KR20160080997A - Transmission of vehicle - Google Patents
Transmission of vehicle Download PDFInfo
- Publication number
- KR20160080997A KR20160080997A KR1020140193959A KR20140193959A KR20160080997A KR 20160080997 A KR20160080997 A KR 20160080997A KR 1020140193959 A KR1020140193959 A KR 1020140193959A KR 20140193959 A KR20140193959 A KR 20140193959A KR 20160080997 A KR20160080997 A KR 20160080997A
- Authority
- KR
- South Korea
- Prior art keywords
- shaft
- clutch
- power
- plate clutch
- synchronous
- Prior art date
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
- F16D13/52—Clutches with multiple lamellae Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
-
- 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
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
- F16H3/38—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with synchro-meshing
Abstract
Description
The present invention relates to a vehicle transmission, and more particularly to a power shift transmission suitable for a working vehicle such as a tractor.
A power shift transmission that can be automatically shifted in place of a manual transmission has been developed. Most power shift gearboxes use the same wet multi-plate clutch as conventional cars to change speed and travel direction.
A wet multi-plate clutch is a must for an automatic transmission, but it has less power efficiency than a mechanical transmission. In addition, the wet multi-plate clutch requires hydraulic pressure for the operation of the hydraulic actuator, and the hydraulic pump must always be operated to provide a constant pressure and flow rate at all times.
When the hydraulic pump is driven, the power for driving the transmission and the working machine is lost because the power of the engine is consumed in proportion to the pressure and the flow rate to be formed. Further, since a separate pump and a cooler for cooling are required, the wet multi-plate clutch occupies a lot of installation space as compared with the mechanical transmission.
To overcome this limitation, attempts have been made to construct a transmission using a wet multi-plate clutch and a mechanical synchronous clutch.
However, according to the related art, the power transmission path is complicated by mixing the two types of clutches, and it is difficult to downsize.
SUMMARY OF THE INVENTION The present invention has been made to solve the above problems of the prior art and provides a transmission capable of simplifying a power transmission path and having excellent power transmission efficiency and miniaturization while using a hydraulic multi-plate hydraulic clutch and a mechanical synchronous clutch .
In order to achieve the above object, according to one aspect of the present invention, there is provided a transmission for transmitting engine power of a vehicle, comprising: an input shaft rotated by an engine; And a wet clutch pack which is connected to the input shaft and which is driven by hydraulic pressure to connect or disconnect power, And a synchronous clutch having a synchronous clutch pack for connecting or disconnecting power by synchronizing the gears is provided on the first connection shaft, and the first multi-plate clutch and the synchronous clutch Wherein the power transmission path is functionally connected to change the power transmission path to perform the shifting, Clutch pack is provided to the transmission to be staggered with each other so as not to overlap an axial position.
According to one embodiment, the synchronous clutch pack is located on the downstream side of the wet clutch pack.
According to one embodiment, the first wet multi-plate clutch includes a first multi-plate clutch portion and a second multi-plate clutch portion selectively connected to the input shaft, and the synchronous clutch selectively connects the first multi- Wherein the first synchronous clutch portion is operatively connected to the first multi-plate clutch portion and the second multi-plate clutch portion, and the second synchronous clutch portion is operatively connected to the first synchronous clutch portion and the second synchronous clutch portion, And is operatively connected to the multi-plate clutch portion.
According to one embodiment, on the driven shaft, there is provided a second wet multi-plate clutch which is actuated by hydraulic pressure to connect or disconnect the power, and the first wet multi-plate clutch and the second wet multi- By selectively changing the power transmission path by engaging, four-speed shifting is achieved.
According to one embodiment, eight-speed shifting is achieved by selectively engaging the synchronous clutch, the first wet multi-plate clutch and the second wet multi-plate clutch with the corresponding shaft to selectively change the power transmission path.
According to one embodiment, the first connection shaft and the driven shaft are formed coaxially.
According to one embodiment, on the driven shaft, a forward-reverse clutch capable of changing the rotating direction of the driven shaft is formed.
According to one embodiment, the synchronous clutch and the forward / reverse clutch are constituted by a synchromesh mechanism.
According to one embodiment, the transmission further includes a sub shift portion that selectively transmits the rotational driving force of the driven shaft to the output shaft connected to the wheels of the vehicle, and the sub shift portion is provided in a state of being parallel to the driven shaft at the side of the driven shaft And a third connection shaft that transmits power to the output shaft via a third connection shaft that is formed on the output shaft and a fourth connection shaft that is formed in a straight line with the driven shaft, .
According to one embodiment, the driven shaft and the output shaft connected to the wheels of the vehicle are formed coaxially.
1 is a diagram of a transmission according to an embodiment of the present invention.
FIG. 2 is a longitudinal axial view of the input shaft, the first connecting shaft, and the second connecting shaft of the transmission of FIG. 1;
Fig. 3A is a diagram for explaining a power transmission path in the vicinity of the first and third stages of the transmission of Fig. 1; Fig.
3B is a diagram for explaining a power transmission path in the vicinity of the second and fourth stages of the transmission of FIG.
Fig. 4A is a diagram for explaining a power transmission path in the vicinity of the fifth and seventh stages of the transmission of Fig. 1; Fig.
Fig. 4B is a diagram for explaining a power transmission path in the vicinity of the sixth and eighth stages of the transmission of Fig. 1; Fig.
5A to 5C are diagrams illustrating a power transmission path in the case of a negative speed change of the transmission of FIG.
Fig. 6 is a diagram for explaining a power transmission path when the transmission of Fig. 1 is reversed. Fig.
Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. Although the present invention has been described with reference to the embodiments shown in the drawings, it is to be understood that the technical idea of the present invention and its essential structure and operation are not limited thereby.
1 is a diagram of a transmission according to an embodiment of the present invention.
1, the transmission includes an
The
Here, "parallel relationship" means that the two axes are arranged side by side so that the gears connected to the two axes can be directly engaged with each other.
A third connecting
A fourth connecting
The term " upstream " as used herein refers to the direction in which the engine is located in the drawing, and the term "downstream " means the direction in which the final end of the transmission of power is located. Sometimes, the term " upstream "means the side to which power is input by one member, and the term" downstream " means that the power input from the member is transmitted.
A second connecting
2 is an axial view of the
2, the
According to this embodiment, the first connecting
Referring again to FIG. 1, a first wet
As will be described later, the first wet
The wet multi-disc clutch has a structure in which a plurality of drive discs and a driven disc are repeatedly arranged in turn in the clutch housing. More specifically, the clutch pressure spring simultaneously presses the pressure plate, the drive disk, and the driven disk so that the clutch hub is integrated with the clutch housing, so that the driving force of the shaft is transmitted to the clutch hub by the clutch housing rotating with the shaft, The formed drive gear can be rotated.
Conversely, by disengaging the clutch hub from the clutch housing, power transmission between the shaft and the clutch hub can be interrupted.
The structure of the wet type multi-plate clutch operated by the hydraulic pressure is already known, and a detailed description thereof will be omitted here.
The
The synchromesh transmission mechanism is a transmission mechanism that forms a clutch gear in front of the transmission, and a synchronizer ring that moves the clutch gear and the sleeve to move the sleeve to perform shifting. When shifting, the gear teeth of the sleeve and the gear teeth of the synchronizer ring engage as the sleeve moves. In this state, the sleeve is moved toward the clutch gear. At this time, the portion where the clutch gear and the synchronizer ring abut each other is smooth, and as the friction is increased, the number of revolutions of the two gears becomes equal.
The construction and operation principle of the synchromesh transmission mechanism are well known, and therefore, a detailed description thereof will be omitted here.
The first wet
The synchromesh mechanism constituting the
The
According to the present embodiment, the synchronous clutch pack 130 'is located on the downstream side of the wet
The clutch pack is relatively bulky in structure constituting the clutch and is difficult to reduce its volume. According to the present embodiment, the wet
The first wet multi-plate clutch 110 according to the present embodiment is a two-stage clutch in which the first multi-plate
The first
The second
Here, "freely rotatable" does not mean that one structure can rotate without any friction with respect to another structure, but bearing frictional force can be applied through a member such as a bearing, but rotational force is directly transmitted It is to be understood that the present invention encompasses cases where it can be seen that the present invention is not limited to the above.
The
Here, "functionally connected" means not only that the first configuration and the second configuration are directly connected to each other, but also the power output from the first configuration is connected to the second configuration via the third configuration As shown in FIG.
According to the present embodiment, the
The synchronizing
A
The
The
That is, the first synchronous clutch portion of the
A
The
The first connecting
Conversely, when the
The driven
The forward and reverse clutch 140 includes a
The
A
A
The
When the
Conversely, when the
On the other hand, on the
Driving gears 152 and 153 are formed on both ends of the
The second connecting
The
The rotational force of the first connecting
A second wet
The third multi-plate
A third
A fourth
Four driving gears 51, 52, 53 and 54 are formed on the third connecting
At the downstream end of the driven
A cylindrical
An output shaft (80) is formed coaxially with the fourth connecting shaft (60) at the downstream end of the fourth connecting shaft (60). The
The
The
A
Between the
The
The fourth connecting
Conversely, when the
On the other hand, a fifth connecting
The fifth connecting
The synchro shaft (71) has a clutch gear (72) at an upstream end and a drive gear (73) at a downstream end. The
A
The
A
A single-stage wet multi-plate clutch 77 capable of stopping the rotation of the fifth connecting
According to this embodiment, the rotational driving force of the driven
Hereinafter, referring to Figs. 3A and 3B, the power transmission path along the periphery of the first to fourth stages of the transmission of the present embodiment will be described.
FIG. 3A is a diagram illustrating a power transmission path in the first and third stages, and FIG. 3B is a diagram illustrating a power transmission path in the second and fourth stages.
It is assumed that the forward and reverse clutch 140 is connected to the forward side in the peripheral speed.
And follows the path indicated by the solid black solid arrow in FIG.
The first multi-plate
The
In the first to fourth stages, the
The first multi-plate
Since the
Since the
As the driven
The first multi-plate
Following the path indicated by the solid black solid arrow in FIG.
The second multi-plate
Since the
The first multi-plate
And follows the path indicated by the thick black solid line and the dotted line arrow in FIG.
In the third stage, the power transmission path from the
As the driven
The first multi-plate
Followed by the path indicated by the thick black solid line and the dotted line arrow in FIG.
In the fourth stage, the power transmission path from the
The transmission according to the present embodiment is capable of eight stages of peripheral speed through the
Hereinafter, referring to Figs. 4A and 4B, a power transmission path along the periphery of the fifth to eighth stages of the transmission of the present embodiment will be described.
And the path indicated by an arrow in bold black solid line in FIG.
The first multi-plate
In the fifth to eighth stages, the second synchronous clutch portion remains connected to the first connecting
The first multi-plate
The rotation of the
As the
Since the
The rotational force of the first connecting
When the first multi-plate
And follows the path indicated by the bold black solid arrow in FIG.
The second multi-plate
Since the
The rotational force of the first connecting
The first multi-plate
And the path indicated by the solid black solid lines and dotted line arrows in FIG.
In the seventh stage, the power transmission path from the
As the driven
The first multi-plate
And the path indicated by the thick black solid line and the dotted line arrow in FIG.
The power transmission path from the
The transmission according to the present embodiment is provided with a third speed change portion capable of three-speed shifting, so that a total of 24 speeds are possible (except for reverse speed change).
Hereinafter, with reference to Figs. 5A to 5C, the power transmission path according to the negative speed change of the transmission of the present embodiment will be described.
5A is a diagram for explaining the power transmission path of the one-stage shift, FIG. 5B is a diagram for explaining the power transmission path of the two-stage shift, and FIG. 5C is a diagram for explaining the power transmission path of the three- .
The
5A, as the third connecting
As the
The
The
5B, the
On the other hand, the
As the third connecting
5C, the
As the third connecting
The
Fig. 6 is a diagram for explaining the power transmission path when the transmission is retracted according to the present embodiment. Fig. For ease of explanation, the power transmission to the
The sleeve 149 moves to the right to connect the
6, when the
As the
The
At this time, the rotational direction of the driven
According to the present embodiment, by mixing a hydraulic multi-plate hydraulic clutch and a mechanical synchronous clutch, the size of the transmission can be reduced and the structure can be simplified.
In addition, since the length of the shafts for transmitting the power is short, a ball bearing capable of receiving an inexpensive but thrust can be used as a bearing for supporting the shaft on the frame, and a helical gear having an axial thrust .
In the drawing, black circles represent ball bearings, and black squares represent needle bearings.
Also, since the rotational force of the
Claims (10)
An input shaft 10 rotated by an engine;
A first connecting shaft 20 connected to the input shaft 10 so as to be parallel with the input shaft 10; And
And a driven shaft (40) rotated by the power of the input shaft (10) via the first connecting shaft (20)
A first wet multi-plate clutch 110 is provided on the input shaft 10 and includes a wet clutch pack 113 that is operated by hydraulic pressure to connect or disconnect power,
On the first connecting shaft 20, there is provided a synchronous clutch 130 having a synchronous clutch pack 130 'that connects or disconnects power by synchronizing gears,
The first wet multi-plate clutch 110 and the synchronous clutch 130 are functionally connected to change the power transmission path to perform shifting,
Wherein the wet clutch pack (113) and the synchronous clutch pack (130 ') are staggered from one another so that their axial positions do not overlap.
Wherein the synchronous clutch pack (130 ') is located downstream of the wet clutch pack (113).
The first wet multi-plate clutch 110 selectively includes a first multi-plate clutch portion 111 and a second multi-plate clutch portion 112 connected to the input shaft 10,
The synchronous clutch 130 selectively connects the first synchronous clutch part 131, 132, 133, 134 and the second synchronous clutch part 135, 136, 137 connected to the first connection shaft 20, And,
The first synchronous clutch unit 131, 132, 133, 134 is operatively connected to the first multi-plate clutch unit 111 and the second multi-plate clutch unit 112,
Wherein the second synchronous locking clutch portion (135, 136, 137) is operatively connected to the second multi-plate clutch portion (112).
A second wet multi-plate clutch 120 is provided on the driven shaft 40 to operate or block the power by being operated by hydraulic pressure.
Wherein the first wet multi-plate clutch (110) and the second wet multi-plate clutch (120) are selectively engaged with corresponding axes to selectively change the power transmission path, thereby achieving four-speed shifting.
The synchromesh clutch 130, the first wet multi-plate clutch 110 and the second wet multi-plate clutch 120 selectively engage corresponding shafts to selectively change the power transmission path so that an eight- Features a transmission.
And the first connecting shaft (20) and the driven shaft (40) are formed coaxially.
And a forward / backward clutch (140) is formed on the driven shaft (40) to change the rotational direction of the driven shaft (40).
Wherein the synchromesh clutch (130) and the forward / reverse clutch (140) are constituted by a synchromesh mechanism.
Further comprising a sub shift portion selectively transmitting the rotational driving force of the driven shaft (40) to an output shaft (80) connected to the wheels of the vehicle,
Wherein the auxiliary speed-
First and second gear shifts for transmitting power to the output shaft (80) via a third connecting shaft (50) formed parallel to the driven shaft (40) on the side of the driven shaft (40)
Is configured to perform a three-stage shifting to transmit power to the output shaft (80) via a fourth connecting shaft (60) formed in a straight line with the driven shaft (40).
Wherein the driven shaft (40) and the output shaft (80) connected to the wheels of the vehicle are coaxially formed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020140193959A KR102030198B1 (en) | 2014-12-30 | 2014-12-30 | Transmission of vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020140193959A KR102030198B1 (en) | 2014-12-30 | 2014-12-30 | Transmission of vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| KR20160080997A true KR20160080997A (en) | 2016-07-08 |
| KR102030198B1 KR102030198B1 (en) | 2019-10-08 |
Family
ID=56503307
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| KR1020140193959A KR102030198B1 (en) | 2014-12-30 | 2014-12-30 | Transmission of vehicle |
Country Status (1)
| Country | Link |
|---|---|
| KR (1) | KR102030198B1 (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR19990059802A (en) * | 1997-12-31 | 1999-07-26 | 정몽규 | Car continuously variable transmission |
| KR20050066090A (en) | 2003-12-26 | 2005-06-30 | 현대자동차주식회사 | Multi-plate clutch for an automatic transmission |
| JP2008095748A (en) * | 2006-10-06 | 2008-04-24 | Yanmar Co Ltd | Transmission |
| JP2010096215A (en) * | 2008-10-14 | 2010-04-30 | Mitsubishi Agricult Mach Co Ltd | Traveling change gear of working vehicle |
-
2014
- 2014-12-30 KR KR1020140193959A patent/KR102030198B1/en active IP Right Grant
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR19990059802A (en) * | 1997-12-31 | 1999-07-26 | 정몽규 | Car continuously variable transmission |
| KR100298772B1 (en) * | 1997-12-31 | 2001-11-22 | 이계안 | Continuously variable transmission for vehicle |
| KR20050066090A (en) | 2003-12-26 | 2005-06-30 | 현대자동차주식회사 | Multi-plate clutch for an automatic transmission |
| JP2008095748A (en) * | 2006-10-06 | 2008-04-24 | Yanmar Co Ltd | Transmission |
| JP2010096215A (en) * | 2008-10-14 | 2010-04-30 | Mitsubishi Agricult Mach Co Ltd | Traveling change gear of working vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| KR102030198B1 (en) | 2019-10-08 |
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