 are idly rotated in view of the fact that fluid flows between teeth of the auxiliary gear 4321 when the main gear 4311 connected to the output shaft 4051 of the engine 2 is rotated.

Therefore, the output shaft 4051 of the engine 2 which is connected to the main gear 4311, is rotated, and the input shaft 4061 of the automatic transmission 3 is maintained in a stopped state. In other words, input torque of the automatic transmission 3 equals zero.

On the contrary, if engine power is perfectly transferred to the automatic transmission 3, a condition in which torque of output power of the engine 2 equals to torque of input power of the automatic transmission 3 must be satisfied (see FIGs. 29 and 30). Accordingly, if control section 4045 constituting the fluid control means 4004 fully moves forward the rotary plate 4044 which is connected to the control section 4045, the circular spool 4041 which is connected to the pair of forward and backward moving shafts 4043 is moved forward, and at the same time, the rearward of the main gear room 4031 is fully closed. By this, fluid which is filled in the circular fluid chamber 4033 is concentrated rearward of the circular spool 4041 through the fluid flowing passages 4132 and 4142 which are defined at upper and lower parts of the circular fluid chambers 4033, and at the same time, flow of fluid which is filled in the main gear room 4031 and the auxiliary gear rooms 4032 is stopped. In other words, a state wherein the main gear 4311 and the auxiliary gears 4321 are integrally and rigidly connected with each other by fluid is maintained.

At this time, if the main gear 4311 which is connected to the output shaft 4051 of the engine 2 is rotated in a forward direction, because fluid which is filled in the gear rooms 4031 and 4032 rigidly connects the main gear 4311 and the auxiliary gears 4321 with each other, the auxiliary gear 4321 revolves about the main gear 4311, and the rotary housing 4003 is rotated at the same rpm as the main gear 4311. According to this, on the assumption that fluid loss is neglected, it is possible to perfectly transfer power of the output shaft 4051 of the engine 2 to the input shaft 4061 of the automatic transmission 3.

On the other hand, if engine power is transferred to the automatic transmission 3 while being varied, a condition in which torque of output power of the engine 2 is larger than torque of input power of the automatic transmission 3 must be satisfied (see FIGs. 29 and 30). Accordingly, if the control section 4045 constituting the fluid control means 4004 moves to a middle position the rotary plate 4044 which is connected to the control section 4045, after recognizing a variable power transfer situation, one portion of fluid which is filled in the gear rooms 4031 and 4032 is maintained in the gear rooms 4031 and 4032 and the other portion of the fluid which is filled in the gear rooms 4031 and 4032 flows through the fluid flowing passages 4331 rearwardly of the circular spool 4041.

At this time, if the main gear 4311 which is connected to the output shaft 4051 of the engine 2 is rotated in a forward direction, because fluid which is filled in the gear rooms 4011 and 4012 flows at velocity which corresponds to that at an intermediate state between a fully opened state and a fully closed state of the first and second fluid chambers 4021 and 4022, the auxiliary gear 4121 is rotated half a turn while the main gear 4311 is rotated a full turn. In other words, due to the fact that when the main gear 4311 is rotated a full turn in the forward direction, fluid pressure which biases teeth of the auxiliary gear 4321 is reduced to half, the rotary housing 4003 is rotated half a turn in the forward direction.

Therefore, in the case that torque of power generated by the output shaft 4151 of the engine 2 is transferred to the input shaft 4161 of the automatic transmission 3 after being finely adjusted, by adjusting the opening degree of the gear rooms 4031 and 4032 through the control section 4045 constituting the fluid control means 4004, torque of the output shaft 4051 of the engine 2 can be transferred to the input shaft 4061 of the automatic transmission 3 in a state wherein torque thereof is varied.

Industrial Applicability

As described above, by the present invention, advantages are provided in that since a torque converter for an automatic transmission is actuated using fluid pressure, it is possible to prevent fuel from being wasted due to a load as generated in a conventional torque converter . Also, it is possible to prevent fuel from being wasted due to idle rotation of a power input shaft upon initial actuation of the torque converter.

Further, since torque corresponding to engine output can be obtained while the torque converter is actuated, perfect power transfer can be accomplished while an automobile runs.

In addition, by the fact that fluid pressure is used upon transferring engine power, it is possible to prevent the torque converter from being broken and capability thereof from being deteriorated.

Moreover, since fluid flow is optimized when opening or closing fluid by actuating the torque converter, it is possible to prevent excessive pressure from being applied to a gear and a housing, whereby life time of the torque converter is extended and reliability thereof is also elevated.

Besides, since a pressure regulating section is disposed in a fluid flowing passage, it is possible to minimize a load while a gear is rotated, whereby life time of the torque converter is extended.

Also, since a fluid flowing passage for connecting respective supply port and discharge port with each other is independently disposed in a gear room, precision of the torque converter can be raised.

Moreover, since the torque converter is interlocked with an accelerator, it is possible to enable a gear shift to be implemented when the accelerator is not operated, whereby gear shift operations can be easily performed. And, when engine power is no longer transferred to the transmission, a perfect operation of a brake is ensured. Further, since fluid pressure in the gear room is adjusted within respective gears, it is possible to prevent the torque converter from being broken or mis- actuated due to a load.

In the drawings and specification, there have been disclosed typical preferred embodiments of the invention and, although specific terms are employed, they are used in a generic and descriptive sense only and not for purposes of limitation, the scope of the invention being set forth in the following claims.

Claims

1. A torque converter for an automatic transmission, mounted between an output shaft of an engine and an input shaft of the automatic transmission for transferring engine power to the automatic transmission, the torque converter comprising: a rotary housing connected to the input shaft of the automatic transmission and formed with a gear room having a main gear room in which a main gear connected to the output shaft of the engine is mounted and at least one auxiliary gear room which is arranged at a side of the main gear room and in which at least one auxiliary gear meshing with the main gear is mounted, the rotary housing having first and second space portions arranged at upper and lower parts of the gear room, respectively, between the main gear room and the auxiliary gear room, the first and second space portions being communicated with each other through a fluid flowing passage; and fluid control means disposed in the fluid flowing passage of the rotary housing and having a fluid control valve and a control section for controlling operation of the fluid control valve.

2. A torque converter for an automatic transmission as claimed in claim 1, wherein the input shaft of the automatic transmission is aligned with the output shaft of the engine on the same axis, in the rearward of the main gear room formed in the rotary housing.

3. A torque converter for an automatic transmission as claimed in claim 1, wherein lost fluid replenishing means is disposed in the middle of the fluid flowing passage; and the lost fluid replenishing means includes a fluid tank having an air hole, for replenishing fluid which is lost upon rotation of the main gear and the auxiliary gear, and a fluid inlet pipe connected to the fluid flowing passage and having a check valve installed therein.

4. A torque converter for an automatic transmission as claimed in claim 1, wherein the rotary housing is formed with a gear room which has the main gear room and first and second auxiliary gear rooms located at both sides of the main gear room, respectively; the main gear connected to the output shaft of the engine is mounted in the main gear room, and first and second auxiliary gears are mounted in the first and second auxiliary gear rooms at both sides of the main gear, respectively; and the rotary housing has first and second space portions which are arranged at upper and lower parts of the gear room between the main gear and the first and second auxiliary gears, with fluid flowing passages diagonally defined between the first and second space portions.

5. A torque converter for an automatic transmission as claimed in claim 4, wherein a spool mounting hole is defined in the rotary housing such that it extends through the fluid flowing passage; and fluid control means which has a spool possessing at a front part thereof a fluid flowing groove for controlling fluid flow while being moved forward and backward and a control section for controlling forward and backward movement of the spool, is mounted in the spool mounting hole.

6. A torque converter for an automatic transmission, comprising: a rotary housing formed with a gear room having a main gear room which has a fluid chamber inward thereof and in which a main gear connected to an output shaft of an engine is mounted, and first and second auxiliary gear rooms which are arranged at both sides of the main gear room, respectively, and in which first and second auxiliary gears are mounted at both sides of the main gear, respectively; fluid control means mounted in the main gear, the fluid control means having a spool inserted into the main gear to prevent outside fluid from flowing into the gear room, a rotational shaft fixed to the spool and a rotary plate fixed to the rotational shaft; transmission connection means positioned in the rearward of the spool and having a front end integrally connected to the rotary housing and a rear end connected to an input shaft of the automatic transmission, the transmission connection means including a pair of connection shafts which are formed with a fluid inlet passage and a fluid outlet passage for supplying and discharging fluid into and from the rotary housing, respectively; and spool control means having a forward and backward moving section for controlling stroke movement of the rotary plate and a control section for controlling operation of the forward and backward moving section.

7. A torque converter for an automatic transmission as claimed in claim 6, wherein lost fluid replenishing means is provided in the fluid chamber which is arranged in the rearward of the main gear room; and the lost fluid replenishing means has a safety valve which comprises a through hole, a push bolt, a spring and a valve packing, the lost fluid replenishing means further having a replenishing fluid supply hole which is formed forwardly of the through hole and is communicated with the gear room.

8. A torque converter for an automatic transmission as claimed in claim 6, wherein a spool mounting hole into which the spool is inserted, is formed in a center part of the main gear; and a plurality of fluid flowing slots through which outside fluid is supplied into the gear room and inside fluid is discharged into the fluid chamber arranged in front of the spool, are formed around the spool mounting hole.

9. A torque converter for an automatic transmission as claimed in claims 6 or 8, wherein a circumferential outer surface of the spool is formed with a plurality of prominences for opening and closing the plurality of fluid flowing slots, respectively, formed in the main gear, and a plurality of horizontal fluid flowing grooves through which fluid flowing inward through the fluid inlet passage formed in the transmission connection means is supplied into the gear room, with the plurality of prominences and the plurality of horizontal fluid flowing grooves alternately formed.

10. A torque converter for an automatic transmission as claimed in claim 6, wherein a plurality of cooling fins for lowering temperature inside the gear room upon operation of the torque converter are mounted onto a circumferential outer surface of the rotary housing.

11. x A torque converter for an automatic transmission as claimed in claims 6 or 8, wherein a vane room which has an elliptical configuration and in which a vane is mounted, is defined in the rotary housing; a spool mounting hole into which the spool is inserted, is formed in a center part of the vane; and a plurality of fluid flowing slots are formed around the spool mounting hole.

12. A torque converter for an automatic transmission, comprising: a rotary housing having a main gear room in which a main gear is mounted and first and second auxiliary gear rooms in which first and second auxiliary gears are mounted, respectively, with first through fourth fluid passing holes formed at upper and lower parts of boundary regions between the main gear room and the first and second auxiliary gear rooms, with a pair of fluid flowing ways defined between the first and second fluid passing holes and between the third and fourth fluid passing holes, respectively; a valve control section having a movable magnetic ring which defines a circumferential outer surface of the rotary housing and is formed at a circumferential inner surface thereof with a horizontally extending rack and a coil ring which is mounted around a circumferential outer surface of the movable magnetic ring and connected to a power source for controlling operation of the movable magnetic ring; and a fluid control section and a pressure regulating section each being disposed in the course of each fluid flowing way, the fluid control section being opened and closed by the movable magnetic ring and being equipped with a cam valve.

13. A torque converter for an automatic transmission as claimed in claim 12, wherein at least one compression coil spring is mounted between a side surface of the movable magnetic ring and a side surface of a ring gear which projects from an engine, for returning the movable magnetic ring to its original position.

14. A torque converter for an automatic transmission as claimed in claim 12, wherein a press piece which is biased by a spring, is disposed in a rear part of each auxiliary gear room, and a fluid remaining room is defined at a side of each auxiliary gear room, the fluid remaining room being connected with a fluid passage for moving the press piece forward and backward.

15. A torque converter for an automatic transmission as claimed in claim 12, wherein the fluid control section comprises a pinion which is positioned at a side thereof and is rotated while being meshed with the horizontally extending rack formed in the movable magnetic ring, and a cam valve which is mounted to a center shaft of the pinion and is positioned inside a housing; the cam valve comprises a pair of rotating cams which are arranged such that they are opposite to each other and a bracket which connects center portions of the pair of rotating cams with each other; each rotating cam is formed with a pair of fluid passing grooves which are opposed to each other, and a cam inclined surface for lowering sucking velocity and discharging velocity of fluid is formed at a side wall of each fluid passing groove such that it is inclined inward; the housing is formed with a pair of first fluid passing apertures which are communicated with a fluid passing space and are opposite to each other, and at positions which correspond to mounting positions of the pair of rotating cams, the housing is formed with two pairs of second fluid passing apertures so that the two pairs are opposed to each other; and a single fluid flowing way is connected to each pair of first and second fluid passing apertures .

16. A torque converter for an automatic transmission as claimed in claim 12, wherein the pressure regulating section comprises a pressure regulating chamber which is formed adjacent the fluid flowing way such that it is communicated with the fluid flowing way, and an air bladder member which is received in the pressure regulating chamber.

17. A torque converter for an automatic transmission as claimed in claim 12, further comprising: a torque converter control section connected to the coil ring constituting the valve control section through a variable resistor which is in turn connected to an accelerator, so that power level is adjusted depending upon pressing of the accelerator.

18. A torque converter for an automatic transmission as claimed in claim 12, wherein the valve control section comprises : a cylinder provided at one end of the valve control section; a piston which is disposed in the cylinder and has a rod mounted thereto, the rod being connected at one end thereof to the horizontally extending rack; and a housing positioned at the other end of the rod and having a spool mounted therein, the spool being moved forward and backward by a solenoid, connected to the housing via a spring and formed at a middle portion thereof with first and second circumferential grooves, with the first and second circumferential grooves communicated with the cylinder via first and second fluid paths, respectively, the housing being formed, at portions except those where the first and second circumferential grooves are formed, with an inlet fluid path through which fluid is sucked and a pair of outlet fluid paths which are located at both sides of the inlet fluid path and through which fluid is discharged.

19. A torque converter for an automatic transmission as claimed in claim 12, wherein a plurality of holes in each of which a ball and a spring are mounted, are formed respectively between teeth of the main gear or teeth of the auxiliary gear; and a fluid passage which connects the plurality of holes, is formed radially inward of the plurality of holes.

20. A torque converter for an automatic transmission as claimed in claim 12, wherein the pressure regulating section comprises a forward direction check valve and a backward direction check valve which are mounted in a reverse direction from each other and in a parallel relationship with each other, to keep pressure balance when pressure differential is created in the gear room.

21. A torque converter for an automatic transmission as claimed in claim 12, wherein, as the pressure regulating section, a spool which is moved leftward and rightward when pressure differential is created in the gear room and which is formed at its middle portion with a passing groove and at one end with a pair of left and right locking grooves, is mounted in the fluid flowing way, with the fluid flowing way defining adjacent a center part of the passing groove a first fluid path which is connected to the main gear room and at a point opposed to the first fluid path second and third fluid paths which are connected to the first and second auxiliary gear rooms, respectively.

22. A torque converter for an automatic transmission, comprising: a rotary housing having a main gear room in which a main gear connected to an output shaft of an engine is centrally and inwardly mounted, a pair of auxiliary gear rooms which are defined at both sides of the main gear room and in which a pair of auxiliary gears are mounted, respectively, and first and second fluid chambers which are defined above and below the main gear room, respectively, and filled with fluid, each of the first and second fluid chambers having a shaft inserting hole which is defined at a rear part thereof and a fluid flowing passage which is defined at an upper part or a lower part thereof; and fluid control means having first and second spools which are inserted into the first and second fluid chambers of the rotary housing and have at front parts thereof first and second fluid amount adjusting shafts, respectively, first and second connection shafts which extend into the rotary housing and connected to rear parts of the first and second spools, respectively, and a rotary plate which is connected to rear ends of the first and second connection shafts and moved forward and backward under a control of a control section.

23. A torque converter for an automatic transmission as claimed in claim 22, wherein lost fluid replenishing means is mounted in the fluid flowing passage which is formed at the upper part of the first fluid chamber; and the lost fluid replenishing means includes a fluid tank having an air hole, for replenishing fluid which is lost due to abrasion or heat generated upon rotation of the main gear and the pair of auxiliary gears, and a fluid inlet pipe connected to the first fluid chamber and having a check valve installed therein.

24. A torque converter for an automatic transmission, comprising: a rotary housing having a main gear room in which a main gear connected to an output shaft of an engine is centrally and inwardly mounted, a pair of auxiliary gear rooms which are defined at both sides of the main gear room and in which a pair of auxiliary gears are mounted, respectively, and a circular fluid chamber which is arranged in the rearward of the main gear room and filled with fluid, with a pair of fluid flowing passages defined above and below the circular fluid chamber, respectively; and fluid control means having a circular spool which is inserted into the circular fluid chamber of the rotary housing, a pair of connection members which extend through the fluid flowing passages, respectively, and are connected to a rear part of the circular spool, a pair of forward and backward moving shafts which extend through the rotary housing and are connected to the pair of connection members, respectively, and a rotary plate which is fixed to rear ends of the pair of forward and backward moving shafts and is connected to a control section.