CN113153854A - Hybrid power hydraulic system and overhead working truck - Google Patents
Hybrid power hydraulic system and overhead working truck Download PDFInfo
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- CN113153854A CN113153854A CN202110484939.XA CN202110484939A CN113153854A CN 113153854 A CN113153854 A CN 113153854A CN 202110484939 A CN202110484939 A CN 202110484939A CN 113153854 A CN113153854 A CN 113153854A
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- 230000007246 mechanism Effects 0.000 claims description 10
- 238000010248 power generation Methods 0.000 abstract description 8
- 230000002035 prolonged effect Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 98
- 239000010720 hydraulic oil Substances 0.000 description 21
- 230000009471 action Effects 0.000 description 9
- 230000008859 change Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- 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
- B60K6/24—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 combustion engines
-
- 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
- B60K6/26—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 motors or the generators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/088—Characterised by the construction of the motor unit the motor using combined actuation, e.g. electric and fluid actuation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B2015/206—Combined actuation, e.g. electric and fluid actuated
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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- 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
Abstract
The invention discloses a hybrid power hydraulic system and an aerial working vehicle, comprising: the engine and the motor are separable and connectable, and the gear pump is connected with the motor; a high-pressure oil passage connected to a discharge port of the gear pump; an oil inlet of the proportional valve is connected with the high-pressure oil way; an oil inlet of the hydraulic control reversing valve is connected with the high-pressure oil path, and an oil return port of the hydraulic control reversing valve is connected with the low-pressure oil return path; the control oil way is arranged between a control oil port of the hydraulic control reversing valve and a working oil port of the proportional valve, the control oil way is provided with a one-way valve, and an oil inlet of the one-way valve is connected with the working oil port of the proportional valve; the switch valve is arranged between the high-pressure oil way and the oil inlet of the hydraulic control reversing valve, and is closed when the engine does not work; when the engine works, the switch valve is opened. The outlet pressure of the gear pump under the diesel mode is reduced under the condition that the electric mode is not influenced, the energy loss is reduced, the power generation rate is improved, and the service life of the gear pump is prolonged.
Description
Technical Field
The invention relates to the technical field of hydraulic systems, in particular to a hybrid power hydraulic system. In addition, the invention also relates to an aerial working vehicle comprising the hybrid power hydraulic system.
Background
In order to respond to the mainstream of energy-saving and environment-friendly development and meet the requirements of complex working conditions, hybrid power overhead working trucks appear in the market. The hybrid power aerial working truck adopts a gear pump hydraulic system with double power mixing of an engine and a motor, namely, the engine and the motor are connected in series through a clutch, the motor is connected with the gear pump, and the gear pump is driven to rotate through the rotation of the motor, so that a power oil source is provided for the whole hydraulic system. The hybrid power aerial working vehicle has two working modes, namely an electric mode and a diesel mode, and the two working modes are controlled to be switched by a swing switch (or a knob switch) on a control panel.
When the hybrid power overhead working truck is in an electric mode, the engine is disconnected from the motor, the motor rotates under the power supply of the battery, and then the gear pump is driven to rotate to supply hydraulic oil; at this time, the speed of each actuator in the hydraulic system is controlled by the rotation speed of the motor, that is, by controlling the rotation speed of the motor, the flow output by the gear pump is controlled, and further the operation speed of each actuator is controlled.
When the hybrid power aerial working vehicle is in a diesel mode, the engine is coupled with the motor through the clutch, at the moment, the motor is used as a generator, the engine is used as a power source to drive the generator (the motor) to generate electricity and drive the gear pump to rotate so as to supply hydraulic oil; under the working condition, the rotating speed of the engine is fixed, so that the flow output by the gear pump at the fixed rotating speed is fixed, and the flow required by the action of each actuating mechanism is inconsistent, so that the gear pump can only output the flow according to the maximum required flow. Therefore, the flow output by the gear pump is larger than the actual flow required by some actuating mechanisms, and the redundant flow forms high-pressure overflow, so that on one hand, the gear pump works in a high-pressure state for a long time, and the service life of the gear pump is greatly reduced; on the other hand, because the power required for driving the gear pump to rotate is in direct proportion to the pressure of the outlet of the gear pump, when the pressure of the outlet of the gear pump is higher, great power waste can be caused; further, when the hybrid aerial work vehicle is in a diesel mode, the engine rotates at a constant speed, redundant power is used for a generator (motor) to generate power, and a gear pump causes great energy waste, so that the efficiency of the engine for generating power is low.
In summary, those skilled in the art need to solve the above problems how to provide a hybrid hydraulic system to reduce the outlet pressure of a gear pump of an overhead working truck in a diesel mode without affecting the working condition of the overhead working truck in an electric mode.
Disclosure of Invention
Accordingly, an object of the present invention is to provide a hybrid hydraulic system, which can reduce the outlet pressure of a gear pump in a diesel mode without affecting the normal operation of an electric mode, thereby reducing energy loss, increasing power generation efficiency, and prolonging the service life of the gear pump.
The invention also aims to provide an overhead working truck comprising the hybrid power hydraulic system, which has the advantages of low energy loss, high power generation rate and long service life of the gear pump.
In order to achieve the above purpose, the invention provides the following technical scheme:
a hybrid hydraulic system comprising:
an engine, an electric motor, and a gear pump, the engine being separable from and connectable to the electric motor, the gear pump being connected to the electric motor;
a high-pressure oil passage connected to a discharge port of the gear pump;
an oil inlet of the proportional valve is connected with the high-pressure oil way;
an oil inlet of the hydraulic control reversing valve is connected with the high-pressure oil way, and an oil return port of the hydraulic control reversing valve is connected with a low-pressure oil return way;
the control oil way is arranged between a control oil port of the hydraulic control reversing valve and a working oil port of the proportional valve, the control oil way is provided with a one-way valve, and an oil inlet of the one-way valve is connected with the working oil port of the proportional valve;
the switch valve is arranged between the high-pressure oil path and an oil inlet of the hydraulic control reversing valve, and is closed when the engine does not work; when the engine works, the switch valve is opened.
Preferably, the valve is arranged between the control oil path and the low-pressure oil return path.
Preferably, the proportional valve, the one-way valve, the pilot operated directional valve and the switching valve are integrated in the same valve block.
Preferably, a working oil port of the proportional valve is connected with a load reversing valve, and the working oil port of the load reversing valve is connected with an execution mechanism.
Preferably, the load-reversing valve comprises a three-position, five-way reversing valve or a two-position, three-way reversing valve.
Preferably, the number of the proportional valves is at least two.
Preferably, the number of the load reversing valves connected to the working oil port of the single proportional valve is one or two.
Preferably, the safety overflow valve is arranged between the high-pressure oil path and the low-pressure oil return path.
Preferably, the switching valve is a solenoid valve.
An overhead working truck comprises a hybrid power hydraulic system, wherein the hybrid power hydraulic system is any one of the hybrid power hydraulic systems.
According to the hybrid power hydraulic system provided by the invention, in the electric mode, the engine is separated from the motor, the engine is in a non-working state, at the moment, the motor works under the condition of power supply of the battery, the gear pump is driven by the motor to rotate, and hydraulic oil is supplied to the high-pressure oil way. Under the working condition, the switch valve is closed, so that the high-pressure oil way is not communicated with the hydraulic control reversing valve; meanwhile, the opening of the proportional valve is in the maximum state, and the action speed of each actuating mechanism is controlled by controlling the rotating speed of the motor, namely, the power output by the motor is provided for the hydraulic system to drive each actuating mechanism to act at the maximum efficiency.
In the diesel mode, the engine is connected to the electric motor, which is used as a generator, and the gear pump is driven by the engine to rotate while the remaining power of the engine is used to charge the battery of the electric motor (generator). In the working mode, the switch valve is opened to communicate the high-pressure oil path with the hydraulic control reversing valve, so that the hydraulic oil in the high-pressure oil path can flow to the hydraulic control reversing valve; meanwhile, the opening size of the proportional valve is controlled by the current obtained by the proportional valve, so that the opening size of the proportional valve is controlled by controlling the current of the proportional valve, namely, the flow of the proportional valve is controlled, and the action speed of an actuating mechanism corresponding to the proportional valve is controlled; at this time, because the working oil port of the proportional valve is communicated with the control oil port of the pilot-controlled directional control valve through the control oil path, under the action of the one-way valve, the hydraulic oil flowing out of the working oil port of the proportional valve is introduced into the control oil port of the pilot-controlled directional control valve, so that the hydraulic oil of the high-pressure oil path is arranged on one side of the pilot-controlled directional control valve, and the hydraulic oil of the working oil port of the proportional valve is arranged on the other side of the pilot-controlled directional control valvefAre approximately equal. Compared with the prior art, the energy loss is effectively reduced, and the power P of the power generation part of the engine is improvedmAnd the whole system is more energy-saving. Further, because the pressure P of the gear pump discharge port is approximately equal to the actual load pressure, the gear of the gear pump can be prevented from working in a high-pressure state for a long time, and the service life of the gear pump can be prolonged.
The high-altitude operation vehicle provided by the invention comprises the hybrid power hydraulic system and has the same beneficial effects.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the provided drawings without creative efforts.
Fig. 1 is a control schematic diagram of a hybrid hydraulic system according to an embodiment of the present invention.
The reference numerals in fig. 1 are as follows:
the engine is 1, the motor is 2, the clutch is 3, the gear pump is 4, the high-pressure oil way is 5, the proportional valve is 6, the hydraulic control reversing valve is 7, the control oil way is 8, the low-pressure oil return way is 9, the switch valve is 10, the one-way valve is 11, the flow valve is 12, the load reversing valve is 13, the safety overflow valve is 14, and the execution mechanism function valve group is 15.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The core of the invention is to provide a hybrid power hydraulic system which can reduce the outlet pressure of a gear pump in a diesel mode and simultaneously does not influence the normal operation of an electric mode, thereby reducing energy loss, improving the power generation rate and prolonging the service life of the gear pump. The other core of the invention is to provide the high-altitude operation vehicle comprising the hybrid power hydraulic system, which has the advantages of low energy loss, high power generation rate and long service life of the gear pump.
Referring to fig. 1, a control schematic diagram of a hybrid hydraulic system according to an embodiment of the present invention is shown.
The invention provides a hybrid power hydraulic system which comprises an engine 1, a motor 2, a gear pump 4, a high-pressure oil way 5, a low-pressure oil return way 9, a control oil way 8, a proportional valve 6, a one-way valve 11, a hydraulic control reversing valve 7 and a switch valve 10.
Specifically, the engine 1 is connected to the motor 2, and the motor 2 is connected to the gear pump 4. It should be noted that the engine 1 and the motor 2 are connectable and disconnectable to switch between the electric mode and the diesel mode. Preferably, the engine 1 is connected with the motor 2 through a clutch 3, and when the clutch 3 is coupled, the connection of the engine 1 and the motor 2 is realized; when the clutch 3 is disengaged, the engine 1 is disengaged from the motor 2.
The high-pressure oil path 5 is connected with a discharge port of the gear pump 4, the gear pump 4 supplies hydraulic oil to the whole hybrid power hydraulic system, and the hydraulic oil supplied by the gear pump 4 is delivered to each load loop through the high-pressure oil path 5. Wherein, the oil inlet of the proportional valve 6 and the oil inlet of the hydraulic control reversing valve 7 are respectively connected with the high-pressure oil path 5. The low-pressure return line 9 is preferably connected to the oil tank for pressure relief return. The control oil path 8 is arranged between the working oil port of the proportional valve 6 and the control oil port of the hydraulic control reversing valve 7, the control oil path 8 is provided with a one-way valve 11, an oil inlet of the one-way valve 11 is connected with the working oil port of the proportional valve 6, namely, hydraulic oil can only enter the hydraulic control reversing valve 7 from the working oil port of the proportional valve 6 along the control oil path 8 and cannot flow reversely. The oil return port of the hydraulic control reversing valve 7 is connected with a low-pressure oil return path 9. The switch valve 10 is arranged between the high-pressure oil path 5 and an oil inlet of the hydraulic control reversing valve 7 and used for controlling the on-off of the oil path between the high-pressure oil path 5 and the hydraulic control reversing valve 7, and when the engine 1 does not work, the switch valve 10 is closed; when the engine 1 is operated, the on-off valve 10 is opened.
It can be understood that when the hybrid power hydraulic system is in the electric mode, the engine 1 is separated from the electric motor 2, the engine 1 is in the non-working state, and at this time, the electric motor 2 works under the condition of power supply of the battery, the gear pump 4 is driven by the electric motor 2 to rotate, and the high-pressure oil circuit 5 is supplied with hydraulic oil. Under the working condition, the switch valve 10 is closed, so that the high-pressure oil path 5 is not communicated with the hydraulic control reversing valve 7; meanwhile, the opening of the proportional valve 6 is in the maximum state, and the action speed of each actuator is controlled by controlling the rotating speed of the motor 2, namely, the power output by the motor 2 is provided for the hydraulic system with the maximum efficiency to drive each actuator to act.
When the hybrid power hydraulic system needs to be in a diesel mode, the engine 1 is connected with the motor 2, the motor 2 is used as a generator, the engine 1 works, the gear pump 4 is driven to rotate by the motor 2, and meanwhile, the residual power of the engine 1 is used for charging a battery of the motor 2 (generator). In this working mode, the switching valve 10 is opened to communicate the high-pressure oil path 5 with the pilot-operated directional control valve 7, so that the hydraulic oil in the high-pressure oil path 5 can flow to the pilot-operated directional control valve 7; meanwhile, the opening size of the proportional valve 6 is controlled by the current obtained by the proportional valve 6, so that the opening size of the proportional valve 6 is controlled by controlling the current of the proportional valve 6, that is, the flow of the proportional valve 6 is controlled, and the action speed of an actuating mechanism corresponding to the proportional valve 6 is controlled; at this time, since the working oil port of the proportional valve 6 is communicated with the control oil port of the pilot operated directional control valve 7 through the control oil path 8, under the action of the check valve 11, the hydraulic oil flowing out from the working oil port of the proportional valve 6 is introduced into the control oil port of the pilot operated directional control valve 7, so that one side of the pilot operated directional control valve 7 is the hydraulic oil of the high-pressure oil path 5, and the other side of the pilot operated directional control valve 7 is the working oil port hydraulic oil of the proportional valve 6, and at this time, the excess flow of the hydraulic oil of the high-pressure oil path 5 minus the hydraulic oil of the proportional valve 6 can be discharged to the low-pressure oil return path 9 through the oil return port of the pilot operated directional control valve 7.
It will be appreciated by those skilled in the art that in the diesel mode, the power P required to drive the gear pump 4 in rotation isPComprises the following steps:
where Q is the flow rate of the discharge port of the gear pump 4, P is the pressure of the discharge port of the gear pump 4, and η is the efficiency of the gear pump 4. Since the engine 1 rotates at a constant rotation speed in the diesel mode, that is, the rotation speed n of the engine 1 is constant and the displacement V of the gear pump 4 is constant, the flow rate Q of the discharge port of the gear pump 4 is constant, where Q is equal to nV. Meanwhile, η is a constant. Thus, the power P required to drive the gear pump 4 in rotationPProportional to the pressure P at the discharge port of the gear pump 4.
As can be seen from the above, in the diesel mode, the on-off valve 10 is opened, so that the pilot-operated directional control valve 7 is communicated with the high-pressure oil path 5, and at the same time, the hydraulic oil of the working oil port of the proportional valve 6 flows into the control oil port of the pilot-operated directional control valve 7 through the control oil path 8 under the action of the check valve 11, that is, the actual load pressure is fed back to the pilot-operated directional control valve 7 through the control oil path 8, so that the excess flow except for the flow required by the load discharged from the discharge port of the gear pump 4 can be discharged to the low-pressure oil return path 9 through the pilot-operated directional control valve 7. It can be seen that the pressure P at the discharge port of the gear pump 4 and the load pressure P are made to be negligible in terms of pressure loss such as line pressure lossfApproximately equal, i.e. P ≈ PfTherefore, the power P required to drive the gear pump 4 to rotate can be approximatedPComprises the following steps:
compared with the prior art, under the diesel mode, no liquid control switching-over valve 7 carries out the pressure release, but utilizes the overflow valve to carry out the pressure release, that is, gear pump 4 is with the biggest demand flow discharge hydraulic oil of load for the flow that gear pump 4 discharge port was discharged is greater than the required actual flow of some actuating mechanism, and this just leads to unnecessary flow to form the pressure-holding at the discharge port of gear pump 4, and the overflow valve is opened after pressure risees to the setting value of overflow valve, makes unnecessary flow let out to low pressure oil return circuit 9 from the overflow valve. It follows that this results in the pressure P at the discharge of the gear pump 4 being much greater than the pressure P required for the actual loadfSo that the energy loss is large.
Therefore, the hybrid power hydraulic system provided by the invention effectively reduces energy loss.
In addition, since the surplus power of the engine 1 is used to charge the motor 2 (used as a generator) in the diesel mode, the power supplied from the engine 1 is referred to herein as power for generating power for the motor 2 (generator)Part of power being PmThen P ism＝(PW-PP)*ηw. Wherein, PWTotal power output from the engine 1, PPThe power required for driving the gear pump 4 to rotate among the power output from the engine 1, ηwFor transmission efficiency. From the above description, the hybrid power hydraulic system provided by the invention effectively reduces the power P required for driving the gear pump 4 to rotatePAccordingly, the power P of the portion of the engine 1 for power generation is increased accordinglymAnd the whole system is more energy-saving.
Further, since the pressure P at the discharge port of the gear pump 4 is substantially equal to the actual load pressure, the gears of the gear pump 4 can be prevented from operating in a high-pressure state for a long time, and the service life of the gear pump 4 can be prolonged. Moreover, as is known, when the overflow valve is opened and is in a high-pressure overflow state, the oil temperature of the hydraulic system can be rapidly increased, so that the hybrid power hydraulic system provided by the invention also effectively avoids the phenomenon of oil temperature increase caused by the overflow valve being opened for a long time, and avoids the adverse effect of the temperature rise of the hydraulic oil on the hydraulic system.
In addition, in order to make the control oil path 8 recover to the initial state after each stop of the actuator and avoid the pressure build-up in the control oil path 8 from affecting the next load operation, on the basis of the above embodiment, the hydraulic control system further includes a flow valve 12 disposed between the control oil path 8 and the low-pressure return oil path 9. That is, after the actuator stops operating, the pressure of the pilot oil path 8 can be discharged from the flow valve 12 to the low-pressure return oil path 9, so that the pilot oil path 8 is restored to the original state, and the normal operation of the pilot-operated directional control valve 7 is ensured.
In view of installation convenience, on the basis of the above-described embodiment, the proportional valve 6, the check valve 11, the pilot-operated directional valve 7, and the switching valve 10 are integrated in the same valve block, forming the actuator function valve group 15.
That is, in the present embodiment, the proportional valve 6, the check valve 11, the pilot operated directional control valve 7 and the switch valve 10 are integrated into a whole to form an integrated valve set, which is convenient for one-time installation. Meanwhile, the universality of the electric mode and the diesel mode in the same valve group can be realized through the combined use of the switch valve 10, the hydraulic control reversing valve 7 and the control oil way 8 for load feedback.
When the hybrid hydraulic system further includes a flow valve 12, the proportional valve 6, the check valve 11, the pilot-controlled directional valve 7, and the switching valve 10 may be integrated into a whole to form an integrated valve set.
In order to control the action direction of the actuator, on the basis of the above embodiment, as shown in fig. 1, the working oil port of the proportional valve 6 is connected with the load-switching valve 13, and the control oil port of the load-switching valve 13 is connected with the actuator.
That is, in this embodiment, the hydraulic oil flowing out of the proportional valve 6 enters the load switching valve 13, and the load switching valve 13 is controlled to switch the direction of the actuator to change the operation direction, thereby flexibly adjusting the operation of the load.
It should be noted that the specific type of the load-reversing valve 13 is not limited in this embodiment, and preferably, on the basis of the above-mentioned embodiment, the load-reversing valve 13 includes a three-position five-way reversing valve or a two-position three-way reversing valve.
In addition, in each of the above embodiments, the specific number of the comparative proportional valves 6 is not limited, and preferably, the number of the proportional valves 6 is at least two based on the above embodiments. For example, the number of the proportional valves 6 may preferably be four.
It will be appreciated that the greater the number of proportional valves 6, the more actuators there are to be, and the more actuators can be made to move independently.
Further, on the basis of the above embodiment, the number of the load reversing valves 13 connected to the working oil ports of the single proportional valve 6 is one or two.
That is, in this embodiment, the direction change of one actuator can be realized by one load changeover valve 13, and the direction change of one actuator can also be realized by two load changeover valves 13.
As shown in fig. 1, the working oil port of one proportional valve 6 may be connected to one three-position five-way directional valve, and the working oil port of one proportional valve 6 may also be connected to two-position three-way directional valves.
Further, in view of safety, the above embodiment further includes a safety relief valve 14 provided between the high-pressure oil passage 5 and the low-pressure return oil passage 9.
That is, when the pressure at the discharge port of the gear pump 4 rises to the set value of the safety relief valve 14, the safety relief valve 14 opens to perform the function of pressure relief, so as to ensure the safety of the hybrid hydraulic system.
It should be noted that, in the above embodiments, the specific type of the on-off valve 10 is not limited, and preferably, the on-off valve 10 is a solenoid valve, that is, the solenoid valve is controlled to be opened or closed by controlling whether the solenoid valve is powered. That is, in the motoring mode, the solenoid valve is not energized; in the diesel mode, the electromagnetic valve is electrified and opened.
Further, the load reversing valve 13 and the relief valve 14 can also be integrated in the same valve block formed by the proportional valve 6, the pilot operated reversing valve 7, the switch valve 10 and the flow valve 12.
In addition to the hybrid hydraulic system, the invention further provides an aerial platform including the hybrid hydraulic system disclosed in the above embodiments, and the structure of other parts of the aerial platform is referred to the prior art and is not described herein again.
The high-altitude operation vehicle is characterized in that the hybrid power hydraulic system disclosed by any one of the embodiments is adopted to achieve the purposes of reducing energy loss, improving power generation rate and prolonging the service life of the gear pump 4.
The embodiments are described in a progressive manner in the specification, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The hybrid power hydraulic system and the overhead working truck provided by the invention are described in detail above. The principles and embodiments of the present invention are explained herein using specific examples, which are presented only to assist in understanding the method and its core concepts. It should be noted that, for those skilled in the art, it is possible to make various improvements and modifications to the present invention without departing from the principle of the present invention, and those improvements and modifications also fall within the scope of the claims of the present invention.
Claims (10)
1. A hybrid hydraulic system, comprising:
the engine (1), the electric motor (2) and the gear pump (4), wherein the engine (1) and the electric motor (2) are separable and connectable, and the gear pump (4) is connected with the electric motor (2);
a high-pressure oil passage (5) connected to a discharge port of the gear pump (4);
an oil inlet of the proportional valve (6) is connected with the high-pressure oil way (5);
an oil inlet of the hydraulic control reversing valve (7) is connected with the high-pressure oil way (5), and an oil return port of the hydraulic control reversing valve (7) is connected with a low-pressure oil return way (9);
the control oil way (8) is arranged between a control oil port of the hydraulic control reversing valve (7) and a working oil port of the proportional valve (6), the control oil way (8) is provided with a one-way valve (11), and an oil inlet of the one-way valve (11) is connected with the working oil port of the proportional valve (6);
the switching valve (10) is arranged between the high-pressure oil path (5) and an oil inlet of the hydraulic control reversing valve (7), and when the engine (1) does not work, the switching valve (10) is closed; when the engine (1) works, the switch valve (10) is opened.
2. Hybrid hydraulic system according to claim 1, characterized in that it further comprises a flow valve (12) arranged between the control oil circuit (8) and the low pressure return (9).
3. Hybrid hydraulic system according to claim 1 or 2, characterized in that the proportional valve (6), the non-return valve (11), the pilot-operated directional valve (7) and the on-off valve (10) are integrated in one and the same valve block.
4. The hybrid hydraulic system according to claim 3, characterized in that a control oil port of the proportional valve (6) is connected with a load reversing valve (13), and the control oil port of the load reversing valve (13) is connected with an actuating mechanism.
5. Hybrid hydraulic system according to claim 4, characterized in that the load-reversing valve (13) comprises a three-position, five-way reversing valve or a two-position, three-way reversing valve.
6. Hybrid hydraulic system according to claim 4, characterized in that the number of proportional valves (6) is at least two.
7. Hybrid hydraulic system according to claim 6, characterized in that the number of load-reversing valves (13) to which the working ports of a single proportional valve (6) are connected is one or two.
8. A hybrid hydraulic system according to claim 3, characterized by further comprising a safety spill valve (14) provided between the high pressure oil circuit (5) and the low pressure return oil circuit (9).
9. Hybrid hydraulic system according to claim 3, characterized in that the on-off valve (10) is a solenoid valve.
10. An aerial lift truck comprising a hybrid hydraulic system, wherein the hybrid hydraulic system is as claimed in any one of claims 1 to 9.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110484939.XA CN113153854A (en) | 2021-04-30 | 2021-04-30 | Hybrid power hydraulic system and overhead working truck |
| PCT/CN2021/139057 WO2022227621A1 (en) | 2021-04-30 | 2021-12-17 | Hybrid power hydraulic system and aerial platform truck |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110484939.XA CN113153854A (en) | 2021-04-30 | 2021-04-30 | Hybrid power hydraulic system and overhead working truck |
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| Publication Number | Publication Date |
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| CN113153854A true CN113153854A (en) | 2021-07-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110484939.XA Pending CN113153854A (en) | 2021-04-30 | 2021-04-30 | Hybrid power hydraulic system and overhead working truck |
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| Country | Link |
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| CN (1) | CN113153854A (en) |
| WO (1) | WO2022227621A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022227621A1 (en) * | 2021-04-30 | 2022-11-03 | 湖南星邦智能装备股份有限公司 | Hybrid power hydraulic system and aerial platform truck |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11351202A (en) * | 1998-06-10 | 1999-12-24 | Shin Caterpillar Mitsubishi Ltd | Load sensing hydraulic circuit |
| CN201574992U (en) * | 2009-11-10 | 2010-09-08 | 三一重工股份有限公司 | Multi-way valve, hydraulic device and concrete pump vehicle |
| CN102434502B (en) * | 2011-12-23 | 2014-08-13 | 四川大学 | Frequency-conversion pump controlled steering hydraulic system for loader |
| CN103244496B (en) * | 2013-05-13 | 2016-02-10 | 三一汽车起重机械有限公司 | Rotary control valve group, revolution hydraulic control system and hoist |
| CN103671335B (en) * | 2013-12-19 | 2015-12-02 | 杭叉集团股份有限公司 | Load-sensitive electric proportional multi-loop valve |
| CN112591681A (en) * | 2020-12-24 | 2021-04-02 | 杭叉集团股份有限公司 | Portal rises to rise and hydraulic circuit that potential energy was retrieved |
| CN112607673A (en) * | 2020-12-24 | 2021-04-06 | 杭叉集团股份有限公司 | Hydraulic oil way for lifting and potential energy recovery of portal frame of electric empty-box forklift |
| CN113153854A (en) * | 2021-04-30 | 2021-07-23 | 湖南星邦智能装备股份有限公司 | Hybrid power hydraulic system and overhead working truck |
| CN214533782U (en) * | 2021-04-30 | 2021-10-29 | 湖南星邦智能装备股份有限公司 | Hybrid power hydraulic system and overhead working truck |
-
2021
- 2021-04-30 CN CN202110484939.XA patent/CN113153854A/en active Pending
- 2021-12-17 WO PCT/CN2021/139057 patent/WO2022227621A1/en unknown
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022227621A1 (en) * | 2021-04-30 | 2022-11-03 | 湖南星邦智能装备股份有限公司 | Hybrid power hydraulic system and aerial platform truck |
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| WO2022227621A1 (en) | 2022-11-03 |
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