WO1980001153A1 - Systeme de transmission d'energie bidirectionnel - Google Patents

Systeme de transmission d'energie bidirectionnel Download PDF

Info

Publication number
WO1980001153A1
WO1980001153A1 PCT/US1978/000177 US7800177W WO8001153A1 WO 1980001153 A1 WO1980001153 A1 WO 1980001153A1 US 7800177 W US7800177 W US 7800177W WO 8001153 A1 WO8001153 A1 WO 8001153A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
source
drive
inlets
valve
Prior art date
Application number
PCT/US1978/000177
Other languages
English (en)
Inventor
W Blake
Original Assignee
Caterpillar Tractor Co
W Blake
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 Caterpillar Tractor Co, W Blake filed Critical Caterpillar Tractor Co
Priority to PCT/US1978/000177 priority Critical patent/WO1980001153A1/fr
Priority to JP50125978A priority patent/JPS55500953A/ja
Priority to IT26812/79A priority patent/IT1124660B/it
Priority to ES486364A priority patent/ES486364A1/es
Publication of WO1980001153A1 publication Critical patent/WO1980001153A1/fr
Priority to EP19790900945 priority patent/EP0020363A1/fr

Links

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
    • F16H61/065—Smoothing ratio shift by controlling rate of change of fluid pressure using fluid control means
    • F16H61/067—Smoothing ratio shift by controlling rate of change of fluid pressure using fluid control means using an accumulator
    • 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
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0284—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof characterised by valve arrangements supplying fluid to a two chamber- cylinder
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • F16H61/0272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals characterised by initiating reverse gearshift

Definitions

  • This invention relates to a bidirectional power transmission system, and more specifically, to such a system wherein there is included a hydraulically en ⁇ gaged clutch for controlling the directional output of the system.
  • each of the clutches in the assembly will be formed of a clutch pack which may be compressed by a hydraulic piston when hydraulic fluid under pressure is applied against the piston.
  • the clutch may brake a ring gear in a planetary gear set and, of course, the system will include means where ⁇ by both clutches cannot be simultaneously engaged.
  • the systems will usually include some sort of pressure modulating device interconnecting a source of
  • OMPI ⁇ WIPO hydraulic fluid under pressure such as a pump' and a valve which is utilized to select the direction of the assembly output, that is, control the engagement of one or the other of the clutches.
  • the modulating means is typically a modulating relief valve and frequently, the same do not modulate pressure build-up to the desired extent, particularly at relatively low pressures.
  • "grabbing" in the clutch pack will occur rather than smooth en- gagement as desired.
  • This is communicated to components connected to the output of the clutch assem ⁇ bly as well as components therein and produces consider ⁇ able shock. Shock, in turn, reduces the useful life of such components causing premature wear and failure thereof.
  • a bidirectional power transmission system including a bidirectional, hydraulically engaged clutch adapted to be coupled to a source of rotary power and to a rotary drive and having two hydraulic inlets, each for receiving hydraulic fluid under pressure, one to engage the clutch to cause one direction of rotation of the drive and the other to engage the clutch to cause the opposite rotation of the drive, a source of hy ⁇ draulic fluid under pressure, a directional control valve interconnecting the source and one or the other of the inlets, and a hydraulic pressure modulating de ⁇ vice connected between the source and the valve, the improvement including accumulator means connected to each of the inlets between the clutch and the valve. Each receives hydraulic fluid under pressure when the valve is directing fluid to an associated inlet for modulating pressure build-up therein to thereby provide smooth clutch engagement to minimize shock in the drive
  • Fig. 1 is a schematic of a bidirectional power transmission system made according to one embodiment of the invention
  • Fig. 2 is a graph illustrating the pressure rise in a prior art system
  • Fig. 3 is a graph similar to that of Fig. 2 but illustrating the pressure rise in a system made accord ⁇ ing to the embodiment of the present invention.
  • FIG. 1 An exemplary embodiment of a bidirectional, power transmission system made according to the invention is illustrated in Fig. 1 and is seen to be used in con ⁇ nection with an engine 10 having a rotary output shown schematically at 12. Ultimately, the engine 10 is to provide rotary power to a driven element 14.
  • the driven element 14 includes a rotary input 16, shown schematicall .
  • the clutch assembly 18 is for providing direction control in a conventional fashion.
  • the same includes a forward clutch, generally designated 20, and a reverse clutch, generally designated 22.
  • a forward clutch 20 When the forward clutch 20 ⁇ s engaged, both the output 12 and the input 16 will be rotating in the same direction while when the reverse clutch 22 is engaged, the input 16 will be driven in a direction oppositely that of the output 12.
  • Each of the clutches 20 and 22 is comprised of a clutch pack including interleaved clutch disks.
  • ' Clutch disks 24 are, for example, splined to the housing 25 of " the assembly 18 while alternate ones of the clutch disks 26 may be splined, for example, to the radially outer surface of a ring gear in a conventional fashion.
  • Each clutch 20 and 22 includes a hydraulic piston 28 by which the pack comprising the disks 24 and 26 may be compressed. When such occurs, the disks 26 are no longer free to rotate thereby braking the associated ring gear. Disengagement of each clutch 20 and 22 is typically provided for by the use of a spring (not shown) biasing the associated piston 28 away from the pack. Hydraulic fluid under pressure may be directed to each of the pistons 28 through associated inlets 30 and 32 in the assembly 18 from a source 34 in the form of a hydraulic pump. Typically, but not always, the pump 34 will be driven by the engine 10.
  • the output of the pump 34 is connected to a modu ⁇ lating means in the form of a conventional modulating relief valve 36.
  • the modulating relief valve 36 is operative to control the rate of pressure increase from the pump 34 but inherent in its construction is an inability to provide such control at relatively low pressures. For example, for a maximum pressure of about 300 psi, smooth pressure build-up provided by the modulating relief valve 36 can generally only be obtained from about 45-50 psi on upward to the maximum system pressure.
  • Hydraulic fluid under pressure from the valve 36 is conveyed via a conduit 38 to a direction selector spool valve 40 of conventional construction.
  • the valve 40 can route hydraulic fluid under pressure to the in ⁇ lets 30 via a line 42, to the inlet 32 via a line 44, or to neither.
  • the forward clutch 20 will be engaged while when fluid under pressure is applied to the line
  • An accumulator is connected to each of the lines 42 and 44 and serves to modulate pressure build-up in each line over the lower part of the range of system pressures.
  • the accumulator acts over that part of the range wherein the valve 36 is ineffective to provide for smooth engagement of the clutches at low pressures, that is, during initial engagement.
  • the accumula ⁇ tors are defined by a single, opposed spring accumulator, generally designated ' 46.
  • the same includes a body 48 having a bore 50 therein.
  • a piston 52 is slidable with- in the bore 50 and divides the same into two chambers 54 and 56.
  • the piston 52 carries a seal 58 so as to isolate the chambers 54 and 56 from each other.
  • Addi ⁇ tionally, oppositely directed stops 60 project axially from both ends of the piston 52.
  • both of the springs 62 have substantially identical spring rates .
  • the system is completed by a line 64 connecting the chamber 54 to the line 42, and thus to the inlet
  • valve 40 In operation, when it is desired to engage the forward clutch 20, the valve 40 will be shifted appro ⁇ priately to route fluid under pressure from the line 38 to the line 42.
  • the valve 40 will include means whereby, for such a configuration, the line 44 will be connected to the hydraulic reservoir of the system. Fluid will flow through the line 42 through the inlet 30 to encounter the piston 28 for the forward clutch 20. The piston 28 will begin to move to engage the forward clutch pack. As the clutch pack begins to compress, resistence toward further movement of the piston 28 will increase resulting in pressure in the line 42 elevating. Such elevating pressure will result in the piston 52 in the accumulator 46 moving to the left against the bias of the leftmost spring 62. And, as the spring 62 compresses, it will offer increasing resistence to such movement of the piston 52.
  • the chamber 54 which varies in volume as the piston 52 moves will receive some of the ' fluid from the pump 34 thereby modulating the pressure build-up in the line 42 so that the pressure build-up is gradual, in a large part, controlled by the value of the spring 62 resisting leftward movement of the piston 52.
  • the modulating relief valve 36 takes over and there will be a relatively smooth increase, shown at C, up to the maximum system pressure, for example, 300 psi.
  • the piston 52 of the accumulator will be shifting and at about 45 psi, it will be at the end of its stroke, one or the other of the stops 60 abutting the end of the bore 50 to which it is adjacent.
  • the exemplary embodiment of the invention provides a further ad ⁇ vantage in terms of minimizing spacial requirements for the components thereof.
  • the unique construction of the accumulator 46 provides for accumulators for both inlet ports in a single structure thereby con ⁇ siderably reducing the amount of space that would be required if two separate accumulators, one for each inlet, were employed.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

Un systeme de transmission d'energie bidirectionnel comprend un embrayage hydraulique bidirectionnel (18) adapte pour etre accouple a une source d'energie rotative (10) et a un entrainement rotatif (14) et ayant deux entrees hydrauliques (30, 32) chacune recevant du fluide hydraulique sous pression, l'une (30) pour engager l'embrayage pour une direction de rotation de l'entrainement et l'autre (32) pour engager l'embrayage dans la direction opposee de rotation de l'entrainement, une source (34) de fluide hydraulique sous pression, une soupape de commande de direction (40) connectant entre elles la source et l'une ou l'autre des entrees, un dispositif de modulation de pression hydraulique (36) connecte entre la source et la soupape, l'amelioration comprenant un accumulateur (46) connecte a chacune des entrees entre l'embrayage et la soupape pour recevoir le fluide hydraulique sous pression lorsque la soupape dirige le fluide vers l'entree associee.
PCT/US1978/000177 1978-11-29 1978-11-29 Systeme de transmission d'energie bidirectionnel WO1980001153A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/US1978/000177 WO1980001153A1 (fr) 1978-11-29 1978-11-29 Systeme de transmission d'energie bidirectionnel
JP50125978A JPS55500953A (fr) 1978-11-29 1978-11-29
IT26812/79A IT1124660B (it) 1978-11-29 1979-10-26 Sistema di trasmissione di coppia bidirezionale particolarmente per veicoli a motore
ES486364A ES486364A1 (es) 1978-11-29 1979-11-27 Perfeccionamientos en sistemas de transmision de fuerza bi- direccional para vehiculos utilizados en la construccion y similares
EP19790900945 EP0020363A1 (fr) 1978-11-29 1980-06-17 Systeme de transmission d'energie bidirectionnel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
WOUS78/00177 1978-11-29
PCT/US1978/000177 WO1980001153A1 (fr) 1978-11-29 1978-11-29 Systeme de transmission d'energie bidirectionnel

Publications (1)

Publication Number Publication Date
WO1980001153A1 true WO1980001153A1 (fr) 1980-06-12

Family

ID=22141285

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1978/000177 WO1980001153A1 (fr) 1978-11-29 1978-11-29 Systeme de transmission d'energie bidirectionnel

Country Status (5)

Country Link
EP (1) EP0020363A1 (fr)
JP (1) JPS55500953A (fr)
ES (1) ES486364A1 (fr)
IT (1) IT1124660B (fr)
WO (1) WO1980001153A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102650092A (zh) * 2012-04-01 2012-08-29 重庆乾合科技有限公司 一种新型的编机离合器及其改进方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3541791A (en) * 1968-09-06 1970-11-24 Kiva Yakovlevich Lvovsky Hydraulic device for controlling the actuating cylinders of the gearshift friction clutches and brakes of self-propelled vehicles,mainly tractors
US3896705A (en) * 1974-01-21 1975-07-29 Clark Equipment Co Pressure feedback system
US3905459A (en) * 1972-09-13 1975-09-16 Reintjes Eisenwerke Hydraulically actuated plate clutch with accumulator
US4000795A (en) * 1976-03-29 1977-01-04 Clark Equipment Company Apparatus for controlling the pressure of a fluid fed to a clutch
US4023444A (en) * 1973-07-25 1977-05-17 Aisin Seiki Kabushiki Kaisha Pressure control circuit for use in automatic transmission of vehicle

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3541791A (en) * 1968-09-06 1970-11-24 Kiva Yakovlevich Lvovsky Hydraulic device for controlling the actuating cylinders of the gearshift friction clutches and brakes of self-propelled vehicles,mainly tractors
US3905459A (en) * 1972-09-13 1975-09-16 Reintjes Eisenwerke Hydraulically actuated plate clutch with accumulator
US4023444A (en) * 1973-07-25 1977-05-17 Aisin Seiki Kabushiki Kaisha Pressure control circuit for use in automatic transmission of vehicle
US3896705A (en) * 1974-01-21 1975-07-29 Clark Equipment Co Pressure feedback system
US4000795A (en) * 1976-03-29 1977-01-04 Clark Equipment Company Apparatus for controlling the pressure of a fluid fed to a clutch

Also Published As

Publication number Publication date
IT1124660B (it) 1986-05-14
JPS55500953A (fr) 1980-11-13
ES486364A1 (es) 1980-05-16
EP0020363A1 (fr) 1981-01-07

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Designated state(s): CH DE FR GB SE