WO2023045706A1 - 齿轮箱的控制装置 - Google Patents

齿轮箱的控制装置 Download PDF

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Publication number
WO2023045706A1
WO2023045706A1 PCT/CN2022/115432 CN2022115432W WO2023045706A1 WO 2023045706 A1 WO2023045706 A1 WO 2023045706A1 CN 2022115432 W CN2022115432 W CN 2022115432W WO 2023045706 A1 WO2023045706 A1 WO 2023045706A1
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WO
WIPO (PCT)
Prior art keywords
oil
way valve
port
clutch
brake
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.)
Ceased
Application number
PCT/CN2022/115432
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English (en)
French (fr)
Inventor
王福亮
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.)
ZF Wind Power Antwerpen NV
Zf Wind Power Tianjin Co Ltd
Original Assignee
ZF Wind Power Antwerpen NV
Zf Wind Power Tianjin Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Wind Power Antwerpen NV, Zf Wind Power Tianjin Co Ltd filed Critical ZF Wind Power Antwerpen NV
Priority to US18/693,536 priority Critical patent/US12104689B2/en
Priority to EP22871758.3A priority patent/EP4407214A4/en
Publication of WO2023045706A1 publication Critical patent/WO2023045706A1/zh
Anticipated expiration legal-status Critical
Ceased 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control
    • F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
    • 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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F03D80/705—Lubrication circuits; Lubrication delivery means
    • F03D80/707—Gearing lubrication, e.g. gear boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • 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
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • 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
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/183—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with force-transmitting members arranged side by side acting on a spot type force-applying member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/50—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital conical gears
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/32—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using fluid pressure actuators
    • 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control
    • F16H57/0436—Pumps
    • F16H57/0439—Pumps using multiple pumps with different power sources or a single pump with different power sources, e.g. one and the same pump may selectively be driven by either the engine or an electric motor
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps; Pressure control
    • F16H57/0441—Arrangements of pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/98—Lubrication
    • 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
    • F16D2500/308—Signal inputs from the transmission
    • F16D2500/30802—Transmission oil properties
    • F16D2500/30805—Oil 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
    • F16D2500/70422—Clutch parameters
    • F16D2500/70424—Outputting a clutch engaged-disengaged signal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • F16H61/0267—Layout of hydraulic control circuits, e.g. arrangement of valves
    • 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
    • F16N—LUBRICATING
    • F16N2210/00—Applications
    • F16N2210/02—Turbines
    • F16N2210/025—Wind Turbines
    • 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
    • F16N—LUBRICATING
    • F16N2270/00—Controlling
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a control device, in particular to a control device for an oil pump of a wind power gearbox.
  • a wind turbine gearbox is used to transmit torque between the main shaft connected to the wind rotor and the engine, and it usually uses a planetary gear train to achieve speed increase.
  • the electric pump does not turn on or works at a very low speed, and the flow rate it provides is very low, so at this time the mechanical pump will be mainly responsible for the circulation of the lubricating oil in the gearbox and Achieve lubrication.
  • the displacement of the mechanical pump is designed according to the rated load and rated speed of the gearbox, and the flow rate of the mechanical pump is completely determined by the input speed of the gearbox.
  • the rotational speed of the mechanical pump is also low, which cannot provide sufficient oil volume. Insufficient oil quantity will lead to insufficient lubrication of parts such as gears and bearings in the gearbox, thereby affecting the operation and life of the gearbox.
  • the present invention provides a control device for a gearbox, which can adapt to rated working conditions and special working conditions Under different lubrication requirements.
  • a control device for a gear box includes a mechanical pump and an electric pump, characterized in that the control device includes: a sensor module for detecting the system oil pressure of lubricating oil in the gear box, a differential, Clutches, brakes and control modules, of which,
  • the differential includes an input bevel gear that meshes with the bevel gear of the output shaft of the gearbox, a differential case that is connected to the input bevel gear, and is arranged in the differential case and connected to the differential
  • the first half shaft and the second half shaft meshed by the bevel gear of the gear housing, the second half shaft is connected to the input of the mechanical pump, due to the construction of the differential, the rotational speed of the first half shaft and the second half shaft
  • the sum is twice the rotational speed of the differential case, and the power distribution of the two half shafts is realized through the introduction of the differential;
  • the brake includes a brake caliper, a brake disc, and a brake disc shaft fixedly connected to the brake disc, and the brake disc shaft is fixedly connected to the first half shaft;
  • the outer disk of the clutch is connected to the differential case, and the inner disk of the clutch is sleeved on the first half shaft;
  • the control module is used to actuate the brake calipers to clamp the brake disc and release the clutch when the system oil pressure is lower than the system oil pressure threshold, that is, when the high-speed operation of the mechanical pump is required.
  • the rotational speed of the first axle shaft is zero, and the rotational speed of the second axle shaft is twice the rotational speed of the differential case; and it is used when the system oil pressure is higher than the system oil pressure threshold, that is, under the rated working condition Releasing the brake caliper and closing the clutch causes the inner and outer discs to rotate synchronously so that the rotational speeds of the first and second half shafts are the same.
  • control module includes a two-position four-way valve
  • the two-position four-way valve includes an oil inlet and an oil discharge port connected to the oil tank, a first oil port connected to the brake, and a second oil port connected to the clutch,
  • the spool of the two-position four-way valve when the system oil pressure is lower than the system oil pressure threshold, the spool of the two-position four-way valve is in the first position to establish a passage between the first oil port and the oil inlet to actuate the brake caliper, and in the second A passage is established between the oil port and the oil discharge port to release the clutch;
  • the spool of the two-position four-way valve When the system oil pressure is higher than the system oil pressure threshold, the spool of the two-position four-way valve is in the second position to establish a passage between the second oil port and the oil inlet port to close the clutch, and the first oil port and the discharge port A passage is established between the oil ports to release the brake caliper.
  • the two-position four-way valve is hydraulically controlled or electronically controlled.
  • the two-position four-way valve is provided with a damping hole.
  • the sensor module is also used to respectively detect the first oil pressure of the mechanical pump and the second oil pressure of the electric pump;
  • the control module is used to actuate the brake caliper to clamp the brake disc and release the clutch when the first oil pressure is lower than a first threshold and the second oil pressure is lower than a second threshold.
  • the rotational speed of the first axle shaft is zero, and the rotational speed of the second axle shaft is twice the rotational speed of the differential case; and for when the first oil pressure is higher than the first threshold and the second oil pressure is lower than the second
  • the brake caliper is released and the clutch is closed so that the inner disc and the outer disc rotate synchronously so that the rotational speeds of the first half shaft and the second half shaft are the same; and for when the second oil pressure is higher than the second Threshold, that is, when the lubrication depends on the electric pump and the mechanical pump does not need to work, the brake calipers and the clutch are released so that the speed of the second half shaft is zero and the speed of the first half shaft is the differential housing 2 times the speed.
  • the control module includes a two-position four-way valve, a first two-position three-way valve, and a second two-position three-way valve
  • the two-position four-way valve includes an oil inlet connected to the oil tank and a first discharge valve.
  • the oil port and the first oil port and the second oil port, the first two-position three-way valve includes the second oil discharge port, the third oil port connected to the first oil port and the fourth oil port connected to the brake, the second The two-position three-way valve includes a third oil discharge port, a fifth oil port connected to the second oil port and a sixth oil port connected to the clutch,
  • the spools of the two-position four-way valve, the first two-position three-way valve and the second two-position three-way valve are all located at the first position to establish passages between the first oil port and the oil inlet port, and between the third oil port and the fourth oil port to actuate the brake calipers, and between the fifth oil port and the sixth oil port, establishing a passage between a second oil port and said first oil discharge port to release said clutch;
  • the spool of the two-position four-way valve When the first oil pressure is higher than the first threshold and the second oil pressure is lower than the second threshold, the spool of the two-position four-way valve is in the second position, the valves of the first two-position three-way valve and the second two-position three-way valve
  • the cores are all located in the first position to establish passages between the second oil port and the oil inlet port, between the fifth oil port and the sixth oil port to close the clutch, and between the first oil port and the first oil discharge port. establishing a passage between the ports and establishing a passage between the third oil port and the fourth oil port to release the brake caliper;
  • the spools of the first two-position three-way valve and the second two-position three-way valve are both in the second position to establish a passage between the fourth oil port and the second oil discharge port to The brake caliper is released, and a passage is established between the sixth oil port and the third oil discharge port to release the clutch.
  • the two-position four-way valve, the first two-position three-way valve, and the second two-position three-way valve are hydraulically controlled or electrically controlled.
  • the two-position four-way valve, the first two-position three-way valve and the second two-position three-way valve are respectively provided with damping holes.
  • the technical effect obtained by the present invention is: by adopting the combination of differential, clutch and brake, the operation of the mechanical pump can be adapted to the needs of different working conditions, avoiding the lack of lubrication under low speed and/or low temperature conditions, and the rated working condition The potential risk of excessive oil quantity to the gearbox under certain conditions.
  • Fig. 1 shows a schematic diagram of a control device according to an embodiment of the present invention
  • Fig. 2 shows the schematic diagram of the control device of another embodiment of the present invention.
  • the control device for a gearbox is applicable to a gearbox including a mechanical pump 30 and an electric pump (not shown).
  • the power of the mechanical pump 30 comes from the output of the gear box.
  • 80 denotes the gear box housing
  • 81 denotes the output shaft of the gear box for driving the mechanical pump 30 to work.
  • the control device includes: a sensor module (not shown) for detecting the system oil pressure of lubricating oil in the gearbox, a differential 40 , a clutch 60 , a brake 50 and a control module 70 .
  • the power is transmitted to the differential 40 through the output shaft 81 provided with bevel gears, and the power distribution is realized together with the clutch 60 and the brake 50, so that the mechanical pump 30 can obtain different speed ratios.
  • the differential 40 includes an input bevel gear 44 meshing with the bevel gear of the gearbox output shaft 81, a differential housing 41 connected to the input bevel gear 44, and a
  • the first half-shaft 42 and the second half-shaft 43 are inside the differential case 41 and meshed with the bevel gear of the differential case 41 , and the second half-shaft 43 is connected to the input of the mechanical pump 30 .
  • twice the rotational speed of the differential case 41 is the sum of the rotational speeds of the first half shaft 42 and the second half shaft 43 .
  • the brake 50 includes a brake caliper 51, a brake disc 52, and a brake disc shaft 53 fixedly connected to the brake disc 52, wherein the brake disc shaft 53 is fixedly connected to the first half shaft 42, thus The brake disc shaft 53 and the first half shaft 42 move synchronously or are stationary.
  • the outer disc 61 of the clutch is connected to the differential case 41 , and the inner disc 62 of the clutch is sheathed on the first half shaft 42 .
  • the control module 70 is used to actuate the brake caliper 51 to clamp the brake disc 52 and release the clutch 60 (outer disc 61 of the clutch and Inner disc 62 does not contact, and does not rotate synchronously) so that the rotational speed of the first semi-shaft 42 is zero, and the rotational speed of the second semi-shaft 43 is 2 times of the rotational speed of the differential case 41;
  • the brake caliper 51 is released and the clutch is closed to make the inner disc and the outer disc rotate synchronously so that the rotational speeds of the first half shaft 42 and the second half shaft 43 are the same.
  • the control module includes a two-position four-way valve 71, and the two-position four-way valve 71 includes an oil inlet P and an oil discharge port T connected to the oil tank, and the first oil port 1 connected to the brake 50 and the first oil port connected to the brake 50.
  • the second oil port 2 of the clutch 60 wherein, when the system oil pressure is lower than the system oil pressure threshold, the spool of the two-position four-way valve is in the first position (left position) to establish a passage between the first oil port 1 and the oil inlet P to activate the brake.
  • the movable caliper 51 and a passage is established between the second oil port 2 and the oil discharge port T to release the clutch.
  • the first half-shaft 42 is at rest due to the clamping of the brake caliper 51, so the rotational speed of the first half-shaft 42 is zero, and the rotational speed of the second half-shaft 43 connected to the mechanical pump 30 is the differential housing. 41 times the speed, the mechanical pump 30 is at high speed, which can bring a higher oil volume to the gearbox. This working condition corresponds to the case where the electric pump does not work or works at a very low speed.
  • the supply of lubricating oil depends on mechanical pump.
  • the spool of the two-position four-way valve is in the second position (right position) to establish a passage between the second oil port 2 and the oil inlet P to close the clutch , and establish a passage between the first oil port 1 and the oil discharge port T so that the oil in the brake 50 returns to the oil tank to release the brake caliper.
  • the rotation speed of the brake disc is consistent with that of the first semi-shaft 42, and since the outer disc 61 and the inner disc 62 of the clutch rotate synchronously, the rotational speed of the first semi-shaft 42 is the same as that of the differential housing 41 connected to the clutch outer disc 61 , the rotational speeds of the first half shaft 42 , the differential case 41 and the second half shaft 43 are all the same.
  • the rotational speed of the mechanical pump 30 is lower than that of the foregoing situation, corresponding to the rated working condition of the gear box, there is no need to obtain more lubricating oil through high speed.
  • the two-position four-way valve 71 is hydraulically controlled or electrically controlled, and is actuated according to the detection signal S of the sensor module. In order to avoid the impact of oil pressure when the brake is activated and the clutch is closed, the two-position four-way valve is provided with a damping hole.
  • FIG. 2 it shows a control device of a gearbox according to another embodiment of the present invention, which can be used to control three different working conditions of a mechanical pump.
  • the sensor module is also used to respectively detect the first oil pressure of the mechanical pump and the second oil pressure of the electric pump (represented by S1 and S2 respectively), through the detection of the first oil pressure and the second oil pressure To judge the working status of mechanical pump and electric pump.
  • the control module is used to actuate the brake caliper 51 to Clamping the brake disc 52 and releasing the clutch 60 so that the speed of the first half shaft 42 is zero and the speed of the second half shaft 43 is twice the speed of the differential case 41; and for When the first oil pressure is higher than the first threshold and the second oil pressure is lower than the second threshold, the brake caliper 51 is released and the clutch 60 is closed so that the inner disc 62 and the outer disc 61 rotate synchronously so that the first The rotational speeds of the semi-shaft 42 and the second semi-shaft 43 are the same; and are used to release the brake caliper 51 and the clutch 60 when the second oil pressure is higher than the second threshold so that the rotational speed of the second semi-shaft is zero, The rotational speed of the first axle shaft is twice the rotational speed of the differential case, and the mechanical pump does not work at this moment.
  • the control module 70 includes a two-position four-way valve 71, a first two-position three-way valve 72 and a second two-position three-way valve 73, and the two-position four-way valve 71 includes an inlet connected to the fuel tank.
  • the first two-position three-way valve 72 includes the second oil discharge port
  • the second two-position three-way valve 73 includes a third oil discharge port
  • the fifth oil port 5 connecting the second oil port 2 and the sixth oil port communicating with the clutch 60 Mouth 6.
  • the mechanical pump when the first oil pressure is lower than the first threshold and the second oil pressure is lower than the second threshold, the mechanical pump needs to run at high speed.
  • the spools of the three-way valve 73 are all located at the first position (left position) to establish passages between the first oil port 1 and the oil inlet P, and between the third oil port 3 and the fourth oil port 4 so that The brake caliper 51 is activated, and a passage is established between the fifth oil port 5 and the sixth oil port 6, and between the second oil port 2 and the first oil discharge port T to release the clutch 60.
  • the rotational speed of the first semi-shaft 42 is zero
  • the rotational speed of the second semi-shaft 43 (mechanical pump 30) is twice the rotational speed of the differential housing 41. condition.
  • the spool of the two-position four-way valve 71 is in the second position (right side position)
  • the spools of the first two-position three-way valve 72 and the second two-position three-way valve 73 are all located in the first position (left position) so that between the second oil port 2 and the oil inlet P, at the second A passage is established between the fifth oil port 5 and the sixth oil port 6 to close the clutch 60, and a passage is established between the first oil port 1 and the first oil discharge port and between the third oil port 3 and the fourth oil port 4 for releasing the brake caliper 51.
  • the rotational speeds of the first half shaft 42 , the second half shaft 43 and the differential case 41 are all equal, and the mechanical pump can meet the requirements of the rated working condition by running at a low speed.
  • the circulation of lubricating oil can be completed by the electric pump.
  • the mechanical pump is used as a backup when the power is cut off.
  • the mechanical pump does not need to work, and it is in the standby condition with zero speed. That is, when the second oil pressure is higher than the second threshold, the spools of the first two-position three-way valve 72 and the second two-position three-way valve 73 are both in the second position (right position) so that the fourth oil port 4 and the second oil port A passage is established between the two oil discharge ports to release the brake caliper 51 , and a passage is established between the sixth oil port 6 and the third oil discharge port to release the clutch 60 .
  • the two-position, four-way valve, the first two-position, three-way valve, and the second two-position, three-way valve are hydraulically controlled or electrically controlled.
  • the two-position four-way valve, the first two-position three-way valve, and the second two-position three-way valve are respectively provided with damping holes.
  • the mechanical pump can obtain different speeds in different working conditions to adapt to the needs of the current working conditions.

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Abstract

本发明提供了一种齿轮箱的控制装置，包括：传感器模组、差速器、离合器、制动器和控制模组，所述控制模组用于在所述系统油压低于系统油压阈值时致动所述制动卡钳以夹紧所述制动盘并且释放所述离合器；以及用于在所述系统油压高于系统油压阈值时释放所述制动卡钳并且闭合所述离合器。通过离合器、差速器和制动器的组合控制来获得机械泵的不同转速比，使得在不同的工况下机械泵可以具有不同的流量，兼顾了额定工况和特殊工况的润滑需求，避免了低速和/或低温条件下润滑的不足，以及额定工况下过多的油量。

Description

齿轮箱的控制装置 技术领域
本发明涉及一种控制装置，特别涉及一种风电齿轮箱的油泵的控制装置。
背景技术
风电齿轮箱用于在连接风轮的主轴和发动机之间传递扭矩，其通常采用行星轮系来实现增速。在齿轮箱的运行过程中，行星轮系的各个部件，特别是齿轮啮合部和轴承都需要润滑以保证齿轮箱的正常工作。目前的风电齿轮箱系统中，存在机械泵和电动泵的双油泵设计，其中机械泵由风轮的转动提供动力，而电动泵则完全由外部电力供电。
然而，在润滑油油温较低的情况下，电动泵不开启或者以很低的转速工作，其提供的流量很低，因而此时将主要由机械泵来负责齿轮箱中润滑油的循环以实现润滑。通常机械泵的排量是根据齿轮箱的额定负载和额定速度来设计的，并且机械泵的流量完全由齿轮箱的输入速度来决定。然而当齿轮箱的输入速度较低时，机械泵的转速也较低，从而不能提供充足的油量。油量的不足又会导致齿轮箱中齿轮和轴承等零部件的不充分润滑从而影响齿轮箱的运行和寿命。
为了克服这一问题，如果按照低输入转速的情况来设计机械泵的排量，这又会导致额定工况下流量过大，而过大的流量又会引起较高的油压，增加了漏油的风险，并且增加齿轮箱的能源损耗。
发明内容
本发明为了解决现有技术中采用固定排量的机械泵难以实现额定工况和特殊工况下不同润滑需求的缺陷，提供一种齿轮箱的控制装置，其可以适应额定工况和特殊工况下不同的润滑需求。
本发明的目的是通过以下技术方案来实现的：
一种齿轮箱的控制装置，所述齿轮箱包括机械泵和电动泵，其特点在于，所述控制装置包括：用于检测齿轮箱的润滑油的系统油压的传感器模组、差速器、离合器、制动器和控制模组，其中，
所述差速器包括与齿轮箱输出轴的锥齿轮相啮合的输入伞齿轮、与所述输入伞齿轮相连的差速器壳体、设置于所述差速器壳体内且与所述差速器壳体的锥齿轮啮合的第一半轴和第二半轴，所述第二半轴连接所述机械泵的输入，由于差速器的构造，第一半轴和第二半轴的转速之和为差速器壳体转速的两倍，通过差速器的引入来实现两个半轴的动力分配；
所述制动器包括制动卡钳、制动盘、与制动盘固定连接的制动盘轴，所述制动盘轴与所述第一半轴固定连接；
所述离合器的外盘连接于所述差速器壳体，所述离合器的内盘套设于所述第一半轴上；
所述控制模组用于在所述系统油压低于系统油压阈值时，即需要机械泵高速运转时致动所述制动卡钳以夹紧所述制动盘并且释放所述离合器以使第一半轴的转速为零、第二半轴的转速为所述差速器壳体转速的2倍；以及用于在所述系统油压高于系统油压阈值时，即额定工况时释放所述制动卡钳并且闭合所述离合器使所述内盘和所述外盘同步旋转以使第一半轴和第二半轴的转速相同。
优选地，所述控制模组包括两位四通阀，所述两位四通阀包括连接油箱的进油口和卸油口以及连通制动器的第一油口和连接离合器的第二油口，
其中，系统油压低于系统油压阈值时两位四通阀的阀芯位于第一位置以在第一油口和进油口之间建立通路以致动所述制动卡钳，以及在第二油口和所述卸油口之间建立通路以释放所述离合器；
系统油压高于系统油压阈值时两位四通阀的阀芯位于第二位置以在第二油口和进油口之间建立通路以闭合所述离合器，并在第一油口和卸油口之间建立通路以释放所述制动卡钳。
优选地，所述两位四通阀是液压控制的或者电信号控制的。
优选地，所述两位四通阀上设置有阻尼孔。
优选地，所述传感器模组还用于分别检测机械泵的第一油压和电动泵的第二油压；
所述控制模组用于在第一油压低于第一阈值且第二油压低于第二阈值时致动所述制动卡钳以夹紧所述制动盘并且释放所述离合器以使第一半轴的转速为零、第二半轴的转速为所述差速器壳体转速的2倍；以及用于在第一油压高于第一阈值且第二油压低于第二阈值时释放所述制动卡钳并且闭合所述离合器使所述内盘和所述外盘同步旋转以使第一半轴和第二半轴的转速相同；并且用于在第二油压高于第 二阈值时，即润滑依靠电动泵而机械泵不需要工作时释放所述制动卡钳和所述离合器以使第二半轴的转速为零、第一半轴的转速为所述差速器壳体转速的2倍。
优选地，所述控制模组包括一两位四通阀、第一两位三通阀和第二两位三通阀，所述两位四通阀包括连接油箱的进油口和第一卸油口以及第一油口和第二油口，第一两位三通阀包括第二卸油口、连接第一油口的第三油口和连通所述制动器的第四油口，第二两位三通阀包括第三卸油口、连接第二油口的第五油口和连通所述离合器的第六油口，
其中，第一油压低于第一阈值且第二油压低于第二阈值时两位四通阀、第一两位三通阀和第二两位三通阀的阀芯均位于第一位置以在第一油口和进油口之间、以及第三油口和第四油口之间建立通路以致动所述制动卡钳，并在第五油口和第六油口之间、在第二油口和所述第一卸油口之间建立通路以释放所述离合器；
第一油压高于第一阈值且第二油压低于第二阈值时两位四通阀的阀芯位于第二位置、第一两位三通阀和第二两位三通阀的阀芯均位于第一位置以在第二油口和进油口之间、在第五油口和第六油口之间建立通路以闭合所述离合器，并在第一油口和第一卸油口之间建立通路以及在第三油口和第四油口之间建立通路以释放所述制动卡钳；
第二油压高于第二阈值时第一两位三通阀和第二两位三通阀的阀芯均位于第二位置以在第四油口和第二卸油口之间建立通路以释放所述制动卡钳，以及在第六油口和第三卸油口之间建立通路以释放所述离合器。
优选地，所述两位四通阀、第一两位三通阀、第二两位三通阀分别各自是液压控制的或者电信号控制的。
优选地，所述两位四通阀、第一两位三通阀、第二两位三通阀分别各自设置有阻尼孔。
本发明获得的技术效果是：通过采用差速器、离合器和制动器的组合，可以使得机械泵的运行适应于不同工况的需求，避免了低速和/或低温条件下润滑的不足，以及额定工况下过多的油量给齿轮箱带来的潜在风险。
附图概述
本发明的特征、性能由以下的实施例及其附图进一步描述。
图1示出了本发明一实施例的控制装置的示意图；
图2示出了本发明另一实施例的控制装置的示意图；
本发明的较佳实施方式
下面参考图1-2，根据本发明的具体实施方式并结合附图来进一步说明。
参考图1，本实施例所述的齿轮箱的控制装置适用于包括机械泵30和电动泵(未示出)的齿轮箱。机械泵30的动力来源于齿轮箱的输出，图1中以80表示齿轮箱壳体，81表示齿轮箱的用于驱使机械泵30工作的输出轴。
所述控制装置包括：用于检测齿轮箱的润滑油的系统油压的传感器模组(未示出)、差速器40、离合器60、制动器50和控制模组70。在本实施例中，由设置有锥齿轮的输出轴81将动力传递至差速器40，与离合器60和制动器50一起实现动力分配，从而使得机械泵30获得不同的转速比。
具体来说，所述差速器40包括与齿轮箱输出轴81的锥齿轮相啮合的输入伞齿轮44、与所述输入伞齿轮44相连的差速器壳体41、设置于所述差速器壳体41内且与所述差速器壳体41的锥齿轮啮合的第一半轴42和第二半轴43，所述第二半轴43连接所述机械泵30的输入。在差速器40的构造中，差速器壳体41的转速的2倍为第一半轴42和第二半轴43的转速之和。
所述制动器50包括制动卡钳51、制动盘52、与制动盘52固定连接的制动盘轴53，其中，所述制动盘轴53与所述第一半轴42固定连接，因而制动盘轴53和第一半轴42是同步运动或者静止的。
在所述离合器60中，离合器的外盘61连接于所述差速器壳体41，所述离合器的内盘62套设于所述第一半轴42上。
所述控制模组70用于在所述系统油压低于系统油压阈值时致动所述制动卡钳51以夹紧所述制动盘52并且释放所述离合器60(离合器的外盘61和内盘62并没有接触，也不同步旋转)以使第一半轴42的转速为零、第二半轴43的转速为所述差速器壳体41转速的2倍；以及用于在所述系统油压高于系统油压阈值时释放所述制动卡钳51并且闭合所述离合器使所述内盘和所述外盘同步旋转以使第一半轴42和第二半轴43的转速相同。
具体来说，所述控制模组包括两位四通阀71，所述两位四通阀71包括连接油箱的进油口P和卸油口T以及连通制动器50的第一油口1和连接离合器60的第二油口2。其中，系统油压低于系统油压阈值时两位四通阀的阀芯位于第一位置(左侧位置)以在第一油口1和进油口P之间建立通路以致动所述制动卡钳51，以及在第二油口2和所述卸油口T之间建立通路以释放所述离合器。 此时第一半轴42由于制动卡钳51的夹紧而处于静止，由此第一半轴42的转速为零，连接机械泵30的第二半轴43的转速则为差速器壳体41的转速的2倍，机械泵30处于高速，可以为齿轮箱带来较高的油量，这一工况对应于电动泵不工作或者以极低转速工作的情况，润滑油的供应依赖于机械泵。
而当系统油压高于系统油压阈值时两位四通阀的阀芯位于第二位置(右侧位置)以在第二油口2和进油口P之间建立通路以闭合所述离合器，并在第一油口1和卸油口T之间建立通路使得制动器50中的油返回油箱以释放所述制动卡钳。此时，制动盘与第一半轴42转速一致，由于离合器的外盘61和内盘62同步旋转，则第一半轴42的转速与连接着离合器外盘61的差速器壳体41的转速相同，此时第一半轴42、差速器壳体41和第二半轴43的转速均相同。机械泵30的转速较之前述的情况而言有所降低，对应于齿轮箱的额定工况，无需再通过高速来获得较多的润滑油。
所述两位四通阀71是液压控制的或者电信号控制的，其根据传感器模组的检测信号S被致动。为了避免致动制动器和闭合离合器时油压的冲击，所述两位四通阀上设置有阻尼孔。
参考图2，示出了本发明另一实施例的齿轮箱的控制装置，其可以用于控制机械泵的三种不同工况。
具体来说，所述传感器模组还用于分别检测机械泵的第一油压和电动泵的第二油压(分别以S1和S2表示)，通过第一油压和第二油压的检测来判断机械泵和电动泵的工作状态。
在本实施例中，所述控制模组用于在第一油压低于第一阈值且第二油压低于第二阈值(电动泵基本不工作)时致动所述制动卡钳51以夹紧所述制动盘52并且释放所述离合器60以使第一半轴42的转速为零、第二半轴43的转速为所述差速器壳体41转速的2倍；以及用于在第一油压高于第一阈值且第二油压低于第二阈值时释放所述制动卡钳51并且闭合所述离合器60使所述内盘62和所述外盘61同步旋转以使第一半轴42和第二半轴43的转速相同；并且用于在第二油压高于第二阈值时释放所述制动卡钳51和所述离合器60以使第二半轴的转速为零、第一半轴的转速为所述差速器壳体转速的2倍，此时机械泵不工作。
参考图2，所述控制模组70包括一两位四通阀71、第一两位三通阀72和第二两位三通阀73，所述两位四通阀71包括连接油箱的进油口P和第一卸油口T以及第一油口1和第二油口2，第一两位三通阀72包括第二卸油口、连接第一油口1 的第三油口3和连通所述制动器50的第四油口4，第二两位三通阀73包括第三卸油口、连接第二油口2的第五油口5和连通所述离合器60的第六油口6。
其中，第一油压低于第一阈值且第二油压低于第二阈值时，需要机械泵高速运转，此时两位四通阀71、第一两位三通阀72和第二两位三通阀73的阀芯均位于第一位置(左侧位置)以在第一油口1和进油口P之间、以及第三油口3和第四油口4之间建立通路以致动所述制动卡钳51，并在第五油口5和第六油口6之间、在第二油口2和所述第一卸油口T之间建立通路以释放所述离合器60。这样第一半轴42转速为零，第二半轴43(机械泵30)转速为差速器壳体41的转速的2倍，机械泵处于高速运转中，对应于电动泵几乎不工作的工况。
对于齿轮箱正常运转的额定工况来说，即第一油压高于第一阈值且第二油压低于第二阈值时，两位四通阀71的阀芯位于第二位置(右侧位置)、第一两位三通阀72和第二两位三通阀73的阀芯均位于第一位置(左侧位置)以在第二油2口和进油口P之间、在第五油口5和第六油口6之间建立通路以闭合所述离合器60，并在第一油口1和第一卸油口之间建立通路以及在第三油口3和第四油口4之间建立通路以释放所述制动卡钳51。此时第一半轴42、第二半轴43和差速器壳体41的转速均相等，机械泵低速运转即可适应额定工况的需求。
如果电动泵正常工作，那么润滑油的循环则可以通过电动泵来完成，此时机械泵作为断电时的备用，在电动泵正常工作时机械泵无需工作，处于转速为零的待命工况，即第二油压高于第二阈值时第一两位三通阀72和第二两位三通阀73的阀芯均位于第二位置(右侧位置)以在第四油口4和第二卸油口之间建立通路以释放所述制动卡钳51，以及在第六油口6和第三卸油口之间建立通路以释放所述离合器60。此时无论两位四通阀71的阀芯处于何种位置，制动卡钳和离合器都被释放，第一半轴42的转速为差速器壳体41转速的2倍，第二半轴43转速为零，即机械泵不工作。
其中，所述两位四通阀、第一两位三通阀、第二两位三通阀分别各自是液压控制的或者电信号控制的。为了防止油压波动，所述两位四通阀、第一两位三通阀、第二两位三通阀分别各自设置有阻尼孔。
通过差速器、离合器和制动器的组合，可以在不同工况中使机械泵获得不同的转速以适应于当前工况的需求。
虽然以上描述了本发明的具体实施方式，但是本领域的技术人员应当理解，这些仅是举例说明，本发明的保护范围是由所附权利要求书限定的。本领域的技术人 员在不背离本发明的原理和实质的前提下，可以对这些实施方式做出多种变更或修改，但这些变更和修改均落入本发明的保护范围。

Claims (8)

  1. 一种齿轮箱的控制装置，所述齿轮箱包括机械泵(30)和电动泵，其特征在于，所述控制装置包括：用于检测齿轮箱的润滑油的系统油压的传感器模组、差速器(40)、离合器(60)、制动器(50)和控制模组，其中，
    所述差速器(40)包括与齿轮箱输出轴的锥齿轮(81)相啮合的输入伞齿轮(44)、与所述输入伞齿轮(44)相连的差速器壳体(41)、设置于所述差速器壳体(41)内且与所述差速器壳体(41)的锥齿轮啮合的第一半轴(42)和第二半轴(43)，所述第二半轴(43)连接所述机械泵(30)的输入；
    所述制动器(50)包括制动卡钳(51)、制动盘(52)、与制动盘(52)固定连接的制动盘轴(53)，所述制动盘轴(53)与所述第一半轴(42)固定连接；
    所述离合器(60)的外盘(63)连接于所述差速器壳体(41)，所述离合器(60)的内盘(62)套设于所述第一半轴上；
    所述控制模组用于在所述系统油压低于系统油压阈值时致动所述制动卡钳(51)以夹紧所述制动盘(52)并且释放所述离合器(60)以使第一半轴(42)的转速为零、第二半轴(43)的转速为所述差速器壳体(41)转速的2倍；以及用于在所述系统油压高于系统油压阈值时释放所述制动卡钳(51)并且闭合所述离合器(60)使所述内盘(62)和所述外盘(63)同步旋转以使第一半轴(42)和第二半轴(43)的转速相同。
  2. 如权利要求1所述的控制装置，其特征在于，所述控制模组包括两位四通阀(71)，所述两位四通阀(71)包括连接油箱的进油口和卸油口以及连通制动器(50)的第一油口(1)和连接离合器(60)的第二油口(2)，
    其中，系统油压低于系统油压阈值时两位四通阀的阀芯位于第一位置以在第一油口(1)和进油口之间建立通路以致动所述制动卡钳(51)，以及在第二油口(2)和所述卸油口之间建立通路以释放所述离合器(60)；
    系统油压高于系统油压阈值时两位四通阀的阀芯位于第二位置以在第二油口(2)和进油口之间建立通路以闭合所述离合器(60)，并在第一油口(1)和卸油口之间建立通路以释放所述制动卡钳(51)。
  3. 如权利要求2所述的控制装置，其特征在于，所述两位四通阀(71)是液压控制的或者电信号控制的。
  4. 如权利要求2所述的控制装置，其特征在于，所述两位四通阀上(71)设置有阻尼孔。
  5. 如权利要求1所述的控制装置，其特征在于，
    所述传感器模组还用于分别检测机械泵(30)的第一油压和电动泵的第二油压；
    所述控制模组用于在第一油压低于第一阈值且第二油压低于第二阈值时致动所述制动卡钳(51)以夹紧所述制动盘(52)并且释放所述离合器(60)以使第一半轴(42)的转速为零、第二半轴(43)的转速为所述差速器壳体(41)转速的2倍；以及用于在第一油压高于第一阈值且第二油压低于第二阈值时释放所述制动卡钳(51)并且闭合所述离合器(60)使所述内盘(62)和所述外盘(61)同步旋转以使第一半轴(42)和第二半轴(43)的转速相同；并且用于在第二油压高于第二阈值时释放所述制动卡钳(51)和所述离合器(60)以使第二半轴(43)的转速为零、第一半轴(42)的转速为所述差速器壳体(41)转速的2倍。
  6. 如权利要求5所述的控制装置，其特征在于，所述控制模组包括一两位四通阀(71)、第一两位三通阀(72)和第二两位三通阀(73)，所述两位四通阀(71)包括连接油箱的进油口和第一卸油口以及第一油口(1)和第二油口(2)，第一两位三通阀(72)包括第二卸油口、连接第一油口(1)的第三油口(3)和连通所述制动器(50)的第四油口(4)，第二两位三通阀(73)包括第三卸油口、连接第二油口(2)的第五油口(5)和连通所述离合器(60)的第六油口(6)，
    其中，第一油压低于第一阈值且第二油压低于第二阈值时两位四通阀(71)、第一两位三通阀(72)和第二两位三通阀(73)的阀芯均位于第一位置以在第一油口(1)和进油口之间、以及第三油口(3)和第四油口(4)之间建立通路以致动所述制动卡钳(51)，并在第五油口(5)和第六油口(6)之间、在第二油口(2)和所述第一卸油口之间建立通路以释放所述离合器(60)；
    第一油压高于第一阈值且第二油压低于第二阈值时两位四通阀(71)的阀芯位于第二位置、第一两位三通阀(72)和第二两位三通阀(73)的阀芯均位于第一位置以在第二油口(2)和进油口之间、在第五油口(5)和第六油口(6)之间建立通路以闭合所述离合器(60)，并在第一油口(1)和第一卸油口之间建立通路以及在第三油口(3)和第四油口(4)之间建立通路以释放所述制动卡钳(51)；
    第二油压高于第二阈值时第一两位三通阀(72)和第二两位三通阀(73)的阀芯均位于第二位置以在第四油口(4)和第二卸油口之间建立通路以释放所述制动卡钳(51)，以及在第六油口(6)和第三卸油口之间建立通路以释放所述离合器(60)。
  7. 如权利要求6所述的控制装置，其特征在于，所述两位四通阀(71)、第一两位三通阀(72)、第二两位三通阀(73)分别各自是液压控制的或者电信号控制的。
  8. 如权利要求6所述的控制装置，其特征在于，所述两位四通阀(71)、第一两位三通阀(72)、第二两位三通阀(73)分别各自设置有阻尼孔。
PCT/CN2022/115432 2021-09-23 2022-08-29 齿轮箱的控制装置 Ceased WO2023045706A1 (zh)

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