KR101639593B1 - HydroMechanical Transmission - Google Patents

HydroMechanical Transmission Download PDF

Info

Publication number
KR101639593B1
KR101639593B1 KR1020150047023A KR20150047023A KR101639593B1 KR 101639593 B1 KR101639593 B1 KR 101639593B1 KR 1020150047023 A KR1020150047023 A KR 1020150047023A KR 20150047023 A KR20150047023 A KR 20150047023A KR 101639593 B1 KR101639593 B1 KR 101639593B1
Authority
KR
South Korea
Prior art keywords
ring gear
gear
carrier
sun gear
output
Prior art date
Application number
KR1020150047023A
Other languages
Korean (ko)
Inventor
배명호
김당주
정순배
최성광
김병곤
Original Assignee
(주)대호하이드로릭
(주)스마텍
배명호
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by (주)대호하이드로릭, (주)스마텍, 배명호 filed Critical (주)대호하이드로릭
Priority to KR1020150047023A priority Critical patent/KR101639593B1/en
Application granted granted Critical
Publication of KR101639593B1 publication Critical patent/KR101639593B1/en

Links

Images

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
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members 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
    • 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
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H2047/04—

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The present invention relates to a hydromechanical continuously variable transmission, transmitting power of an engine of a vehicle. The hydromechanical continuously variable transmission comprises: a hydraulic continuously variable transmission; a first planetary gear device; a second planetary gear device; a clutch member; and a brake member. A second ring gear is rotated in the opposite direction to the first ring gear.

Description

[0001] Hydromechanical Transmission [0002]

TECHNICAL FIELD The present invention relates to a continuously variable transmission of a vehicle, and more particularly to a hydraulic-mechanical type continuously variable transmission suitable for a working vehicle such as a tractor or a forklift.

Generally, the type of the continuously variable transmission can be classified according to the power transmission medium.

A belt-type continuously variable transmission using a belt as a power transmission medium transmits power by using a belt connecting a pulley and a pulley. At this time, a constant tension should be maintained on the belt connecting the pulley and the pulley, and a constant frictional force should be applied between the pulley and the belt to prevent slippage.

Therefore, in the conventional belt-type continuously variable transmission, precise power transmission is impossible due to inevitable sliding between the pulley and the belt, energy is wasted due to the constant tension of the belt, regardless of whether the transmission power is large or small. There is a problem that a difference in the electric power capability is generated due to a change in the tension of the belt.

On the other hand, the toroidal type, which uses the adhesive friction force of the oil film formed by contact between the rotating disk and the roller as a medium of power transmission, has an advantage in that the efficiency of transmission of power is high and a relatively large power can be transmitted. The durability and the exclusive lubricating oil for generating the adhesive friction force by the oil film are not economically competitive, but it is possible to transmit relatively large power.

On the other hand, a pure hydraulic type continuously variable transmission is capable of transmitting a high output power under appropriate torque, and is capable of convenient operation with unstable variable in the entire speed range. However, it is unnecessarily heavy, Has a disadvantage that it has low efficiency compared with the basic transmission, and is used in a limited amount in some construction heavy equipment.

In order to compensate for the low efficiency and heavy and bulky volume, which is the disadvantage of such a pure hydrodynamic continuously variable transmission, a mechanical-hydraulic type continuously variable transmission has been developed.

Generally, a hydraulic-mechanical type continuously variable transmission refers to a multi-speed transmission having two or more power transmission paths using a planetary gear device and a hydraulic step-variable transmission.

That is, the output of the engine continuously variable by the hydraulic step-variable transmission and the output of the engine, which is not shifted by the continuously-variable transmission, are synthesized by using the planetary gear device and the synthesized power is selectively transmitted to the axle .

Generally, the prior art has a gear train configured by a plurality of spur gears to be switched to the forward mode and the reverse mode, but this has a problem that it occupies a large volume.

Korean Registered Patent No. 10-1498810 "Stepless Transmission" (registered Feb. 26, 2015) U.S. Pat. No. 4,345,488 entitled "HYDROMECHANICAL STEERING TRANSMISSION" (registered Aug. 8, 1982)

SUMMARY OF THE INVENTION It is an object of the present invention to provide a planetary gear unit capable of switching to a forward mode and a reverse mode by a very simple structure by means of a pair of planetary gear sets, Mechanical < / RTI > continuously variable transmission.

In order to solve the above problems, the present invention provides a continuously variable transmission for transmitting engine power of a vehicle, comprising: a hydraulic type power source for inputting an engine power of a vehicle and continuously outputting the engine power of the vehicle by a hydraulic pump and a hydraulic motor Transmission; A first ring gear, and a plurality of first planetary gears disposed between the first sun gear and the first ring gear and supported by a first carrier, wherein the first sun gear, Wherein the first ring gear is rotated by receiving the engine power of the vehicle which is not subjected to the continuously variable transmission and the first ring gear is rotated by receiving the output of the continuously variable transmission, A first planetary gear device configured to synthesize and output the power input by one carrier; A second sun gear, a second ring gear, and a plurality of second planetary gears disposed between the second sun gear and the second ring gear and supported by a second carrier, Is directly connected to the first ring gear of the first planetary gear unit and is rotated at the same rotation direction and at a rotation speed in response to the output of the first ring gear, and the second ring gear is rotated by the second sun gear A second planetary gear device configured to synthesize and output the power input to the carrier; A clutch member configured to intermittently transmit the rotational force of the first ring gear to the second carrier; A brake member provided for braking the rotation of the second carrier; Wherein the second carrier rotates in the same rotational direction and rotational speed as the first ring gear by the operation of the clutch member so that the second ring gear rotates in the same rotational direction as the first ring gear And the rotation of the second carrier is stopped by the operation of the brake member, whereby the second ring gear rotates in a direction opposite to the first ring gear.

The first sun gear may further include a first sun gear input gear connected via a first sun gear input shaft to receive the output of the hydraulic step-variable transmission, And a first ring gear output shaft which is disposed coaxially with the sun gear input shaft and to which the second sun gear is fixedly coupled.

As described above, the present invention provides a hydraulic-mechanical type continuously variable transmission capable of switching between a forward mode and a reverse mode with a very simple structure by means of a pair of planetary gear sets and a clutch member and a brake member provided therebetween.

1 is a configuration diagram showing a configuration of an embodiment according to the present invention;

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings, which will be readily apparent to those skilled in the art. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. In order to clearly illustrate the present invention in the drawings, portions not related to the description are omitted, and like reference numerals are given to similar portions throughout the specification.

Throughout the specification, when an element is referred to as "comprising ", it means that it can include other elements as well, without excluding other elements unless specifically stated otherwise.

1 is a configuration diagram showing the configuration of an embodiment of the present invention.

One embodiment according to the present invention is an automotive vehicle having an engine 10, first and second planetary gear sets 110 and 120, a hydraulic step-variable transmission 130, a clutch member 140 and a brake member 150, .

The drive input shaft (not shown) rotated by the engine 10 of the vehicle provides rotational power to the hydraulic stepless transmission device 130 while providing rotational force to the first carrier 111r of the first planetary gear set 110 .

The hydraulic power stepless transmission (130) includes at least a hydraulic pump (131) and a hydraulic motor (132). The rotational force of a drive input shaft (not shown) driven by the engine 10 is transmitted to the hydraulic pump 131 through a gear or the like to drive the hydraulic pump 131. The hydraulic pump 131, And the hydraulic motor 132 is driven by the pumping of the fluid by the hydraulic pump 131. As shown in FIG.

Accordingly, the driving ratio of the hydraulic motor 132 to the hydraulic pump 131 can be adjusted by adjusting the pumping capacity of the hydraulic pump 131, and thus the size of the power output from the hydraulic motor 132 can be adjusted have.

As described above, the structure of the hydraulic step-variable transmission 130, which receives the driving force of the engine 10 and continuously shifts the driving force, is already well known in the art, so that the structure of the hydraulic step- A more detailed description of the characteristics will be omitted.

The first planetary gear set 110 includes a first sun gear 110s disposed at the center, a first ring gear 110r disposed in a manner surrounding the first sun gear 110s, And a plurality of first planetary gears 110p positioned between the first ring gear 110s and the first ring gear 110r and supported by the first carrier 110c. Since the structure of the first planetary gear set 110 is a general technology, a detailed description thereof will be omitted.

On the other hand, the first sun gear 110s of the first planetary gear set 110 is rotationally driven by receiving the output of the hydraulic step-variable transmission 130 in which the engine power of the vehicle is continuously changed.

The first sun gear 110s is connected to the first sun gear input gear 112s via the first sun gear input shaft 111s and the first sun gear input gear 112s is connected to the first sun gear input shaft 111s via the first sun gear input shaft 111s, The rotational force is inputted to the first sun gear input gear 112s.

 The first carrier 110c is rotationally driven by receiving the engine power of the vehicle. Namely, the engine power of the vehicle which is not continuously variable is input to the first carrier 110c.

A first carrier input gear 111c is connected to the first carrier 110c and a rotational force output from a drive input shaft (not shown) rotated by the engine 10 of the vehicle is transmitted to the first carrier input gear 111c, .

The first ring gear 110r synthesizes and outputs the power input to the first sun gear 110s and the first carrier 110c as described above. The first ring gear 110r is provided with a first ring gear output shaft 111r disposed coaxially with the first sun gear input shaft 111s.

The second planetary gear set 120 includes a second sun gear 120s arranged in the center, a second ring gear 120r arranged in a manner surrounding the second sun gear 120s, And a plurality of second planetary gears 120p positioned between the second ring gear 120r and the second ring gear 120r and supported by the second carrier 120c. Since the structure of the second planetary gear device 120 is a general technology, a detailed description thereof will be omitted.

On the other hand, the second sun gear 120s of the second planetary gear set 120 receives the output of the first ring gear 110r of the first planetary gear set 110 and is rotated. For this purpose, the second sun gear 120s is fixed to the first ring gear output shaft 111r and rotated.

The rotation of the second carrier 120c is controlled by the clutch member 140 and the brake member 150. [

The clutch member 140 is provided for interrupting the transmission of the rotational force of the first ring gear 110r to the second carrier 120c and the second carrier 120c is rotated by the power transmission of the clutch member 140, The first ring gear 110r is rotationally driven at the same rotational speed as the first ring gear 110r and the rotational force of the first ring gear 110r is transmitted to the second carrier (120c).

The brake member 150 is provided for braking the rotation of the second carrier 120c. That is, the second carrier 120c can be stopped or rotated by the operation of the brake member 150. [

The second ring gear 120r synthesizes and outputs the power input to the second sun gear 120s and the second carrier 120c as described above.

The second ring gear 120r is provided with the second ring gear output gear 121r and the input gear 161 of the output shaft 160 is gear engaged with the second ring gear output gear 121r . The output shaft 160 is connected to an axle or the like.

Of course, the output shaft 160 may be provided with a separate brake member for braking the output shaft 160 according to the embodiment.

The operation of the present embodiment as described above will be described.

The first ring gear 110r of the first planetary gear set 110 is constituted by the first sun gear 110s which is rotatably driven by receiving the output of the hydraulic power stepless transmission 130 in which the engine power of the vehicle is continuously changed, The power of the first carrier 110c to which the engine power of the non-shifted vehicle is input and is rotationally driven is synthesized and output.

At this time, the second ring gear 120r and the output shaft 160 are rotated in the forward mode or the reverse mode according to the operation of the clutch member 140 and the brake member 150 with respect to the rotation of the first ring gear 110r.

That is, when the clutch member 140 is operated, the forward mode is established.

When the clutch member 140 is operated, the rotation speed of the second sun gear 120s and the rotation speed of the second carrier 120c are the same as the rotation speed of the first ring gear 110r, The rotational speed of the first ring gear 110r is equal to the rotational speed of the first ring gear 110r, and the rotational direction thereof is also the same.

Further, when the brake member 150 is operated, the reverse mode is set.

When the brake member 150 is operated, the rotation speed of the second sun gear 120s is equal to the rotation speed of the first ring gear 110r, and the rotation speed of the second carrier 120c is 0 (braking state) The rotational speed of the second ring gear 120r is proportional to the rotational speed of the first ring gear 110r while the rotational direction thereof is opposite.

When the clutch member 140 is operated to rotate the first ring gear 110r as described above, the second ring gear 120r and the output shaft 160 rotate in the forward mode, and when the brake member 150 is operated The second ring gear 120r and the output shaft 160 rotate in the reverse mode.

As described above, the present hydraulic-mechanical type continuously variable transmission is constituted by a pair of planetary gear sets 110 and 120, a clutch member 140 and a brake member 150 provided therebetween, in an advanced mode and a reverse mode To be able to switch.

It will be understood by those skilled in the art that the foregoing description of the present invention is for illustrative purposes only and that those of ordinary skill in the art can readily understand that various changes and modifications may be made without departing from the spirit or essential characteristics of the present invention. will be. It is therefore to be understood that the embodiments described above are intended to be illustrative, but not limiting, in all respects. For example, each component described as a single entity may be distributed and implemented, and components described as being distributed may also be implemented in a combined form.

The scope of the present invention is defined by the appended claims rather than the detailed description and all changes or modifications derived from the meaning and scope of the claims and their equivalents are to be construed as being included within the scope of the present invention do.

10: Engine
110: first planetary gear set 110s: first sun gear
111s: first sun gear input shaft 112s: first sun gear input gear
110c: first carrier 111c: first carrier input gear
110r: first ring gear 111r: first ring gear output shaft
110p: first planetary gear
120: second planetary gear set 120s: second sun gear
120c: second carrier 120r: second ring gear
121r: second ring gear output gear 120p: second planetary gear
130: Hydraulic stepless speed change device 131: Hydraulic pump
132: Hydraulic motor
140:
150: Brake member
160: Output shaft 161: Input gear

Claims (2)

A continuously variable transmission for transmitting engine power of a vehicle, comprising:
A hydraulic step-variable shifting device for continuously inputting the engine power of the vehicle and outputting the engine power of the vehicle by the hydraulic pump and the hydraulic motor;
A first ring gear, and a plurality of first planetary gears disposed between the first sun gear and the first ring gear and supported by a first carrier, wherein the first sun gear, Wherein the first ring gear is rotated by receiving the engine power of the vehicle which is not subjected to the continuously variable transmission and the first ring gear is rotated by receiving the output of the continuously variable transmission, A first planetary gear device configured to synthesize and output the power input by one carrier;
A second sun gear, a second ring gear, and a plurality of second planetary gears disposed between the second sun gear and the second ring gear and supported by a second carrier, Is directly connected to the first ring gear of the first planetary gear unit and is rotated at the same rotation direction and at a rotation speed in response to the output of the first ring gear, and the second ring gear is rotated by the second sun gear A second planetary gear device configured to synthesize and output the power input to the carrier;
A clutch member configured to intermittently transmit the rotational force of the first ring gear to the second carrier;
A brake member provided for braking the rotation of the second carrier;
And,
The second carrier rotates in the same rotational direction and rotational speed as the first ring gear by the operation of the clutch member so that the second ring gear rotates in the same rotational direction and rotational speed as the first ring gear ,
And the rotation of the second carrier is stopped by the operation of the brake member, whereby the second ring gear rotates in the opposite direction to the first ring gear.
The method according to claim 1,
Wherein the first sun gear further comprises a first sun gear input gear connected via a first sun gear input shaft to receive the output of the hydraulic step-variable transmission, wherein the first ring gear is connected to the first sun gear input shaft Further comprising a first ring gear output shaft which is coaxially arranged and to which said second sun gear is fixedly coupled.
KR1020150047023A 2015-04-02 2015-04-02 HydroMechanical Transmission KR101639593B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020150047023A KR101639593B1 (en) 2015-04-02 2015-04-02 HydroMechanical Transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020150047023A KR101639593B1 (en) 2015-04-02 2015-04-02 HydroMechanical Transmission

Publications (1)

Publication Number Publication Date
KR101639593B1 true KR101639593B1 (en) 2016-07-14

Family

ID=56499336

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020150047023A KR101639593B1 (en) 2015-04-02 2015-04-02 HydroMechanical Transmission

Country Status (1)

Country Link
KR (1) KR101639593B1 (en)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4382392A (en) * 1977-04-16 1983-05-10 Zahnradfabrik Friedrichshafen Ag Hydromechanical transmission with power branching
US6663525B1 (en) * 2002-07-17 2003-12-16 Case Corporation Hydro-mechanical transmission with automatic braking capability and method of operation
JP2005114160A (en) * 2003-09-16 2005-04-28 Komatsu Ltd Control system for hydro-mechanical transmission
JP2007321771A (en) * 2006-05-30 2007-12-13 Jatco Ltd Shifting mechanism for stepped automatic transmission
KR101498810B1 (en) 2013-09-03 2015-03-04 엘에스엠트론 주식회사 Continuously variable transmission

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4382392A (en) * 1977-04-16 1983-05-10 Zahnradfabrik Friedrichshafen Ag Hydromechanical transmission with power branching
US6663525B1 (en) * 2002-07-17 2003-12-16 Case Corporation Hydro-mechanical transmission with automatic braking capability and method of operation
JP2005114160A (en) * 2003-09-16 2005-04-28 Komatsu Ltd Control system for hydro-mechanical transmission
JP2007321771A (en) * 2006-05-30 2007-12-13 Jatco Ltd Shifting mechanism for stepped automatic transmission
KR101498810B1 (en) 2013-09-03 2015-03-04 엘에스엠트론 주식회사 Continuously variable transmission

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
미국 등록특허 4,345,488 "HYDROMECHANICAL STEERING TRANSMISSION" (1982. 8.24. 등록)

Similar Documents

Publication Publication Date Title
US10088026B2 (en) Ball type CVT with output coupled powerpaths
US9052000B2 (en) Ball type CVT/IVT including planetary gear sets
EP2971864B1 (en) Split power infinitely variable transmission architecture
EP3206903B1 (en) Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low part count
JP5058992B2 (en) Ratio limiter
US9644721B2 (en) Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges and low variator load at vehicle launch
US9039559B2 (en) Electric drive for a motor vehicle
JP2015527551A5 (en)
JP2015527552A5 (en)
CN106337920B (en) Double clutch continuously variable transmission
EP2882982A1 (en) Infinitely-variable transmission for a vehicle
EP3206901B1 (en) Split power infinitely variable transmission architecture incorporating a planetary type ball variator with multiple fixed ranges
US6561942B2 (en) Dual mode variable ratio transmission
KR20160035328A (en) Continuously variable transmission for vehicles
RU2484333C1 (en) Multirange continuously variable transmission (versions)
KR101639593B1 (en) HydroMechanical Transmission
US10309506B2 (en) Multiple-mode continuously variable transmission
JPH10246305A (en) Continuously variable transmission
WO2015114873A1 (en) Power-dividing continuously variable transmission
JP4072531B2 (en) Power split type continuously variable transmission
WO2016061496A1 (en) Split power infinitely variable transmission architecture incorporating a planetary type ball variator with low variator loading at vehicle launch
KR0154076B1 (en) Cvt for a vehicle
KR20130106567A (en) Hydro-mechanical transmission for commercial vehicle
SU120109A1 (en) Planetary gearless transmission
KR20030017866A (en) continuous variable transmission for vehicle

Legal Events

Date Code Title Description
E701 Decision to grant or registration of patent right
GRNT Written decision to grant
FPAY Annual fee payment

Payment date: 20190514

Year of fee payment: 6