CN101743413A - Manual transmission - Google Patents

Manual transmission Download PDF

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Publication number
CN101743413A
CN101743413A CN200880024633A CN200880024633A CN101743413A CN 101743413 A CN101743413 A CN 101743413A CN 200880024633 A CN200880024633 A CN 200880024633A CN 200880024633 A CN200880024633 A CN 200880024633A CN 101743413 A CN101743413 A CN 101743413A
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CN
China
Prior art keywords
pump
throttle
manual transmission
rotor
pressure
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.)
Pending
Application number
CN200880024633A
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Chinese (zh)
Inventor
沃尔弗拉姆·哈泽文德
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.)
Magna Powertrain GmbH and Co KG
Original Assignee
Magna Powertrain GmbH and Co KG
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Filing date
Publication date
Application filed by Magna Powertrain GmbH and Co KG filed Critical Magna Powertrain GmbH and Co KG
Publication of CN101743413A publication Critical patent/CN101743413A/en
Pending legal-status Critical Current

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    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • 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
    • F16D31/00—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution
    • F16D31/02—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution using pumps with pistons or plungers working in cylinders
    • 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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
    • F16D48/066—Control of fluid pressure, e.g. 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
    • F16D2048/0221—Valves for clutch control systems; Details thereof
    • 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
    • F16D2048/0224—Details of conduits, connectors or the adaptors therefor specially adapted for clutch control
    • 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
    • F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
    • F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
    • F16D2048/0236—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation with multiple independent pumps, e.g. one per clutch, or for supplying fluid to different systems
    • 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
    • F16D2048/0281—Complex circuits with more than two valves in series or special arrangements thereof not provided for in previous groups
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/102—Actuator
    • F16D2500/1021—Electrical type
    • F16D2500/1023—Electric motor
    • F16D2500/1024—Electric motor combined with hydraulic actuation
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/104—Clutch
    • F16D2500/10443—Clutch type
    • F16D2500/1045—Friction clutch
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/108—Gear
    • F16D2500/1081—Actuation type
    • F16D2500/1082—Manual transmission
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/108—Gear
    • F16D2500/1087—Planetary gearing
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/30—Signal inputs
    • F16D2500/302—Signal inputs from the actuator
    • F16D2500/3024—Pressure
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/70—Details about the implementation of the control system
    • F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
    • F16D2500/70402—Actuator parameters
    • F16D2500/7041—Position
    • 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
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/70—Details about the implementation of the control system
    • F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
    • F16D2500/70464—Transmission parameters
    • F16D2500/70488—Selection of the gear ratio
    • 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
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0818—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts comprising means for power-shifting
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • 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
    • 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
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4043—Control of a bypass valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Control Of Transmission Device (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention relates to a manual transmission comprising an input shaft, a first mechanical transmission branch and a second mechanical transmission branch which can both be coupled in a driving manner to the input shaft on the input side and to a common output shaft on the output side by means of different gear steps. Said manual transmission also comprises a first pump and a second pump, both comprising a stationary or rotary pump part, a rotor, a suction chamber and a pressure chamber. A rotary movement of the rotor in relation to the stationary or rotary pump part allows a hydraulic fluid to be transported from the suction chamber into the pressure chamber of each pump, the rotor of the first pump being connected to the first mechanical transmission branch in a driving manner, and the rotor of the second pump being connected to the second mechanical transmission branch in a driving manner. A driving torque transmitted by the input shaft to the mechanical transmission branch is proportional to the pump pressure generated by the respective pump, at least one pressure control device being associated with the pumps, by which means a fluid flow transported by the pumps can be variably throttled in order to vary the rotational speed of the rotor for a gear step shift, in relation to the stationary or rotary pump part of each pump.

Description

Manual transmission
Technical field
The present invention relates to the manual transmission of Motor Vehicle, it comprises input shaft and the first mechanical transmission branch road and the second mechanical transmission branch road, described mechanical transmission branch road can be bonded to input shaft effectively drivingly at input end, and can be bonded to shared output shaft by different gear stage at output terminal.
Background technique
The tradition speed changer allows to shift gears under the zero load condition that drives power cut, this speed changer also is power-shift transmission, thereby has the change that a plurality of binding members and actuator can be carried out gear stage usually, the change of described gear stage is difficult to be noted for the driver of Motor Vehicle, and therefore makes the people comfortable.Utilize this power-shift transmission, what use in automobile usually is double-clutch speed changer, and the control of this shift process does not wish it is complicated.
Summary of the invention
Basic goal of the present invention provides a kind of manual transmission, and described speed changer can be shifted gears when load is arranged, but can not make driving comfort be subjected to the destruction of shift process.The parts that this speed changer is required and the control of manual transmission should be tried one's best simple and sound.Manual transmission should further be designed to, and can realize the multiple driving environment of Motor Vehicle, and not need to increase specific features for this reason.
This target realizes by the technical characteristics in the claim 1.
Mention as beginning, manual transmission has the first mechanical transmission branch road and the second mechanical transmission branch road among the present invention, described transmission branch road can input end effectively drivingly (antriebswirksam) be bonded to input shaft, and be bonded to shared output shaft by different gear stage at output terminal.Manual transmission further comprises first and second pumps, and they all have pump portion, rotor, suction chamber and pressure chamber static or that rotate.By rotor with respect to static or rotate the rotation of pump portion, hydraulic fluid can input to the pressure chamber of respective pump from suction chamber, wherein the rotor of first pump is connected to the first mechanical transmission branch road effectively drivingly, and the rotor of second pump is connected to the second mechanical transmission branch road effectively drivingly.The driving torque that transfers to the mechanical transmission branch road from input shaft is proportional to the pumping pressure that respective pump produces.At least one pressure control device is associated with described pump, and is changed the ground throttling by the fluid stream that described pump is carried by described pressure control device, for the change of gear stage changes rotor with respect to the static of respective pump or rotate the rotational velocity of pump portion.
Therefore manual transmission comprises two mechanical transmission branch roads that separate among the present invention, especially has the transmission branch road of spur wheel or epicyclic train, and described transmission branch road is respectively applied for the specific gear stage that forms manual transmission.For example, the first transmission branch road can form the odd number gear stage, and the second transmission branch road can be provided for the formation of even number gear stage and reverse gear.
Manual transmission further comprises first pump and second pump among the present invention, they respectively with two transmission branch roads in corresponding one be associated.Input shaft can be controlled by pump with the combining of effective driving of corresponding transmission branch road, promptly, by a transmission branch road (getriebezweig) or by two transmission branch roads (especially on gear changes), the driving torque of input shaft can be transferred to output shaft on demand.For this reason, the rotor of first pump is connected to the first mechanical transmission branch road (for example, the regularly rotary or connection indirectly by direct geared) effectively drivingly, and the rotor of second pump is connected to the second mechanical transmission branch road effectively drivingly.
If can there be the difference of rotational velocity between the rotor of the pump portion of static or rotation setting and pump, hydraulic fluid is delivered to pressure chamber from the suction chamber of pump so.Quantity delivered depends on the difference of rotational velocity between the geometrical shape of pump and pump portion and the rotor.Yet, must consider dominant back pressure in pressure chamber, conveyance fluid because pump can not resist any required high-intensity back pressure.The back pressure of opposing pump power is controlled in the intervention of feed flow that therefore can be by hydraulic fluid, and the back pressure effect influences combining of rotor and static or rotation pump portion conversely.The driving torque that transfers to the mechanical transmission branch road from input shaft promptly directly is proportional to pumping pressure, described pumping pressure is based on the transmission capacity of respective pump on the one hand and effectively produces, and is based on the intervention of pressure control device on the other hand and effectively produces.
Based on the change of gear stage, torque transfer has to move to another transmission branch road from a transmission branch road, and the rotational velocity of rotor is had to respect to the static of respective pump or rotated pump portion and change.Control to the change of gear stage is carried out by pressure control device, and for example by one or more throttles, in this way, the flow of pump is changed the ground throttling, and therefore can influence the transmission branch road effectively drives the degree that combines with input shaft.
Because corresponding mechanical transmission branch road only is connected in the rotor of corresponding pump, described rotor can be made has little radially area, so corresponding mechanical transmission branch road has relatively little rotary inertia.It is fast especially that therefore the change of gear stage can carry out ground, and the synchronizer that has little peak torque with low cost can be used in the mechanical transmission branch road.
The control of manual transmission can be based on the control (for example hydraulic control) of easy realization among the present invention.Therefore omitted complicated and/or friction clutch expensive and easy to wear and their executive system, for example traditional double clutch system.In addition, in manual transmission of the present invention, because big rotational velocity difference between input shaft (engine speed) and the output shaft (rotating speed approaches zero when Motor Vehicle is static), and the heat that produces the start up period of speed change output can be derived by hydraulic fluid.Finally, the fluid that acts on mechanical bond has been simplified the design of the cooling of speed changer so in fact therefore simultaneously as freezing mixture.Therefore corresponding pump satisfies triple functions substantially, be respectively hydraulic fluid conveying, be used for the torque transfer purpose hydrostatic in conjunction with and coolant feed.Manual transmission of the present invention needn't be set to the corresponding part of reply particular condition under startup or gearshift situation.Do not need independent coolant pump yet.
Preferred embodiment among the present invention is described in independent claims, specification and accompanying drawing.
Among the embodiment of manual transmission, described pump can hydraulically be blocked by pressure control device, corresponding rotor roughly rotary regularly (promptly without any obvious slip) be connected in the static of respective pump or rotate pump portion.As indicated above, pump can not be resisted any required high-intensity back pressure and conveyance fluid.For example, the outflow of hydraulic fluid can be interrupted because of the blocking-up of pressure chamber, so hydrodynamic pressure increases until rotor no longer with respect to static or to rotate pump portion removable in the pressure chamber.Described subsequently pump is hydraulically blocked by a kind of liquid column, and rotor is connected in pump portion in the rotary fixing mode of cardinal principle.Owing to leak, between corresponding rotor and the pump portion slight slip will take place for example in this process.This slight slip or even be required is in particular for preventing the total mechanically deformation (so-called corrosion (eingraben)) of parts (driving that for example long-continued gearless level changes) under the long-term load of high strength.
And can further do such preparation,,, promptly cancel active drive different between rotor and the pump portion and connect or combination hydraulically with the pump short circuit by pressure control device so that corresponding rotor breaks away from from the static of respective pump or rotation pump portion.Hydraulic pressure short circuit can be understood as the zero load of respective pump.Therefore pump can not produce any pumping pressure or minimum pumping pressure is only arranged.The difference that therefore can have required arbitrarily rotational velocity between pump portion and the rotor.Based on the difference of the rotational velocity between pump portion and the rotor, subsequently fluid roughly directly and almost unpowered loss ground be drawn into the suction chamber of pump from pressure chamber.Combination between rotor and the respective pump portion is correspondingly enough little.
For example may need this situation, promptly corresponding mechanical transmission branch road should be broken away from, and does not just have torque to transfer to output shaft from input shaft by this transmission branch road or by one of its gear stage.For this reason, pressure control device especially has first control valve that is associated with first pump and second control valve that is associated with second pump.Directly connecting the pressure chamber of respective pump and the corresponding short-circuit line of suction chamber can selectively open or block by controlled valve.Alleged short-circuit line is especially walked around the cooling unit of manual transmission, and described short-circuit line preferably only extends (for example pump case) in corresponding pump portion.Therefore power loss and drag torque have correspondingly been avoided largely.
According to another embodiment of manual transmission of the present invention, pressure control device comprises at least one controllable throttle, by this throttle, and can be by the fluid stream that first pump and/or second pump are carried by throttling.As indicated above, fluid stream and pumping pressure thus can be controlled with the combination degree between the respective pump portion that rotor and respective pump are set by throttle, have changed the driving torque that transfers to the mechanical transmission branch road thus.Throttle can be for example horizontal movably poroid barrier film or axially movable slide block, and the conical end of described slide block forms fixing valve.
Can do such preparation, throttle can be bonded to the pressure chamber of first pump selectively or be bonded to the pressure chamber of second pump.In other words, in this embodiment, it is necessary having only an independent throttle, and it can be bonded in two pumps one selectively.Do like this and can not stop throttle to break away from from two pumps.In this embodiment, being used to control the required number of components of manual transmission of the present invention further reduces.
The further improvement of manual transmission in according to the present invention, the pressure chamber of respective pump can directly be bonded to the corresponding suction line of pump by throttle, promptly without any need for the plug-in type service pump and walk around pump sump simultaneously.Promptly under the certain operations condition, need to carry a large amount of fluid streams, especially carry with tangible rotational velocity difference.Therefore can reduce to be used to provide the size of the feed pump of fluid pressure minimum and balance leakage loss greatly.Alleged pressure chamber combines with the direct of suction line, and the especially direct combination by throttle is in or carries out along the same parts of pump (static or rotate pump portion or rotor).Therefore can save the high pressure swivel coupling that is used for pump.
In the textural favourable and compact embodiment of manual transmission, throttle is located at static or is rotated pump portion.Wherein pump portion is rotatable with respect to rotatingshaft, the throttle of being located at pump portion can be guided to and make its direction of actuation extend perpendicular to the rotatingshaft that rotates pump portion, and wherein throttle is arranged so that the centrifugal force of the rotation that acts on pump portion supports opening of throttle.This has represented extra secure context.
Throttle can have inlet opening, first delivery outlet and second delivery outlet, and wherein the inlet opening communicates with the pressure chamber of at least one pump.First delivery outlet is by along static or rotate first connecting line that pump portion extends and directly communicate with the suction chamber of at least one pump, and second delivery outlet communicates with the suction chamber of at least one pump by second connecting line along the cooling unit extension.Flow resistance reduces because of direct be connected of first delivery outlet with the suction chamber of at least one pump with the power loss of following them.On the contrary, therefore cooling unit needn't be located at static or rotate pump portion, but for example is located at the stationary housings of torque transfer device, that is, in this case, the second alleged connecting line extends along the stationary housings of speed changer at least in part.Therefore realized the raising of cooling capacity.
According to further improvement, throttle is arranged so that respectively and can be controlled by throttle through the part hydraulic fluid of delivery outlet outflow that described hydraulic fluid flows into throttle.In other words, manual transmission can more effectively be operated by the controlled distribution that the throttle of flowing through flow to the hydraulic fluid of delivery outlet.For example can do such preparation, in particular case, a large amount of hydraulic fluids is supplied to first delivery outlet so that the power loss in the torque transfer device is reduced to minimum, and on the contrary, in other situation, a large amount of hydraulic fluids is supplied to second delivery outlet, for example when hydraulic fluid should be further cooled.
More preferably, the first throttle valve and second throttle can be provided with shared valve housing, and wherein throttle has shared second delivery outlet.If two throttles are arranged to the mechanical forced guiding and are matched, so that first throttle valve and second throttle can not close simultaneously, and this respect is favourable so.Blocking-up when therefore having prevented two pumps.
Embodiment according to this throttle, under the closed condition of first throttle valve, the valve gate of first throttle valve of delivery outlet that is used to close the first throttle valve is with the gate pier of closing of the valve gate that acts on second throttle, described second throttle is used for the closing of delivery outlet of second throttle, and vice versa.
Pressure control device is controlled, the feasible first mechanical transmission branch road that only is transferred to respect to selected gear stage by the driving torque of input shaft transmission, or only be transferred to the second mechanical transmission branch road, or be used for gear stage and change and transfer to two mechanical transmission branch roads with respect to other selected gear stage.Therefore can between the mechanical transmission branch road, distribute driving torque fully changeably in the mode of pressure control device by the control of corresponding pump.
Therefore the rotor of pump preferably is connected to corresponding mechanical transmission branch road effectively drivingly, and does not need the intervention of friction clutch, has saved parts and has simplified control to manual transmission.
According to the embodiment of the invention, the respective pump portion of parts is rotatable equally.In this structure, pump is as " hydrostatic clutch " between input shaft and the transmission branch road.For example, based on the blocking-up of a pump, transmit by the rotation of the shaft-driven rotatable pump of input portion rotor by corresponding transmission branch road.These " hydrostatic clutches " can infinitely be adjusted between extreme case " transmission of driving torque " and " disengaging ".
Especially advantageously further improve according to textural, the rotary pump portion that is fixedly connected to second pump of the pump portion of first pump, especially one-body molded with the pump portion of second pump.
According to another embodiment of manual transmission of the present invention, first pump and second pump have shared suction chamber, have so just simplified the structure of manual transmission, have reduced manufacturing expense and have improved the efficient of pump.
According to the preferred embodiment of manual transmission of the present invention, at least one pump is peripherally surrounded by annular chamber (especially by corresponding suction chamber or shared suction chamber), roughly fully is filled with hydraulic fluid in the described chamber.Peripherally surround corresponding pump oil seal and therefore form, it causes favourable acoustic damping.First pump and second pump all be preferably by hydraulic fluid at least vertically section peripherally surround.
Alternatively or extraly, suction chamber has annular chamber, described annular chamber externally for example laterally and/or is radially surrounded by the elastic ring wall at least in part, and described elastic ring wall allows the suction chamber capacity to change based on the hydrodynamic pressure of suction chamber inside.The preferred variant of annular wall is to be arranged to annular enclosure, and it is formed by metallic envelope or metal expansion pipe at least in part.
Elasticity suction chamber border produces the pressure storage, and described pressure is stored in the generation of the air pocket that helps to stop hydraulic fluid between other object, for example when the variation in pressure that happens suddenly occurs in the suction chamber.
According to another embodiment of manual transmission of the present invention, corresponding differential gear is associated with two mechanical transmission branch roads.This respect, the input of corresponding differential gear is bonded to input shaft, and first output of corresponding differential gear is bonded to the rotor of respective pump.Second output of corresponding differential gear is bonded to corresponding mechanical transmission branch road.In this embodiment, pump is configured to " hydrostatic break ", and it can the support drive torque.For example, based on the blocking-up of a pump, first output of differential gear is blocked.Therefore drive the transmission branch road by input shaft with rotational velocity corresponding to the gear graduation ratio of differential gear.However, if the formation of the rotational velocity difference between pump portion and the rotor can be reduced by the pressure in the pressure chamber and produce, will influence torque transfer and rotational velocity ratio between mechanical transmission branch road and the input shaft so." hydrostatic break " also can infinitely be adjusted between extreme case " rotor blocking-up " and " rotor zero load ".
Corresponding differential gear is especially formed by planetary pinion.Can further do such preparation, the pump portion of pump is set with sleep mode.This embodiment is especially simple aspect structure, because pump integral body is not rotated, has so also simplified its control.
Further improvement according to manual transmission of the present invention, the input shaft and the first and second mechanical transmission branch roads are permanently bonded to each other, as explained above, be variable equally in conjunction with the driving torque transmitted wherein and depend on the serviceability of pump by this type of.
Alleged static or rotation pump portion is preferably pump case.Alternatively, if alleged pump portion is provided with rotationally, so alleged pump portion can be another rotor of respective pump.
Pump is preferably made simple pump, promptly is not the hydrostatic device with pump or duty of engine.In this case, therefore pump can not drive on own hydrostatic ground.If pump is not to make the variable-displacement pump, have the fixedly pump of maximum delivery but make the pump with constant geometrical shape, especially revolution, be preferred so.In other words, the quantity delivered of revolution is can be not adjustable because of the stroke of piston that changes, but pump is used for carrying with given rotational velocity the hydraulic fluid of same amount basically.Therefore do not provide controlled and geometrical shape transformable pump.These features make pump have the effect of the design of special simplification and economy, after especially combining with one another.
More preferably, pump is a radial piston pump.
According to preferred embodiment, electric installation is connected in pump portion or two pumps rotor of at least one effectively drivingly, can transmit the mechanical transmission branch road of driving torque independently to internal-combustion engine, described internal-combustion engine is bonded to input shaft, or can pass through mechanical transmission branch road of generator brake.
Preferred embodiment according to manual transmission of the present invention, control unit is provided, pass through control unit, pressure control device and gear stage actuator can controlledly be used to be changed to more senior, when the gear stage of the first mechanical transmission branch road chosen, therefore the gear stage of the second mechanical transmission branch road is chosen, and first pump is still hydraulically blocked, and second pump is by short circuit hydraulically; The flow of second pump is little by little limited then, is roughly fully transmitted by the second transmission branch road until driving torque; First pump is released certain flow then, and the rotational velocity of input shaft reduces; And then, second pump is hydraulically blocked.The release of the certain flow of the first alleged pump can be realized by the opening gradually of relevant portion of pressure control device (for example throttle), or alternatively be realized by the instant hydraulic pressure short circuit of first pump.The reducing of difference of the rotational velocity between the input shaft and the second mechanical transmission branch road depended in the reduction of the rotational velocity of alleged input shaft.This process can be realized that especially wherein simultaneously, the engine load signal in the engine management of Motor Vehicle reduces, and therefore engine torque reduces by the further restriction of the flow of second pump.
Be changed to lower gear stage and show opposite order execution greatly.
Description of drawings
With reference to preferred embodiments and drawings, only the present invention is described below in the mode of example.Shown in it:
Fig. 1 is the embodiment's of manual transmission among the present invention schematic representation;
Fig. 2 is the sectional view of radial piston pump;
Fig. 3 to Fig. 6 is the different conditions of pressure control device among the manual transmission embodiment among the present invention;
Fig. 7 is the embodiment of twin throttle door;
Fig. 8 is a manual transmission embodiment's of the present invention partial sectional view;
Fig. 9 is the sectional view perpendicular to the plane of Fig. 8 of the embodiment among Fig. 8;
Figure 10 to Figure 12 is the schematic representation of the different preferred embodiment of manual transmission of the present invention; And
Figure 13 be used for input shaft and hydrostatic pump combine and with the planetary pinion that combines of mechanical transmission branch road.
Embodiment
Fig. 1 illustrates the embodiment of manual transmission 10 of the present invention.The LEFT HAND SIDE towards the engine (not shown) of Motor Vehicle of manual transmission 10 comprises by the input shaft 12 of engine driving to rotate.Rotate nonuniformity and introduce the power system of the Motor Vehicle that comprises manual transmission 10, and cause rotating the formation of vibrations by engine.Input shaft 12 has torque damper 14 to reduce the rotation vibrations.
Input shaft 12 is connected to first and second hydrostatic pumps 18,20 with common housing 16 at the speed change end.The housing 16 rotary input shafts 12 that are bonded to regularly.
Pump 18,20 has rotor 22 and 24 (as shown in Figure 2) respectively, and its rotor 22 is rotary to be fixedly connected to the first mechanical transmission branch road 26, and the rotor 24 rotary second mechanical transmission branch roads 28 that are fixedly connected to.
The first transmission branch road 26 comprises tubular axis 30, permanent rotary speed change gear G1 and the G3 of being fixedly connected to of described tubular axis.In addition, speed change gear G5 and G7 can be by the rotary tubular axis 30 that is fixedly connected to of synchronizer 32 selectivity.
In a similar fashion, the second mechanical transmission branch road 28 comprises variable-speed shaft 34, and described variable-speed shaft is permanent rotaryly to link to each other with speed change gear G2 regularly, and described variable-speed shaft can pass through synchronizer 32, selectively is bonded to speed change gear G4.In addition, gear r is secured to variable-speed shaft 34 and engages with speed change gear R, can form reverse gear by speed change gear R.
Manual transmission 10 further comprises countershaft 36, and described countershaft has eight gears 38.Four gears 38 in centre in eight gears 38 can be by the rotary countershaft 36 that is bonded to regularly of synchronizer 32 selectivity.Other four gears can the permanent rotary countershaft 36 that is bonded to regularly.
By the actuating of corresponding gear stage actuator (not shown in figure 1), synchronizer 32 can be axially displaced so that form six forward gear levels (corresponding to gear G1 to G6) and a reverse gear (R) in known manner.Formation for first gear stage, for example, the LEFT HAND SIDE synchronizer 32 of countershaft 36 is introduced into and is close to engaging of countershaft 36 dexter gears 38, so that the rotation of tubular axis 30 can transfer to countershaft 36 by speed change gear G1, and finally transfer to the output shaft 40 of manual transmission 10, and therefore transfer to other element of Motor Vehicle power system (not shown) by speed change gear G6.Other gear stage of manual transmission 10 forms in a similar fashion.
The driving torque that to explain input shaft 12 below is how to utilize manual transmission 10, transfers to tubular axis 30 and/or variable-speed shaft 34 by rights.
For example, if even number gear stage (the second, the 4th or the 6th gear) or reverse gear are chosen, the torque of input shaft 12 must be transferred to variable-speed shaft 34 so.If the odd number gear stage is chosen, so just driving torque need be transferred to tubular axis 30.If should carry out the variation of gear stage, the drive path of torque also must change so.In this respect, the part of driving torque is transmitted by two mechanical transmission branch roads 26,28 with being spaced apart, and wherein corresponding driving torque transfer part changes during gear stage changes.The variation of this type of gear stage also should be able to take place when load is arranged, and should turn round as far as possible lenitively, so driving comfort just can not stop or similar negative satellite phenomenon and reducing because of neglecting of Motor Vehicle is moving suddenly.
This process can realize by the use of two hydrostatic pumps 18,20.For example, rotor 24 can be blocked about housing 16 by the control of pump 18,20, and the rotor 22 that is associated with transmission branch road 26 breaks away from housing 16.In this case, the torque of input shaft 12 is fully transferred to variable-speed shaft 34 by pump 20.But, also can control the rotation that hydrostatic pump 18,20 so that rotor 22,24 only partly are bonded to housing 16.
Therefore do not need to carry out and change the friction clutch of the torque that transfers to mechanical transmission branch road 26,28.This distribution is only carried out by pump roughly the same on the function 18,20.
On behalf of a class, radial piston pump be particularly suitable for being used in pump in the manual transmission 10.Explain the operation of radial piston pump 20 below with reference to Fig. 2, Fig. 2 illustrates the section of radial piston pump 20.Shown in radial piston pump 20 can also be except its pumping function substantially as engine or power operation, promptly it can rotate by controlled force applications.But, owing to pumping function-is promptly only arranged based on the conveying of the hydraulic fluid of the rotational velocity difference between pump case 16 and the rotor 22,24-be important, so only consider the aspect that is used to understand radial piston pump 20 of manual transmission 10.In other words, can be used in manual transmission 10 with the simplification version of radial piston pump 20 shown in the mode of example, and because the structure of its simplification but preferred.
Shown in radial piston pump 20 comprise rotor 24, described rotor has annular peripheral in the zone of pump 20, center 44 that wherein should annular is with respect to shared rotatingshaft 46 skews of housing 16 and rotor 24 or the variable-speed shaft 34 that is associated.In other words, rotor 24 is eccentric elements.Rotor 24 drives with five pistons 48 and links to each other, and described piston has piston cavity 50 respectively.Based on the rotation of rotor 24 with respect to housing 16, the capacity of piston cavity 50 alternately increases by size and reduces.In other words, the hydraulic fluid of the valve 52 of at first flowing through, by the rotation of rotor 22 with respect to housing 16, be forced through once more subsequently another valve 52 of respective pistons 48 '.Therefore, hydraulic fluid is transported to pressure chamber (not shown) with valve 52 ' be communicated with from the suction chamber (not shown) that is communicated with valve 52.Valve 52,52 ' can be the simple safety check of the passive fixed valve form in the Simple pump 20 (not having the hydraulic engine function).
In the situation shown in Fig. 2, because piston cavity 50 has minimum capacity at first, hydraulic fluid is inhaled in the piston 48 of cylinder 51a of radial piston pump 20 based on rotating counterclockwise of rotor 24 at first.The piston 48 of cylinder 51b and 51c also is in sucting stage.In a single day corresponding piston chamber 50 reaches maximum capacity, because the effect that rotor 24 rotates, the capacity of piston cavity 50 will reduce once more, and promptly hydrodynamic pressure increases.Based on the increase of pressure, close automatically as the valve 52 of safety check effect.The capacity of piston cavity 50 will further reduce owing to the further rotation of rotor 24, and hydraulic fluid continues to be pressurized, until reaching certain threshold level, valve 52 ' (for example ball valve that is loaded by spring force) opens and hydraulic fluid spews out into pressure chamber, and be not shown.
Described Fig. 2 by way of example, supposed that wherein housing 16 can not store (gelagert) with being rotated.But the quantity delivered that is very easy to find hydraulic fluid only depends on the rotational velocity difference between housing 16 and the rotor 24.In other words, when housing 16 rotates with identical speed with rotor 24, there is not hydraulic fluid to be transferred.
About Fig. 2, also should be noted that in essence the pump 18 of same type can be arranged to shown in pump 20 axial dipole fields, wherein outstanding two pump 18,20 can have common housing 16 (comparison diagram 1).But two pumps 18,20 have suction chamber that is associated and the pressure chamber that separates accordingly respectively.
In the application of radial piston pump 20 described here, the most important conveying that needs not to be hydraulic fluid, but controlled combination of housing 16 and rotor 22,24.To the backward of the operating principle of reciprocating pump 20 radially, can realize that wherein the conveying of hydraulic fluid is stoped intentionally based on above-mentioned.If promptly pump 20 can not be through any hydraulic fluid of valve 52 ' discharge, rotor 24 just no longer rotates with respect to housing 16 so.Therefore cancellation combination when allowing the conveying of hydraulic fluid once more.
In Fig. 1 independently the distribution of the driving torque of the input shaft 12 of mechanical transmission branch road 26,28 transmission therefore roughly based on the pressure control of the hydraulic fluid of carrying by pump 18,22 or the pumping pressure that exists based on the pressure chamber end.Fig. 3 illustrates the embodiment's of pressure controller 53 schematic representation.
Fig. 3 illustrates pump 18,20. Pump 18,20 be connected to pressure line 54 or 54 ' (pilot pressure rank) respectively and be connected to suction line 56,56 '.In various situations, all exist pressure line 54,54 ' and suction line 56,56 ' between respectively by short-circuit line 58 and 58 ' direct the connection.The short-circuit line 58 that is associated with pump 18 can be selectively by valve V1 blocking-up, and this state is corresponding to the switching state 0 (closing) of valve V1.If valve V1 opens, be switching state 1 (opening) so.Same valve V2 is associated with pump 20.
Suction line 56,56 ' " link to each other, wherein suction line 56 " is provided with safety check 60, hydraulic fluid filter 62 and swivel coupling 66 by shared suction line 56 with hydraulic control unit (HCU) 64.When pump 18,20 and the pipeline 54,56,58 and 54 that is associated respectively with them and valve V1, V2 ', 56 ', 58 ' (the pivot region R of dotted line top when rotating O), just need swivel coupling 66, and other parts of the following controller that will partly describe 53 are with static form setting (the stagnant zone S of dotted line below).
Guide line 68 can be by hydraulic control unit 64 superchargings, and with can be by the mode of pilot pressure, control valve V1 and V2 control throttle D1 and D2 (its function will be explained hereinafter) on the other hand on the one hand.For security reason, hydraulic valve V1 and V2 are arranged so that when pilot pressure and reduce to certain threshold level when following that described hydraulic valve is converted to open mode (switching state 1).
The pump 70 that links to each other with motor M is the hydraulic fluid of hydraulic control unit 64 supply superchargings, and wherein motor M is controlled by speed Control unit (TCU) 72 electric power.Pump 70 extracts hydraulic fluid from sump 74, and sump 74 also links to each other with hydraulic control unit 64.
The pressure line 54,54 ' respectively of pump 18,20 has throttle D1 and D2, and described throttle can be by hydraulic control unit 64 controls.Throttle D1 is associated with pump 18, and throttle D2 is associated with pump 20.Pressure line 54,54 ' open at shared pressure line 54 " (supercharging rank), described pressure line 54 " then being connected to suction line 56 ".At pressure line 54 " scope in, be provided with heat exchanger 76, it serves the reduction of the temperature of hydraulic fluid.
Shown under the state, valve V1, V2 are in switching state 1, promptly corresponding suction line 56,56 ' and pressure line 54,54 ' by corresponding short-circuit line 58,58 ' by short circuit.Since hydraulic fluid can be pulled into their suction side from the pressure end of pump 18,20 based on the difference of rotational velocity, the housing 16 of pump 18,20 and rotor 22,24 are just broken away from.Thereby rotor 22,24 can freely rotate, except drag torque; Manual transmission 10 is in unloaded state.
If first gear stage is chosen, if and the driving torque of engine should fully be transmitted by the first mechanical transmission branch road 26, the then rotary rotor 22 that is fixedly connected to first pump 18 of tubular axis 30 must be blocked about housing 16, the described housing 16 rotary input shafts 12 (comparison diagram 1) that are fixedly connected to.For this reason, valve V1 shown in Figure 3 (switching state 0) and throttle D1 must fully close.Because the blocking-up of pressure line 54, will produce very high pressure at the pressure chamber end of first pump 18, so that rotor 22 and housing 16 rotate together.Therefore pump 18 is blocked by hydraulic pressure.As shown in Figure 3, opposite second pump 20 is positioned at short-circuit condition (V2 switching state 1).
Below with reference to accompanying drawings 1 to Fig. 3 and from the variation of first gear stage to the second gear stage, the operation of manual transmission 10 is described.
Because second pump 20 is by short circuit, new gear stage can be chosen by the synchronizer 32 that is associated, i.e. the rotary variable-speed shaft 34 that is fixedly connected to of the speed change gear G2 of the second mechanical transmission branch road 28.
From open mode,, facilitate control so by 28 pairs of part driving torques of the second transmission branch road because valve V2 is closed (switching state 0) and throttle D2 is closed continuously.The pressure line 54 of second pump 20 ' in pressure increase by throttle D2 throttling, wherein because the engine speed and the rotational velocity of output shaft 40 ad initio roughly is held, it is identical that the quantity delivered of described second pump keeps substantially.Along with the throttling enhancing of throttle D2, cumulative driving torque is transmitted by the second mechanical transmission branch road 28, and is reduced to identical degree by the driving torque of the first transmission branch road, 26 transmission.During this stage of handoff procedure, the rotor 24 of the housing 16 and the second transmission branch road 28 still rotates with different speed.Otherwise the rotor 22 of the first transmission branch road 26 continues to rotate with housing 16 because of the lasting blocking-up of pressure line 54.
Finally, because throttling, reach following this state, promptly since the second transmission branch road because of the gear graduation of the enhancing of the combination cumulative between rotor 24 and the housing 16 and second gear stage than changeing sooner, so total driving torque mainly is transmitted by the second transmission branch road 28.Engine speed can initiatively reduce now, and wherein the reduction of engine speed is supported by closing gradually of throttle D2.In order to prevent the phase mutual interference of two transmission branch roads 26,28, the short circuit of first pump 18 by the startup (switching state 1) of valve V1, and therefore the first transmission branch road 26 breaks away from from input shaft 12, and wherein said interference is corresponding to the different engine speed based on different gear graduation ratios.Because to the release of blocking-up before first pump 18, driving torque needn't be fully by 28 transmission of the second transmission branch road; For the quick engine speed (being the rotational velocity of input shaft 12) that reduces, even need still to pass through the specific residual torque that the first transmission branch road 26 transmits.
Because the closing fully of throttle D2, at pipeline 54 ' locate to form high pressure, this high pressure makes rotor 24 roughly fully about housing 16 blocking-up of second pump 20.First gear is broken away from by the actuating of corresponding synchronous device 32 subsequently or simultaneously.Therefore the variation of gear stage finishes.
The blocking-up of the hydraulic pressure short circuit of pump 18,20 and/or hydraulic pressure also can only be carried out by throttle D1, D2 substantially, wherein short-circuit line 58,58 ' can be omitted.
The variation of the gear stage between other gear changes is carried out in a similar fashion.Showing opposite order greatly from higher gear stage to the variation of lower gear stage carries out.
Can be clear and definite by above description, therefore the controller 53 of manual transmission 10 can fully save friction clutch.Only simple valve V1 and V2 and throttle D1 and D2 need control by rights.Described control is more powerful, economy and simplified design.
In addition, the advantage of traditional power manual transmission has formed the original state of manual transmission 10, that is, and and in this state, the housing 16 of pump 18,20 accelerates to rotate (engine speed), and selected transmission branch road 26,28 is not done any rotation because Motor Vehicle is static.Therefore have a bigger rotational velocity difference between housing 16 and corresponding rotor 22,24, it causes pump 18 and 20 to have big quantity delivered respectively, and causes pump 18 and 20 heat increase respectively.As indicated above, but in this respect, the hydraulic fluid of conveying is respectively away from pump 18 and 20 and carry.The used heat that pump 18 and 20 produces respectively could be derived by heat exchanger 76 with effective and efficient manner.Therefore do not need extra parts in the motor vehicle starting stage.Therefore one of advantage of manual transmission 10 comprises following actual conditions very at large, and also under normal circumstances, the cooling of binding member (being pump 18,20) is carried out by actuating fluid itself and be therefore very effective.Do not need independent coolant pump.
Fig. 4 illustrates another embodiment of pressure controller 53.This embodiment only has independent throttle D, its can by conversion valve U selectively with two pumps 18,20 in one of be associated.Embodiment's shown in Figure 3 simplification is possible, because throttle D only need be used for one control in two pumps 18,20 of gear variation.
Fig. 5 illustrates another variant of pressure controller 53.Throttle D is set at the stagnant zone S of controller 53 in this embodiment, and is controlled by speed Control unit 72 electric power.Therefore save hydraulic control line 68, and can save complicated and/or expensive swivel coupling 66.
Shown in Figure 5 equally, hydraulic control unit 64 can also be carried out extra work, for example, and to the control of the hydraulic actuating clutch 78 of the switching that is used for full wheel drive.Therefore can know, in the hydraulic system of existing Motor Vehicle, the enforcement of controller 53 can be not only simply but also design neatly, by basic existing parts, for example pump 70, filter 62, sump 74 and similarly parts realize the use of controller 53.
Another embodiment of pressure controller shown in Fig. 6 53.Different with above-mentioned variant is, short-circuit line 58,58 ' and valve V1 and V2 is not set.Throttle D1 and D2 be located at pressure line 54 and 54 ' in, and described throttle has input HP1, HP2 respectively, and is different from Fig. 3 to throttle D1 and D2 shown in Figure 5, they have two outputs separately.The input HP1 of throttle D1 is connected to the pressure line 54 of pump 18, and the input HP2 of throttle D2 be connected to the pressure line 54 of pump 20 '.In all cases, the first output R2 of first of the throttle D1 output R1 and throttle D2 passes through safety check 60 at pivot region R OIn directly with the suction line 56,56 of pump 18,20 ' link to each other.Especially corresponding connecting line along or roll-shell 16 in, extend the corresponding second output LPO of throttle D1, D2, the corresponding suction line 56,56 of and pump 18,20 indirect ' link to each other by heat exchanger 76.Corresponding connecting line extends in stagnant zone S, that is, along or in the stationary housings of speed changer, extend.Hydraulic control signal is provided to throttle D1, D2 by control pipeline 66.
Therefore throttle D1, the D2 in the present embodiment also has the function of valve V1 and V2 except the function with throttling own, and the structure of pressure controller 53 and control are simplified.The quantity of especially required swivel coupling 66 reduces because of this structure.
As surround as shown in the empty frame of throttle D1, D2, preferably, throttle D1, D2 are combined into twin throttle door D '.With reference to Fig. 7 the embodiment of twin throttle door D ' is described below.
Fig. 7 illustrates the sectional view of twin throttle door D '.Yet described twin throttle door D ' does not have the safety check 60 in the empty frame that is included in Fig. 6.The triangle of input HP1, the HP2 that is associated with twin throttle door D ' and output R1, R2, LPO is represented the flow direction of the hydraulic fluid of the respective openings of flowing through.
Twin throttle door D ' roughly have valve housing 100 and two valve gates 110,110 provided thereon ', they have formed throttle D1 and D2 jointly.The throttle D2 that opens fully among Fig. 7 receives the hydraulic fluid of being carried through input HP2 by pump 20, and described hydraulic fluid is drawn out of once more at output R2 place, and is supplied to the suction chamber of pump 20.Because the extraction of the fluid at output R2 place, have only a spot of hydraulic fluid to overflow through the shared output LPO of throttle D2 and throttle D1.Therefore, hydraulic fluid is roughly remained on the pivot region R of this position of throttle D2 (as shown in Figure 6) OTherefore the place so as to short flow path is provided, and reduces to minimum by pressure controller 53 caused tractive resistances.In other words, throttle D2 is pump 20 short circuits, and has the function of short-circuit line 58 in the foregoing description.
As shown in Figure 7, D2 is opposite with throttle, and throttle D1 closes fully.Flowing from input HP1 to the fluid of exporting LPO and/or R1 blocked by valve gate 110, and this just causes the blocking-up of pump 18, so pump 18 transfers to rotor 22 with torque from housing 16.
Valve gate 110,110 ' the position can change the elastic force of described pilot pressure antagonistic spring 112,112 ' applied and acting on by the pilot pressure that changes among guide line 68 and the 68a.Throttle D1, D2 can activate substantially independently of one another.Therefore, yet, close in the time of two throttle D1, D2 and therefore two pumps 18,20 time blocking-up be prevented from.Valve gate 110 ' and 110 towards corresponding another valve gate 110,110 ' end have gate pier extension part 114,114 ', described extension part 114,114 ' size design must make valve gate 110,110 ' end protrude the center of output cavity 116 that is in closed condition and is located at the front end of output LPO of crossing.In valve D1, D2 one is restricted, and another valve D1 or D2 be when closing, and this security feature just is even more important.Throttle down lock 110,110 ' subsequently valve gate 110 that another is limited ' or 110 extrude from its position, so that corresponding pump 20 or 18 no longer is blocked respectively.
To in handoff procedure, explain the operation of twin throttle door D ' below.
As described above, the throttle D1 that the pump that is in starting period 18 shown in Fig. 7 is closed blocks, and torque transfers to the first mechanical transmission branch road 26 from engine thus.After handoff procedure, torque should be transmitted by the second transmission branch road 28.
After the required gear stage of the second transmission branch road 28 was chosen, throttle D2 activated, and valve gate 110 ' moving to the right, output R2 initially closes thus.Therefore the fluid of being carried by pump 20 overflows by output LPO, and leaves pivot region R OFlow path based on hydraulic fluid extends begins to produce drag torque, yet this drag torque is difficult to be recognized at first.Last valve gate 110 ' approaching control edge 118 ', this just means that pressure increases in pump 20, and the part of the increase of driving torque correspondingly is transmitted by pump 20.Derived by output LPO by the hydraulic fluid of carrying by the heat that energy produced that pump 20 increases, and by being shifted out once more in the fluid of heat exchanger 76 from stagnant zone S.
Before throttle D2 closed fully, throttle D1 opened, promptly the pilot pressure in the guide line 68 be reduce and/or the pressure in guide line 68a increase, on the right of being moved under the effect of spring 112 so as to valve gate 110.Throttle D2 close fully and be not strict the time coordination that begins between opening of throttle D1 because after pump 20 has received most driving torque, in the pressure line 54 of pump 18 low pressure is only arranged.The control of throttle D1, D2 is simplified more, and described throttling has secondary (quadratische) characteristic substantially.Correspondingly, do not have basically fluid flow through throttle D1 opening output LPO and overflow.
Throttle D1 is opened rapidly now, and throttle D2 closes now fully.In this process, carry out the required compensation of rotational velocity difference of transmission branch road 26,28, this rotational velocity difference is caused by the different speed change gear level of selected gear stage.At last, the gear stage of the first transmission branch road 28 can be broken away from now, finishes so as to the variation of gear stage.
Usually, all above-mentioned switch valves by name, control valve and throttle D, V can both be hydraulically, electrically, electromagnetic ground or with any alternate manner control.
Fig. 8 illustrates the partial sectional view that the embodiment's of manual transmission 10 structure is implemented.Two pumps 18,20 have shared rotation storage housing 16 shown in figure the right.Pump 18 and 20 rotor 22,24 are connected to corresponding axle 30,34 respectively.
The extension part that projects to the left side 120 of housing 16 hold the pressure line 54,54 of twin throttle door D ' and pump 18,20 ' segmentation and suction line 56,56 ' segmentation.In other words, twin throttle door D ' is integrated in the housing 16.
In case of transmission 122, in all cases, at stagnant zone S, by swivel coupling 66, the output LPO of twin throttle door D ' is connected to pressure line 54 ", and input R1, R2 are connected to suction line 56 ".Swivel coupling 66 also is provided for control pipeline 68.Be connected to the suction line 56,56 of the pump 18,20 of output R1 and R2 ' link to each other respectively with shared suction chamber 124.For clearer, all elements of twin throttle door D ' are not all to go out with designated, however except valve gate 110,110 ' the details of hydraulic actuating aspect, the twin throttle door roughly twin throttle door D ' with shown in Figure 7 is identical.
Pump 18,20 and the integrity compactness of controlling their twin throttle door D ' are provided with the circulation that allows short flow path to be used for the fluid under pump 18,20 unloaded states, and the flow path of described weak point can the minimized drag torque.This structure is sound more and simplifies.
To be the flow path that embodiment describes hydraulic fluid with pump 20 below, wherein the existence of the rotational velocity difference between variable-speed shaft 34 and the housing 16 be necessary.
When rotor 24 from shown in position when shifting out, hydraulic fluid is through valve 52 sucking-off and entering in the piston 48 from suction chamber 124.Based on being rotated further of rotor 24, the hydraulic fluid that is arranged in piston 48 now is pressurized, surpass the elastic force of valve 52 ' medi-spring until the pressure of hydraulic fluid, thus valve 52 ' open and hydraulic fluid can be through the input HP2 of pressure line 54 ' inflow twin throttle door D '.As indicated above, most of fluid is supplied once more by output R2 and suction line 56 ' quilt and is got back to suction chamber 124.Some fluids also can overflow through output LPO, and can " be provided to heat exchanger 76 by pipeline 54.The hydraulic fluid of deriving can pass through pipeline 56, and " and swivel coupling 66 feeds back to pivot region R again O
Two pump 18,20 shared suction chambers 124 are formed in the annular chamber that peripheral direction surrounds pump 18,20, and are filled with hydraulic fluid along the periphery in described chamber.Suction chamber 124 is surrounded by pump case 16 on the one hand, is surrounded by annular enclosure 126 on the other hand.Annular enclosure 126 is elastic cuff, especially is made of metal, for example metal expansion pipe.The steel plate of two corresponding shapings is connected by flange and is welded together, for example the center tie point that extends along peripheral direction.Alternately, for example, can provide one-time formed annular enclosure, it has at least one elastic sidewall (at the elastic annular wall of radial direction extension) and roughly stiff cover surface (axially extended roughly stiff annular enclosure).Therefore the capacity of suction chamber 124 is independent of rotational velocity more, because under action of centrifugal force, suction chamber 124 does not almost have to increase or only have small increase.
The use of annular enclosure 126 has many good qualities.Especially because the resiliency characteristics of annular enclosure 126, suction chamber 124 can play the pressure storage, whereby, for example prevent the fluid air pocket, otherwise described air pocket will produce because of variation in pressure bigger in the suction chamber 124, for example because of there being an operation suddenly in the bigger rotary speed difference different time pump 18,20 between the rotor 22,24 of correspondence and the housing 16.Air pocket will cause the damage of parts and hydraulic fluid between other element, and therefore must avoid as much as possible.
Because hydraulic fluid peripherally surrounds pump 18,20, and therefore form the oil sealing of peripheral closure, annular enclosure 126 has further improved the cooling of fluid, and reduced the generation of noise, also reduced the aerodynamic force loss, even without the elastic design of illustrated annular enclosure 126, these advantages also can realize.
Any bubble that exists in the fluid in the suction chamber 124 inwardly radially is pushed by centrifugal force, and because of shape inclined-plane, roof 128 accumulates in the entry end of ventilation duct 130, so gas can overflow by Ventilating valve 132.
Deviate from embodiment shown in Figure 8, twin throttle door D ' can be arranged to rotate 90 ° with respect to rotatingshaft 46, so that described centrifugal force is supporting the motion of opening of throttle D1, D2.
Fig. 9 illustrates the sectional view of housing extension portion 120 along AA ' line, and wherein the details of twin throttle door D ' is not shown.Fig. 9 schematically show pressure line 54,54 in the extension part 120 ' and suction line 56,56 ' exemplary setting, suction line 56,56 ' linked together wherein, because they all be connected to pump 18,20 shared suction chamber 124, and therefore suction line 56,56 ' in always have identical pressure.Can also see that from Fig. 9 in all cases, in the embodiment shown, pump 18,20 all has five pistons because correspondingly exist five pressure lines 54,54 '.And pump 18,20 also can have the piston of varying number.
Figure 10 illustrates manual transmission 10 and also can drive linked together in simple mode with mixed power.The part from housing 16 to the right of manual transmission 10 is corresponding to the described embodiment of Fig. 1 above.Its left-hand component, then provide the torque damper 14 of uniting with clutch 78.Therefore manual transmission 10 can be separated with the engine (not shown), so that driving torque can be produced on housing 16 by electric motor 80.Electric motor 80 also can be as generator to produce electric energy during braking.
Figure 11 illustrates another embodiment of manual transmission 10, once more corresponding to embodiment's shown in Figure 1 major part.The rotor of electric motor or generator 80 is at this rotary tubular axis 30 that is bonded to the first transmission branch road 26 regularly.In this case, just can save clutch 78.
Figure 12 illustrates another embodiment of manual transmission 10, and wherein pump 18,20 is arranged between the mechanical transmission branch road 26,28.This embodiment has also united the mixed power driving in simple mode.
Figure 13 illustrates the Another Application possibility of the hydrostatic pump 18,20 that belongs to invention thinking of the present invention.Pump 18,20 is without any the shared rotary housing that is fixedly attached to input shaft 12.Pump 18,20 corresponding housings 16 are fastening with static mode institute on the contrary, promptly do not rotate.The driving torque of input shaft 12 transfers to mechanical transmission branch road 26,28 by planetary pinion 82.The central gear 84 of corresponding planetary pinion 82 is on this rotary respectively rotor 22 or 24 that is fixedly connected to the pump 18,20 that is associated.Mechanical transmission branch road 26,28 is rotary to be bonded to corresponding planetary carrier 86 regularly, and planet wheel 88 rotates and is stored in planetary carrier 86.The driving torque of input shaft 12 transfers to corresponding annular gear 90.Planet wheel 88 is meshed with corresponding central gear 84 and with ring gear 90.Planetary pinion 82 also nature can be constructed to be different from the make of describing by way of example here.
In this embodiment, rotor 22,24 can be braked or fixed position tightly by their corresponding central gears 84 as so-called " break " effect.Planetary pinion 82 is therefore as the different gears of the driving torque that is used to transmit input shaft 12.If a quilt in the pump 18,20 is hydraulically blocked, and another is by short circuit hydraulically, and the driving torque of input shaft 12 is fully transmitted by the mechanical transmission branch road 26 and 28 that is associated with the pump 18,20 of blocking-up respectively so.This embodiment is equally also controlled by the described pressure controller 53 of reference Fig. 3 to Fig. 5.Yet aspect structure, there is advantage,, simplified the guiding (f ü hrung) of guide line 68 like this because pump case 16 is not rotated.
Reference numerals list
10 manual transmissions (schaltgetriebe)
12 power shafts
14 torque dampers
16 housings
18,20 hydrostatic pumps
22,24 rotors
26,28 machine driving branch roads
30 tubular axis
32 sychronisations
34 variable-speed shafts
G1-G7, R speed change gear
R, 38 gears
36 countershafts
40 output shafts
44 rotor centers
46 rotatingshafts
48 pistons
50 piston cavity
The 51a-e cylinder
52,52 ' valve
53 controllers
54,54 ', 54 " pressure lines
56,56 ', 56 " suction lines
58,58 ' short-circuit line
60 safety check
62 filters
64 hydraulic control units
66 swivel couplings
68,68a guide line
70 pumps
72 speed Control unit
74 sumps
76 heat exchangers
78 clutches
80 electric motors/generator
82 planetary pinions (planetengetriebe)
84 central gears
86 planetary carriers
88 planet wheels (planetenrad)
90 ring gears
100 valve housings
110,110 ' valve gate (ventilschieber)
112,112 ' spring
114,114 ' gate pier extension part (anschlagfortsatz)
116 output cavities
118,118 ' control edge
120 housing extension portion
122 case of transmissions
124 suction chambers
126 annular enclosures
128 inclined-planes
130 ventilation ducts
132 Ventilating valves
V1, V2 valve
D, D1, D2 throttle
D ' twin throttle door
HP1, the input of HP2 throttle
R1, R2, the output of LPO throttle
The U conversion valve
The M motor
R OPivot region
The S stagnant zone
AA ' line

Claims (34)

1. manual transmission, has input shaft (12), the first and second mechanical transmission branch roads (26,28), described mechanical transmission branch road can be bonded to input shaft (12) effectively drivingly at input end, and at output terminal by different gear stage (G1, G2, G3, G4, G5, G6, G7, R) be bonded to shared output shaft (40) effectively drivingly, and described manual transmission has first and second pumps (18,20), described pump has static respectively or rotates pump portion (16), rotor (22,24), suction chamber and pressure chamber, wherein hydraulic fluid is by rotor (22,24) static or rotate the rotation of pump portion (16) with respect to described, and from corresponding pump (18,20) described suction chamber transfers to described pressure chamber, the rotor (22) of wherein said first pump (18) is connected to the first mechanical transmission branch road (26) effectively drivingly, and the rotor (24) of described second pump (20) is connected to the second mechanical transmission branch road (28) effectively drivingly, wherein driving torque is based on by corresponding pump (18,20) pumping pressure that is produced and transfer to described mechanical transmission branch road (26 from described input shaft (12), 28), wherein at least one pressure control device and pump (18,20) be associated, thus by pump (18,20) the fluid stream of Shu Songing can be changed the ground throttling, thereby change rotor (22,24) with respect to corresponding pump (18, the rotational velocity of static or rotation pump portion (16) 20) is to be used for the change of gear stage.
2. manual transmission according to claim 1, it is characterized in that, described pump (18,20) can hydraulically be blocked by pressure control device (53), to be fixedly connected to the static of respective pump (18,20) or to rotate pump portion (16) corresponding rotor (22,24) is roughly rotary.
3. manual transmission according to claim 1 and 2, it is characterized in that, described pump (18,20) can be by pressure control device (53) short circuit hydraulically, so that corresponding rotor (22,24) is broken away from from the static of respective pump (18,20) or rotation pump portion (16).
4. manual transmission according to claim 3, it is characterized in that, described pressure control device has first control valve (V1) that is associated with first pump (18) and second control valve (V2) that is associated with second pump (20), by described valve, the short-circuit line that correspondingly connects described pressure chamber and described suction chamber (58) of respective pump (18,20) can be selectively opened or block.
5. according to the described manual transmission of above-mentioned each claim, it is characterized in that, described pressure control device comprises at least one controllable throttle (D, D1, D2), by described throttle, can be by the fluid stream that described first pump (18) and/or described second pump (20) are carried by throttling.
6. manual transmission according to claim 5 is characterized in that, described throttle (D) can optionally be bonded to the pressure chamber of described first pump (18) or the pressure chamber of described second pump (20).
7. according to claim 5 or 6 described manual transmissions, it is characterized in that the pressure chamber of respective pump (18,20) can directly be bonded to corresponding suction line (56 ") of pump by described throttle (D, D1, D2).
8. according to each described manual transmission among the claim 5-7, it is characterized in that described throttle (D, D1, D2) is set at described static or rotation pump portion (16).
9. manual transmission according to claim 8 is characterized in that, described pump portion (16) is rotatable with respect to rotatingshaft (46); And wherein said throttle (D, D1, D2) has the direction of actuation perpendicular to rotatingshaft (46) setting of described rotatable pump portion (16), and wherein said throttle (D, D1, D2) is configured to make the centrifugal force of the rotation that acts on pump portion (16) to support opening of described throttle (D, D1, D2).
10. according to each described manual transmission among the claim 5-9, it is characterized in that, described throttle (D, D1, D2) has inlet opening (HP1, HP2), first delivery outlet (the R1, R2) and second delivery outlet (LPO), wherein said inlet opening and at least one pump (18,20) pressure chamber links to each other, wherein said first delivery outlet is by first connecting line (56,56 ') directly link to each other with the suction chamber (124) of at least one pump, described first connecting line (56,56 ') along described static or rotation pump portion (16) extension, and wherein (54 ") link to each other with the described suction chamber of at least one pump (18; 20) second delivery outlet (LPO), and described second connecting line extends along cooling unit (76) by second connecting line.
11. manual transmission according to claim 10, it is characterized in that, described throttle (D, D1, D2) is configured such that the part that flows out through described delivery outlet respectively of hydraulic fluid can be by described throttle (D, D1, D2) control, and described hydraulic fluid flows into described throttle (D, D1, D2).
12. according to claim 10 or 11 described manual transmissions, it is characterized in that, first throttle valve (D1) and second throttle (D2) are provided with shared valve housing (100), and wherein said throttle (D1, D2) has shared second delivery outlet (LPO).
13. manual transmission according to claim 12 is characterized in that, described two throttles (D1, D2) are designed to be and match to such an extent that the described first throttle valve and second throttle can not be closed simultaneously.
14. manual transmission according to claim 13, it is characterized in that, under the closed condition of described first throttle valve (D1), the valve gate (110) of the first throttle valve (D1) of closing of delivery outlet that is used for described first throttle valve (D1) is with the gate pier of closing movement of the valve gate (110 ') that acts on described second throttle (D2), described valve gate (110 ') is used for the closing of delivery outlet of described second throttle (D2), and vice versa.
15. according to each described manual transmission among the claim 5-14, it is characterized in that, be used for cooling by the access path setting of the cooling unit (76) of the hydraulic fluid of described throttle (D, D1, D2) institute throttling along the suction line of the pressure chamber of respective pump and pump.
16. according to the described manual transmission of above-mentioned each claim, it is characterized in that, described pressure control device is controllable, so that the driving torque by described input shaft (12) transmission only is transferred to the first mechanical transmission branch road (26) corresponding to selected gear stage (G1, G3, G5, G7), perhaps only be transferred to the second mechanical transmission branch road (28) corresponding to selected gear stage (G2, G4, G6, R), perhaps be transferred to two mechanical transmission branch roads (26,28), to be used for the change of gear stage.
17., it is characterized in that the rotor (22,24) of described pump (18,20) is connected to corresponding mechanical transmission branch road (26,28) effectively drivingly, and does not need the intervention of friction clutch according to the described manual transmission of above-mentioned each claim.
18., it is characterized in that described first pump (18) and second pump (20) have shared suction chamber (124) according to the described manual transmission of above-mentioned each claim.
19. according to the described manual transmission of above-mentioned each claim, its spy is being that at least one pump (18,20) is peripherally surrounded by annular chamber (124), described annular chamber (124) is filled with hydraulic fluid.
20. according to claim 18 or 19 described manual transmissions, it is characterized in that, described suction chamber (124) has annular chamber, and described annular chamber is surrounded by the elastic annular wall at least in part, and described annular wall can change the capacity of suction chamber based on the hydrodynamic pressure in the suction chamber.
21. manual transmission according to claim 20 is characterized in that, described annular wall is the part of annular enclosure (126), or the annular enclosure that is made of metal (126) forms.
22., it is characterized in that the respective pump portion (16) of described pump (18,20) is rotatable too according to the described manual transmission of above-mentioned each claim.
23. according to the described manual transmission of above-mentioned each claim, it is characterized in that, the rotary pump portion (16) that is fixedly connected to described second pump (20) of the pump portion (16) of described first pump (18), the pump portion (16) of described first pump (18) is especially integrated with the pump portion (16) of described second pump (20).
24., it is characterized in that the rotary corresponding pump portion (16) that is bonded to described pump (18,20) regularly of described input shaft (12) according to the described manual transmission of above-mentioned each claim.
25. according to each described manual transmission among the claim 1-21, it is characterized in that, corresponding differential gear is associated with two mechanical transmission branch roads (26,28), wherein, the input of corresponding differential gear is bonded to input shaft (12), first output is bonded to the rotor (22,24) of respective pump (18,20), and second output is bonded to corresponding mechanical transmission branch road (26,28).
26. manual transmission according to claim 25 is characterized in that, corresponding differential gear is formed by planetary pinion (82).
27., it is characterized in that the pump portion (16) of described pump (18,20) is set to static according to claim 25 or 26 described manual transmissions.
28., it is characterized in that described input shaft (12) is permanently bonded to each other with the described first and second mechanical transmission branch roads (26,28) according to each described manual transmission among the claim 25-27.
29., it is characterized in that described pump (18,20) is made into simple pump and has transformable geometrical shape according to the described manual transmission of above-mentioned each claim.
30., it is characterized in that described pump (18,20) is a radial piston pump according to the described manual transmission of above-mentioned each claim.
31., it is characterized in that electric installation (80) is bonded to described pump portion (16) effectively drivingly or is bonded in described two pumps (18,20) rotor (22,24) of at least one according to the described manual transmission of above-mentioned each claim.
32. according to the described manual transmission of above-mentioned each claim, it is characterized in that, control unit (53) is provided, when the gear stage of the first mechanical transmission branch road (26) is chosen, can controlledly be used for the change of gear stage by described pressure control device of described control unit (53) and gear stage actuator, make
The gear stage of-described second mechanical transmission the branch road (28) is chosen, and described first pump (18) is hydraulically blocked, and described second pump (20) is by short circuit hydraulically;
-fluid the stream carried by described second pump (20) subsequently roughly fully is transmitted by the described second mechanical transmission branch road (28) until driving torque little by little by throttling;
The hydraulic pressure blocking-up of-described subsequently first pump (18) is opened, and the rotational velocity of input shaft (12) reduces; And
-described subsequently second pump (20) is hydraulically blocked.
33. manual transmission according to claim 32 is characterized in that, described pressure control device can be controlled by control unit (53), makes the short circuit hydraulically of described first pump quilt with opening that the hydraulic pressure that is used for described first pump (18) is blocked.
34. according to claim 32 or 33 described manual transmissions, it is characterized in that, described pressure control device and gear stage actuator can be controlled by control unit (53), make that the still chosen gear stage of the described first mechanical transmission branch road (26) breaks away from after the hydraulic pressure blocking-up of described first pump (18) is opened.
CN200880024633A 2007-06-05 2008-06-02 Manual transmission Pending CN101743413A (en)

Applications Claiming Priority (3)

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DE102007026133.2 2007-06-05
DE102007026133A DE102007026133A1 (en) 2007-06-05 2007-06-05 manual transmission
PCT/EP2008/004381 WO2008148511A2 (en) 2007-06-05 2008-06-02 Manual transmission

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CN103702879A (en) * 2011-07-13 2014-04-02 爱信Ai株式会社 Manual transmission
CN106369072A (en) * 2015-07-25 2017-02-01 博格华纳公司 Hydraulic control device for controlling a double clutch and multiple clutch device with such a control device
CN108027043A (en) * 2015-09-29 2018-05-11 舍弗勒技术股份两合公司 For controlling the control device component of fluid assembly
CN109372995A (en) * 2018-11-20 2019-02-22 南京清元景和环境科技有限公司 Manually adjust air-valve

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DE102009030969B4 (en) 2009-06-29 2020-08-06 Magna Pt B.V. & Co. Kg Torque transmission device
DE102017009955A1 (en) * 2017-10-26 2019-05-02 Borgwarner Inc. Rotary feedthrough for a fluid and clutch assembly with such a rotary feedthrough

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US1603179A (en) * 1920-07-20 1926-10-12 Wingquist Sven Gustaf Hydraulic coupling and change-speed-gearing device
JPH0765656B2 (en) * 1985-02-12 1995-07-19 株式会社大金製作所 Automatic transmission
JP4945903B2 (en) * 2005-02-03 2012-06-06 トヨタ自動車株式会社 transmission
JP4892880B2 (en) * 2005-02-22 2012-03-07 トヨタ自動車株式会社 transmission

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CN103702879A (en) * 2011-07-13 2014-04-02 爱信Ai株式会社 Manual transmission
CN103702879B (en) * 2011-07-13 2016-08-03 爱信Ai株式会社 Manual transmission
CN106369072A (en) * 2015-07-25 2017-02-01 博格华纳公司 Hydraulic control device for controlling a double clutch and multiple clutch device with such a control device
CN108027043A (en) * 2015-09-29 2018-05-11 舍弗勒技术股份两合公司 For controlling the control device component of fluid assembly
US10738880B2 (en) 2015-09-29 2020-08-11 Schaeffler Technologies AG & Co.KG Control unit arrangement for controlling a fluid arrangement
CN109372995A (en) * 2018-11-20 2019-02-22 南京清元景和环境科技有限公司 Manually adjust air-valve

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WO2008148511A2 (en) 2008-12-11
DE102007026133A1 (en) 2008-12-11
DE112008001488A5 (en) 2010-04-22

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Application publication date: 20100616