GB2158168A - An automatic transmission for a vehicle - Google Patents

An automatic transmission for a vehicle Download PDF

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Publication number
GB2158168A
GB2158168A GB08411030A GB8411030A GB2158168A GB 2158168 A GB2158168 A GB 2158168A GB 08411030 A GB08411030 A GB 08411030A GB 8411030 A GB8411030 A GB 8411030A GB 2158168 A GB2158168 A GB 2158168A
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GB
United Kingdom
Prior art keywords
shaft
sleeve
planetary gear
input
input shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB08411030A
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GB8411030D0 (en
GB2158168B (en
Inventor
Shuzo Moroto
Shiro Sakakibara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin AW Co Ltd
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Aisin AW Co Ltd
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Publication date
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Priority to GB08411030A priority Critical patent/GB2158168B/en
Publication of GB8411030D0 publication Critical patent/GB8411030D0/en
Publication of GB2158168A publication Critical patent/GB2158168A/en
Application granted granted Critical
Publication of GB2158168B publication Critical patent/GB2158168B/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/065—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the friction or endless flexible member type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

An automatic transmission for a vehicle comprises a fluid coupling 15, a belt type continuously- variable speed transmission (CVT) 3, a planetary gear mechanism 6 and a differential device 2. The planetary gear mechanism includes a first input shaft 51 and a second input shaft 52, wherein when the first input shaft is connected to an output shaft of CVT through a clutch 7, a forward range gear train is formed, whereas when the second input shaft is connected to the output of CVT by the clutch, a reverse range gear train is formed. A low-high speed changeover mechanism 9 including a brake is provided in the planetary gear mechanism, and a first element 93 and a second element 94 of the planetary gear mechanism are selectively held in a stationary position by means of the brake to selectively form the forward range high-speed gear train and forward range low speed gear train. The clutch and the brake are provided with recesses 74, 75, 96, 97 in one part thereof and are provided with projections 77, 98 in the other part which are fitted to the recesses, and the dimension of the outside diameter thereof is reduced as compared with that of clutches or brakes of a wet multiple-disc type. <IMAGE>

Description

SPECIFICATION An automatic transmission for a vehicle The present invention relates to an automatic transmission suitable for a vehicle which uses a belt type continuously-variable speed transmission system (hereinafter referred to as "CVT").
A belt drive CVT comprises an input pulley, an output pulley and an endless belt extended between the pulleys. The input pulley and the output pulley each comprise a fixed sheave secured to a rotational shaft and a movable sheave mounted movably in an axial direction of said rotational shaft by means of a servo motor. The movable sheave can be displaced axially thereby to change the ratio of rotational speed of the output pulley relative to that of the input pulley in the range of approximately 0.5 to 2.0.
When the CVT is used as the transmission for a vehicle, a first rotational shaft having the input pulley of CVT mounted thereon is generally connected to an output shaft of an engine through a coupling means. Between a second rotational shaft having the output pulley of CVT mounted thereon and a differential device there is provided a planetary gear mechanism and a forward-reverse changeover mechanism.
A low-high speed changeover mechanism is provided in the planetary gear mechanism, if necessary. Generally speaking, the forwardreverse changeover mechanism and the lowhigh speed changeover mechanism have to be provided with a clutch for connecting specific elements of the planetary gear mechanism or a brake adapted to connect a specific element of the planetary gear mechanism in a stationary position. However, when a wet multipledisc type clutch or brake is employed as the aforementioned clutch or brake, it is difficult to instal the transmission on a small automobile because the diameter of a frictional engaging element of said wet multiple-disc type clutch or brake is large. This means that the whole transmission is large for such a vehicle.
What is needed is an automatic transmission for a vehicle having a miniature and light weight forward-reverse changeover gear mechanism or a low-high speed changeover gear mechanism, for installment between the rotational shaft having the output pulley of CVT mounted thereof and a transmission output shaft for a vehicle.
According to the present invention there is provided an automatic transmission suitable for a vehicie, comprising, a planetary gear mechanism having a first input shaft, a second input shaft and an output shaft, each of the first and second input shafts having splines on the input end thereof, the planetary gear mechanism including at least a forward range gear train using the first input shaft as an input shaft of the gear train and a reverse range gear train using the second input shaft as an input shaft of the gear train, and a clutch means having a rotatable sleeve and a shift lever being engaged with the sleeve at one end thereof, the sleeve having splines thereon adapted to mesh selectively with splines formed on said first and second input shafts, the shift lever being adapted to shift the sleeve between a position where the sleeve is selectively connected to the first input shaft to establish the forward range gear train and a position where the sleeve is selectively connected to the second input shaft to establish the reverse range gear train.
Generally speaking, the present invention provides an automatic transmission for a vehicle especially suitable for a small size, front-engine front-wheel drive automobile provided with a belt type continuously-variable speed transmission system (CVT) and a planetary gear mechanism. The CVT may comprise an input pulley mounted on a first shaft, an output pulley mounted on a second shaft and an endless belt extended between the input pulley and output pulley to transmit power, the first shaft being disposed coaxially with and coupled to an output shaft of a coupling means, and the second shaft being disposed parallel with the first shaft. The input pulley and output pulley may each comprise a fixed sheave and a movable sheave, as is known.
The planetary gear mechanism may have its input shaft and output shaft disposed coaxially with the second shaft of the CVT and comprise at least one forward speed range and one reverse range.
The planetary gear mechanism usable in the present invention includes a first input shaft, a second input shaft and an output shaft and is of the type in which the output shaft of the CVT is selectively connected to the first input shaft through a clutch thereby to establish the forward range, whereas the output of the CVT is selectively connected to the second input shaft to thereby establish the reverse range.
The clutch is in the form of a dog clutch.
A low-high speed changeover mechanism may be provided in the planetary gear mechanism. The low-high speed changeover mechanism may include first and second discs disposed perpendicularly to and rotatably with respect to a rotational axis of the output shaft of the planetary gear mechanism, a sleeve which is movable axially with respect to the rotational axis and non-rotatable with respect thereto, and a shift lever one end of which is engaged with the sleeve, the first and second discs being formed with splines, the sleeve being formed with splines selectively engageable with the splines formed on the first and second discs.When the sleeve is shifted by the shift lever to a position where the sleeve is selectively connected to the first disc, a gear train for establishing the forward range of the planetary gear mechanism is formed whereas when the sleeve is shifted by the shift lever to a position where the sleeve is selectively connected to the second disc, a gear train for establishing another forward range is formed.
Accordingly, the present invention enables the provision of an improved automatic transmission including a CVT and a planetary gear mechanism for a vehicle, which automatic transmission is capable of establishing a forward range gear train when a first input shaft of the planetary gear mechanism is selectively connected to an output shaft of the CVT by a clutch means and of establishing a reverse range gear train when a second input shaft of the planetary gear train is selectively connected to the output shaft of the CVT by the clutch means.
The present invention also enables the provision of an improved and compact automatic transmission including a CVT and a planetary gear mechanism for a vehicle which automatic transmission is capable of establishing a forward range gear train when a first input shaft of the planetary gear mechanism is selectively connected to an output shaft of the CVT by means of a dog clutch means having a reduced diameter as compared with a wet multiple-disc type clutch means and of establishing a reverse range gear train when a second input shaft of the planetary gear train is selectively connected to the output shaft of the CVT by means of a dog clutch means.
The present invention further enables the provision of an improved automatic transmission including a CVT and a planetary gear mechanism for a vehicle which is capable of establishing a forward range gear train when a first element of the planetary gear mechanism is selectively fixed in a stationary position by means of brake means and of establishing another forward range gear train when a second element of the planetary gear train is selectively fixed in a stationary position by means of brake means.
For a better understanding of the invention, and to show how it may be put into effect, reference will now be made, by way of example, to the accompanying drawings, in which: Figures 1 through 6 are respectively schematic sectional views showing six different embodiments of the present invention.
Fig. 1 shows an embodiment in which the present invention is applied to an automatic transmission for a vehicle of the front-engine front-wheel drive system. This automatic transmission comprises a coupling means 15, a belt type continuously-variable speed transmission system (CVT) 3, a planetary gear mechanism 6, a differential device 2 and a transmission housing 70 for accommodating these elements and fixedly mounted on an engine 1. The housing 70 is partially shown in Fig. 1.
The coupling means 1 5 is shown in the form of a fluid coupling including an input shaft 1 6 connected coaxially with an output shaft (not shown) of the engine 1 and an output shaft 1 7 disposed coaxially with the input shaft 1 6 Other automatic clutch means such as a torque converter, a centrifugal clutch, a magnetic clutch, etc. can be used in place of the fluid coupling 1 5.
The CVT 3 comprises an input pulley 31 mounted on a first shaft 4, an output pulley 32 mounted on a second shaft 5, and an endless belt 33 extended between the pulleys 31 and 32 to transmit power. The pulleys 31, 32 each has fixed sheaves 31 A, 32A secured to the shafts 4, 5, and movable sheaves 31 B, 32B mounted slidably axially on the shafts 4, 5, respectively. Each of the movable sheaves 31 B, 32B is operated by hydraulic servomotor mounted on the shafts 4, 5, respectively. The first shaft 4 is disposed coaxially with the output shaft 1 7 of the coupling means 1 5 and coupled thereto. The second shaft 5 is formed in the form of a tubular shaft, whose rotational axis is arranged parallel with the rotational axis of the first shaft 4.
The planetary gear mechanism 6 includes a first input shaft 51, a second input shaft 52 and an output shaft 53, which are in the form of a tubular shaft, the shafts 51, 52 and 53 being arranged coaxially with the second shaft 5 of the CVT 3. The planetary gear mechanism 6 comprises two sets of planetary gear set and a reduction gear mechanism 8. The first planetary gear set comprises a first sun gear 61 concentrically secured to the second input shaft 52, a first ring gear 62 disposed concentrically with the sun gear 61, a first planetary gear 63 meshing with the sun gear 61 and ring gear 62 and a first planetary carrier 64 for rotatably supporting the planetary gear 63.The second planetary gear set comprises a second sun gear 65 concentrically secured to the second input shaft 52, a second ring gear 66 disposed concentrically with the sun gear 65, a second planetary gear 67 meshing with the sun gear 65 and ring gear 66 and a second planetary carrier 68 for rotatably supporting the planetary gear 67.
The first planetary carrier 64 is connected to the housing 70 in the stationary state so that it may not be rotated with respect to the housing 70, the first ring gear 62 is connected to the second planetary carrier 68 and further connected to a sun gear 81 which also functions as an input gear of a reduction gear mechanism 8 which is hereinafter described, and the second ring gear 67 is connected to the first input shaft 51. It is noted that the first ring gear 62 can be directly connected to the output shaft 53 to omit the reduction gear mechanism 8.
The reduction gear mechanism 8 comprises a sun gear 81 disposed coaxially with the first and second sun gears 61, 65 of the planetary gear mechanism 6, a ring gear 82 disposed concentrically with the sun gear 81, a planetary gear 83 meshing with the sun gear 81 and ring gear 82 and a planetary carrier 84 for rotatably supporting the planetary gear 83.
The sun gear 81 is connected to the first ring gear 62 and the second planetary carrier 68 of the planetary gear mechanism 6, the ring gear 82 is connected to the housing 70 in the stationary state in such a way that the ring gear 82 is not rotated with respect to the housing 70, and the planetary carrier 84 is concentrically connected to the output shaft 53. Thus, the reduction gear mechanism 8 functions as a part of the planetary gear mechanism 6.
The output shaft 53 of the planetary gear mechanism 6 is connected to a gear casing 21 of the differential device 2 concentrically with the rotational axis thereof. The differential device 2 comprises differential gears 22, 23 secured to a shaft supported on the casing 21 perpendicularly to the rotational axis of the casing 21, and output gears 24, 25 meshing with the gears 22, 23 and rotatably supported on the casing 21 with respect to the rotational axis of the casing 21. The output gears 24, 25 each connect with output shafts 28, 29, respectively, which are adapted for connection with an axle (not shown) used to drive front wheels.
The fluid coupling 15 and input pulley 31 of the CVT 3 are rotatably mounted on the housing 70 by means of the first shaft 4, and the output pulley 32 of the CVT 3, planetary gear mechanism 6 and differential device 2 are rotatably supported on the housing 70 by means of the second shaft 5 and output shaft 53.
A clutch 7 is formed between the output pulley 32 of the CVT 3 and the planetary gear mechanism 6. The clutch 7 includes splines 73 formed on the outer circumferential edge of an output end of the output shaft 5 of the CVT 3, splines 74, 75 formed on the outer circumferential edges of input ends of the first and second input shafts 51 and 52 of the planetary gear mechanism 6, respectively, a sleeve 72 which is disposed concentrically with and rotatable with respect to the rotational axis of the input shafts 51, 52 of the planetary gear mechanism 6 and is movable in the direction of the rotational axis, splines 76 formed on the inner circumference of the sleeve 72 and always engaging the splines 73 formed on the output shaft 5, splines 77 formed on the inner circumference of the sleeve 72 and selectively engageable with the splines 74 formed on the first input shaft 51, the splines 75 formed qn the second input shaft 52, a shift ring 79 slidably engaged with a groove formed on the outer circumference of the sleeve 72, and a shift lever 71 one end of which engages the shift ring 79 and supported on the transmission housing 70. When the shift lever 71 is operated to move the sleeve 72 in a direction as indicated by the arrow D shown in Fig. 1 in the direction of the rotational axis, the splines 77 formed on the inner circumference of the sleeve 72 come to mesh with the splines 74 formed on the first input shaft 51 to permit the first input shaft 51 to rotate integrally with the output shaft 5 and allow the second input shaft 52 to rotate freely. Hence the forward range gear train is formed.When the sleeve 72 is moved axially in a direction as indicated by the arrow R shown in Fig. 1, the splines 77 come to mesh with the splines 75 formed on the second input shaft 52 to permit the second input shaft 52 to rotate integrally with the output shaft 5 and allow the first input shaft 52 to rotate freely. Hence the reverse range gear train is formed. The other end of the shift lever 71 projects beside the driver's seat in the vehicle.
The embodiment of the present invention shown in Fig. 1 operates as follows. The engine 1 of the vehicle is started and the shift lever 71 projected besides the driver's seat is positioned to the forward or reverse position to move the shift ring 79. If the engine 1 is in the idling mode, engine torque generated by the engine 1 may not be transmitted to the input pulley 31 of the CVT 3 through the fluid coupling 15, and therefore the sleeve 72 of the clutch 7 is readily spline-coupled with the first input shaft 51 or the second input shaft 52. Next, an accelerator pedal is pressed down by the driver, the engine torque is transmitted to the input pulley 31 of the CVT 3 by means of the fluid coupling 1 5 when the throttle opening of the engine exceeds a predetermined value, and the vehicle starts to move.As is known, the CVT 3 continuously varies the ratio of rotational speed between the input shaft 4 and output shaft 5. The torque transmitted to the output shaft 5 of the CVT 3 is transmitted to the front wheels through the planetary gear mechanism 6, differential device 2 and output shafts 28, 29.
In the above-described transmission, the clutch 7 disposed between the output shaft 5 of the CVT 3 and the input shafts 51, 52 of the planetary gear mechanism 6 is of the form of a dog clutch in which the splines 77 formed on the sleeve 72 selectively engage with the splines 74 formed on the first input shaft 51 and with the splines 75 formed on the second input shaft 52. The size of the clutch 7 can be considerably reduced and the efficiency of transmission of torque from the output shaft 5 to the first input shaft 51 or second input shaft 52 is not lessened.
Another embodiment of the present invention, shown in Fig. 2, is different from one shown in Fig. 1 in connecting means of two rows of planetary gear sets in the planetary mechanism 6. The only difference between the two embodiments is in the final reduction ratio of the planetary gear mechanism 6 but the remainder of the Fig. 2 embodiment is the same as that shown in Fig. 1. Accordingly, the explanation for the same parts as those of Fig. 1 will be omitted.
In Fig. 2, the first sun gear 61 and second sun gear 65 are connected to the second input shaft 52, the first ring gear 62 is connected to the first input shaft 51, the first planetary carrier 64 and second ring gear 66 are connected to the sun gear 81 of the reduction gear mechanism 8, and the second planetary carrier 68 is connected to the transmission housing 70 in the state wherein the carrier 68 is not rotatable with respect to the transmission housing 70.
The operation of this embodiment is the same as that of the embodiment shown in Fig. 1.
Another embodiment of the present invention shown in Fig. 3 is different from that shown in Fig. 1 in connecting means of two rows of planetary gear sets in the planetary mechanism 6. Again, the only difference between the embodiments is in the final reduction ratio of the planetary gear mechanism 6, but the remainder of the Fig. 3 embodiment is the same as that shown in Fig. 1. Accordingly, explanation for the same parts as those of Fig. 1 will be omitted.
In Fig. 3, the first sun fear 61 is connected to the second input shaft 52, the first ring gear 62 and second sun gear 65 are connected to the first input shaft 51, the first planetary carrier 64 and second planetary carrier 68 are connected to the sun gear 81 of the reduction gear mechanism 8, and the second ring gear 66 is connected to the transmission housing 70 in the state wherein the ring gear 66 is not rotatable with respect to the transmission housing 70.
The operation of this embodiment is the same as that of the embodiment shown in Fig. 1.
Fig. 4 shows an embodiment of the present invention in which a low-high speed changeover mechanism 6 is further provided in the planetary gear mechanism 9 in the automatic transmission for the vehicle shown in Fig. 1.
Accordingly, the explanation for the parts common to the embodiment shown in Fig. 1 will be omitted.
The low-high speed changeover mechanism 9 includes first and second discs 93, 94 formed on the inner circumferential edges thereof with splines 96, 97, respectively, a second sleeve 92 which is disposed concentrically with the rotational axis of the first and second input shafts 51 and 52 of the planetary gear mechanism 6 and movable along but non-rotatable with respect to the rotational axis of the input shafts 51, 52, and is formed on the inner circumference thereof with splines 98 selectively engaging the splines 96, 97 formed on said two discs 93, 94, respectively, and at least one guide pin 95 loosely supported on the sleeve 92.Each of the first and the second discs 93, 94 is rotatable concentrically with respect to the rotational axis of the input shafts 51, 52 and has a mean plane thereof in a plane vertical and perpendicular to the rotational axis of said first and second input shafts 51, 52. The first disc 93 is connected to the first planetary carrier 64 of the planetary gear mechanism 6 and is rotatable concentrically relative to the first and second input shafts 51 and 52, and the second disc 94 is connected to the second input shaft 52 for rotation concentrically and integrally therewith.The second sleeve 92 has a key 100 formed on the outer circumference thereof axially and integrally, said key is fitted into a groove 99 formed on the transmission housing 70, the second sleeve 92 is movable in the direction of the rotational axis of the input shafts 51 and 52 but non-rotatable with respect to the rotational axis. A shift ring 101 is fitted into a circumferential groove formed on the outer circumference of the second sleeve 92. One end of a shift lever 102 directly or indirectly associated with the shift lever 71 is engaged with the shift ring 101.
The second sleeve 92 is shifted in a direction of arrow L or H shown in Fig. 4 by means of the shift lever 102.
When the sleeve 92 is shifted in the direction as indicated by the arrow L, the splines 98 formed on the sleeve 92 come to mesh with the splines 96 formed on the first disc 93 to connect the first planetary carrier 64 to the transmission housing 70 to hold the carrier 64 in a stationary position and allow the second disc 94 to be rotated freely. The forward range low-speed gear train, which is the same as the gear train of the planetary gear mechanism 6 shown in Fig. 1, is thereby formed. When the second sleeve 92 is shifted in the direction as indicated by the arrow H, the splines 98 formed in the sleeve 92 come to mesh with the splines 97 formed on the second disc 94 to connect the second input shaft 52 to the transmission housing 70 to hold the first and second sun gears 61, 65 in a stationary position relative to the housing 70 and allow the first disc 93 to rotate freely.
A forward range high-speed gear train is thereby formed.
The guide pin 95 is disposed between opposed surfaces of the first and second discs 93 and 94 with its length parallel with the rotational axis of the first and second input shafts 51 and 52. When the sleeve 92 is shifted in the direction of arrow L or H, one end of the guide pin 95 comes to abut with either the first disc 93 or second disc 94, whereby the rotation of the disc is braked to stop, thus facilitating the spline-coupling between the second sleeve 92 and the first disc 93 or the second disc 94.
The low-high speed changeover mechanism 9 has a reduced outer diameter as compared with that of the wet multiple-disc brake, but the braking force to preclude the rotation of the first input shaft 51 or the second input shaft 52 and to hold the shaft in the stationary position with respect to the housing 70 by the spline-coupling is large compared with that of the multiple-disc brake.
In the embodiment shown in Fig. 4, the changeover from the forward range low-speed gear train to the forward range high-speed train or the changeover from the forward range high-speed gear train to the forward range low-speed gear train is carried out by shifting the second sleeve 92 by means of the shift lever 102 and the shift ring 101. In this operation, one end of the guide pin 95 which is loosely supported on the second sleeve 92 comes into contact with the first disc 93 or the second disc 94 to brake and stop its rotation. Thereafter, the splines 98 formed on the second sleeve 92 engage with the splines 96 formed on the first disc 93 or with the splines 97 formed on the second disc 94.
Therefore, the engagement between these splines is extremely simply and positively effected.
Fig. 5 shows another embodiment of the present invention in which a low-high speed changeover mechanism 9 is provided in the planetary gear mechanism 6 in the automatic transmission for a vehicle shown in Fig. 2.
This mechanism 9 comprises a first disc 93, a second disc 94, a second sleeve 92, a guide pin 95, a shift ring 101 and a shift lever 102, which are the same construction as that of the low-high speed changeover mechanism 9 described in connection with Fig. 4. The sleeve 92 has a key 100, which is axially formed on the outer circumference thereof, and is fitted into a groove 99 formed on the transmission housing 70. The explanation of details of the mechanism 9 and parts common to the transmission shown in Fig. 2 will be omitted.
In this embodiment, the low-high speed changeover mechanism 9 is disposed in between the first planetary gear set and the second planetary gear set of the planetary gear mechanism 6. The first disc 93 is connected to the second planetary carrier 68. The second disc 94 is connected to the second input shaft 52. When the second sleeve 92 is moved in the direction of arrow L shown in Fig. 5, the rotation of the first disc 93 is braked by action of the guide pin 95, the splines 98 formed on the sleeve 92 engage with the splines 96 formed on the first disc 93, and the first disc 93 is connected to the transmission housing 70 to hold the carrier 68 in a stationary position relative to the housing 70. A forward range low-speed gear train similar to that shown in Fig. 2 is thereby formed.When the second sleeve 92 is moved in the direction of arrow H shown in Fig. 5, the first disc 93 rotates freely, the second disc 94 is braked by the second sleeve 92, and the second input shaft 52 is connected to the transmission housing 70 to hold the sun gears 61, 65 in a stationary position relative to the housing 70. The forward range high-speed gear train is thereby formed.
Fig. 6 shows another embodiment of the present invention in which a low-high speed changeover mechanism is further provided in the planetary gear mechanism 6 in the automatic transmission for a vehicle shown in Fig.
3. This mechanism includes a first disc 93, a second disc 94, a second sleeve 92, a guide pin 95, a shift ring 101 and a shift lever 102, which are the same construction as that of the low-high speed changeover mechanism 9 described in connection with Fig. 4. The sleeve 92 has a key 100, which is axially formed on the outer circumference thereof, and which is fitted into a groove 99 formed on the transmission housing 70. The explanations of details of the mechanism 9 and parts common to the transmission shown in Fig. 3 will be omitted. In this embodiment, the low-high speed changeover mechanism 9 is disposed between the clutch 7 and the planetary gear mechanism 6 in a way similar to the transmission shown in Fig. 4.The first disc 93 is connected concentrically with the second ring gear 66 of the planetary gear mechanism 6 and the second disc 94 is connected concentrically with the second input shaft 52 of the planetary gear mechanism 6. When the second sleeve 92 is moved in the direction of arrow L shown in Fig. 6, the rotation of the first disc 93 is braked by action of the guide pin 95, the splines 98 formed on the second sleeve 92 engage with the splines 96 formed on the first disc 93, and the first disc 93 and second ring gear 66 are connected to the transmission housing 70 to hold the ring gear 66 in a stationary position relative to the housing 70. A forward low-speed gear train similar to that shown in Fig. 3 is thereby formed. When the second sleeve 92 is moved in the direction of arrow H shown in Fig. 5, the first disc 93 rotates freely, the second disc 94 is braked by the second sleeve 92, and the second input shaft 52 is connected to the transmission housing 70 to hold the ring gear 62 and sun gear 65 in a stationary position relative to the housing 70. The forward range high-speed gear train is thereby formed.

Claims (14)

1. An automatic transmission suitable for a vehicle, comprising, a planetary gear mechanism having a first input shaft, a second input shaft and an output shaft, each of the first and second input shafts having splines on the input end thereof, the planetary gear mechanism including at least a forward range gear train using the first input shaft as an input shaft of the gear train and a reverse range gear train using the second input shaft as an input shaft of the gear train, and a clutch means having a rotatable sleeve and a shift lever being engaged with the sleeve at one end thereof, the sleeve having splines thereon adapted to mesh selectively with splines formed on said first and second inputs shafts, the shift lever being adapted to shift the sleeve between a position where the sleeve is selectively connected to the first input shaft to establish the forward range gear train and a position where the sleeve is selectively connected to the second input shaft to establish the reverse range gear train.
2. An automatic transmission as claimed in Claim 1 comprising a coupling means having an input shaft and an output shaft.
3. An automatic transmission as claimed in Claim 2, wherein the coupling means is a fluid coupling, a torque converter, a certifugal clutch or a magnetic clutch.
4. An auotmatic transmission as claimed in Claim 1, 2 or 3, comprising a continuouslyvariable speed transmission (CVT) system having a first (input) shaft and a second (output) shaft.
5. An automatic transmission as claimed in Claim 5, wherein the CVT system is a belt type CVT system.
6. An automatic transmission as claimed in Claim 6, wherein the CVT system has an input pulley mounted coaxially on the first shaft, an output pulley mounted coaxially on the second shaft and a belt extending between the first and second pulleys to transfer power, each of the first and second pulleys having a fixed sheave and a movable sheave, the second shaft being disposed in parallel with the first shaft.
7. An automatic transmission as claimed in Claim 4, 5 or 6 when dependent on Claim 2 or 3, wherein the first shaft of the CVT system is disposed coaxially with and rotationally coupled with the output shaft of the coupling means.
8. An automatic transmission as claimed in any one of Claims 4 to 7, wherein both of the input shafts of the planetary gear mechanism and the output shaft of the planetary gear mechanism are disposed coaxially with and rotatably with respect to the rotational axis of the second shaft of the CVT system.
9. An automatic transmission as claimed in any one of Claims 4 to 8, wherein the rotatable sleeve of the clutch means is disposed coaxially, slidably with and rotationally linked to the second shaft of the CVT system.
10. An automatic transmission as claimed in any one of Claims 1 to 9, comprising a low-high speed changeover mechanism.
11. An automatic transmission as claimed in Claim 10, wherein the low-high speed changeover mechanism comprises first and second discs disposed perpendicularly to and rotatably with respect to the rotational axis of the output shaft of the planetary gear mechanism, a second sleeve disposed coaxially with and slidably but not rotatably with respect to the rotational axis of the output shaft of the planetary gear mechanism and a shift lever being engaged with one end of the second sleeve, the first disc being linked to a first element of the planetary gear mechanism and having splines thereon, the second disc being linked to a second element of the planetary gear mechanism and having splines thereon, the second sleeve having splines adapted to mesh selectively with splines formed on the first and second discs, the shift lever being adapted to shift the second sleeve between a position where the second sleeve is connected with the first disc for holding the first element of the planetary gear mechanism in a stationary position to establish the forward range gear train and a position where the sleeve is connected with the second disc for holding the second element of the planetary gear mechanism in a stationary position to establish another forward range gear train.
1 2. An automatic transmission as claimed in Claim 11, wherein the low-high speed changeover mechanism further includes at least one guide pin disposed between the first and second discs in a direction parallel with the rotational axis of the output shaft of said planetary gear mechanism and being loosely supported on the second sleeve, whereby the guide pin contacts selectively with one of said first and second discs for synchronizing the rotational speed of the disc and the second sleeve when the second sleeve is shifted to one of the two positions.
1 3. An automatic transmission for a vehicle, comprising, a coupling means having an input shaft and an output shaft; a belt type continuously-variable speed transmission system having an input pulley mounted coaxially on a first shaft, an output pulley mounted coaxially on a second shaft and a belt extending between the first and second pulleys to transfer power, each of the first and second pulleys having a fixed sheave and a movable sheave, the first shaft being disposed coaxially with and rotationally coupled with the output shaft of the coupling means, the second shaft being disposed in parallel with the first shaft;; a planetary gear mechanism having a first input shaft, a second input shaft and an output shaft, each of the input shafts and the output shaft being disposed coaxially with and rotatably with respect to the rotational axis of the second shaft of the belt type continuouslyvariable speed transmission system, each of the first and second input shafts having splines on the input end thereof, the planetary gear mechanism including at least a forward range gear train using the first input shaft as an input shaft of the gear train and a reverse range gear train using the second input shaft as an input shaft of the gear train, and a clutch means having a sleeve disposed coaxially, slidably with and rotationally linked to the second shaft of the belt type continuously-variable speed transmission system and a shift lever being engaged with the sleeve at one end thereof, the sleeve haivng splines thereon adapted to selectively mesh with the splines formed on the first and second input shafts, the shift lever being adapted to shift the sleeve between a position where the sleeve is selectively connected to the first input shaft to establish the forward range gear train and a position where the sleeve is selectively connected to the second input shaft to establish the reverse range gear train.
14. An automatic transmission substantially as herein described.
1 5. A vehicle having an automatic transmission as claimed in any one of Claims 1 to 14.
GB08411030A 1984-04-30 1984-04-30 An automatic transmission for a vehicle Expired GB2158168B (en)

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GB08411030A GB2158168B (en) 1984-04-30 1984-04-30 An automatic transmission for a vehicle

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Application Number Priority Date Filing Date Title
GB08411030A GB2158168B (en) 1984-04-30 1984-04-30 An automatic transmission for a vehicle

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GB8411030D0 GB8411030D0 (en) 1984-06-06
GB2158168A true GB2158168A (en) 1985-11-06
GB2158168B GB2158168B (en) 1987-12-09

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB399885A (en) * 1932-03-24 1933-10-19 Frederick Henry Royce Improvements in epicyclic gears

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB399885A (en) * 1932-03-24 1933-10-19 Frederick Henry Royce Improvements in epicyclic gears

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Publication number Publication date
GB8411030D0 (en) 1984-06-06
GB2158168B (en) 1987-12-09

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PCNP Patent ceased through non-payment of renewal fee

Effective date: 19980430