CN105715595A - Air pressure loading oil supply device for experiment bench for properties of piston cooling nozzles - Google Patents
Air pressure loading oil supply device for experiment bench for properties of piston cooling nozzles Download PDFInfo
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- CN105715595A CN105715595A CN201610226598.5A CN201610226598A CN105715595A CN 105715595 A CN105715595 A CN 105715595A CN 201610226598 A CN201610226598 A CN 201610226598A CN 105715595 A CN105715595 A CN 105715595A
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- piston cooling
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
Abstract
The invention discloses an air pressure loading oil supply device for an experiment bench for properties of piston cooling nozzles. An oil supply valve is mounted on an oil supply pipe between the middle lower part of an inflation oil tank and an oil inlet of the piston cooling nozzles; an oil return tank is mounted under of a jet opening of each of the piston cooling nozzles, and is positioned above the inflation oil tank; an oil return valve is mounted on an oil return pipe between the oil return tank and the inflation oil tank; an air inlet valve is mounted on an air pipe between the middle upper part of the inflation oil tank and an air outlet of an air pressure regulator; an exhaust pipe is in communicating connection to the air pipe between the air inlet valve and the inflation oil tank, and an exhaust valve is mounted on the exhaust pipe; an air inlet of the air pressure regulator is connected with a high pressure air source. The air pressure loading oil supply device disclosed by the invention is used for providing engine oil for the piston cooling nozzles, conventional electric motors and conventional compressors are not used, the engine oil is not heated, and the control can be precise; experiment results are accurate, and the air pressure loading oil supply device is energy-saving, and environmentally-friendly.
Description
Technical field
The present invention relates to the adnexa of a kind of piston cooling nozzle performance test stand, particularly relate to a kind of air pressure-loading fueller for piston cooling nozzle performance test stand.
Background technology
Piston cooling nozzle (i.e. PCN) is as the important component part of automobile engine, and the lubrication of engine movements piston, cooling effect are had extremely important effect by the quality of its performance.
Piston cooling nozzle is made up of nozzle body and check valve, and based on the multiformity of automobile engine specification, model, the specification of piston cooling nozzle, model are also a lot, but its version is substantially similar.
The test of the switching characteristic of piston cooling nozzle, discharge characteristic is exfactory inspection project, it is desirable to all products that dispatch from the factory are carried out 100% one hundred percent inspection test.The specification of piston cooling nozzle, model are different, its technical requirement difference to some extent.
Piston cooling nozzle needs the technical specification parameter of detection to include:
A) pressure is opened: flow rises to charge oil pressure value during setting from low to high.As: 30mL, 200kPa ± 20kPa.
B) closing presure: flow is dropped to charge oil pressure value during setting on earth by height.Such as: 30mL, more than 170kPa.
C) leakage flow: open flow value during front specified pressure value.Such as: 150kPa, less than 0.1L/min.
D) dredge oil amount: flow rises to flow value during authorized pressure value from low to high.As: 400kPa, 1.15L/min～1.55L/min.
E) target practice position: when charge oil pressure reaches draining flow rate test force value, the position that oil bundle injection is hit.Such as: 400kPa, spray in appointment region flow be more than or equal to 90%.
When piston cooling nozzle carries out switching characteristic, discharge characteristic detection, it is desirable to automobile engine oil for detection medium, and require to provide charge oil pressure by following several phase sequence:
A) aerofluxus: charge oil pressure is quickly increased on unlatching pressure, to discharge the air in oil feed line and piston cooling nozzle.
B) low speed blood pressure lowering: charge oil pressure is reduced to below 100kPa by low speed, tests closing presure, leakage flow in this stage.
C) low speed boosting: charge oil pressure is increased to slightly above opening pressure by low speed, and pressure is opened in test in this stage.
D) rapid pressure: be quickly increased to slightly above dredge oil amount, target practice position measurement pressure by charge oil pressure, tests dredge oil amount, target practice position in this stage.
E) reduction of blood pressure in high-speed: quickly charge oil pressure is dropped to zero.
Therefore, when carrying out the switching characteristic of piston cooling nozzle, discharge characteristic detection, adjustable pressure fueller is necessary.
By controlling the charge oil pressure of fueller, piston cooling nozzle is carried out pressure scanning, test pressure with pressure transducer, detect flow with flow transducer, its pressure of synchronization gain, flow and target practice position measurement curve, extract each feature physical quantity from curve.Shown in Fig. 1 be current germany volkswagen piston cooling nozzle performance test stand provide pressure, traffic characteristic curve.
Traditional adjustable pressure fueller can be summarized as following 4 kinds of structures:
Traditional structure one: as in figure 2 it is shown, adopt meter in pressure regulation test oil circuit: by the aperture of manual adjustment ball valve 2, it is achieved the adjustment of charge oil pressure；Fig. 2 also show high-pressure pump 1, flow transducer 3 (in order to gather data, otherwise available stream scale), pressure transducer 4 is (in order to gather data, otherwise available pressure table) and piston cooling nozzle 5, ball valve 2 is the critical piece of the engine oil pressure changing supply piston cooling nozzle 5, and flow transducer 3, pressure transducer 4 are used as to observe understands real-time traffic and oil pressure.
Traditional structure two: as it is shown on figure 3, adopt by-pass throttle pressure regulation test oil circuit: by program control adjustment rapid switching valve 7, changes bypass flow size, and utilizes flow speed control valve 6 to change bypass flow velocity, it is achieved the adjustment of charge oil pressure；High-pressure pump 1 in Fig. 3, flow transducer 3, pressure transducer 4 are identical with Fig. 2 with piston cooling nozzle 5.
Traditional structure three: as shown in Figure 4, adopts meter in pressure regulation test oil circuit: by the aperture of program control adjustment proportioning valve 9, and utilizes choke valve 8 to change bypass flow velocity, it is achieved the adjustment of charge oil pressure.
Traditional structure four: as it is shown in figure 5, drive high-pressure pump operation different from structure one, structure two, structure three common electric machine, it adopts frequency conversion motor 10 to drive high-pressure pump 1 to run, by the rotating speed of programme-control frequency conversion motor 10, it is achieved the adjustment of charge oil pressure.
The defect of above-mentioned Conventional tunable forced feed device is as follows:
Structure one needs to regulate manually the aperture of ball valve, and the detection efficiency of experimental stand is low, and the labor intensity of operator is big, and the confidence level of testing result depends on operant skill and the responsibility of operator.
There is 1 common shortcoming in structure one, structure two, structure three, structure four: due to the heating of motor, oil pump, electromagnetic valve etc., detection medium machine oil can produce bigger temperature rise.
In order to solve the temperature rise of detection medium machine oil, it is necessary to take constant temperature measures.
Generally adopt following 2 kinds of constant temperature measures:
A) constant temperature measures one: adopt the constant-temperature oil tank with refrigerating function.
B) constant temperature measures two: adopt electrical heating constant-temperature oil tank.
For constant temperature measures one: do not allow quick starting and stopping switch operating due to refrigeration compressor, constant-temperature oil tank needs to have refrigeration simultaneously, heat 2 cover systems, refrigeration system is run continuously, by the heating power of fuel temperature measurement feedback control heating system, it is achieved the thermostatic control of oil temperature；The power consumption cost that its shortcoming is experimental stand operation can be higher, and refrigeration system also can produce bigger operation noise.
For constant temperature measures two: detection medium oil temperature is set higher than ambient temperature, such as 50 DEG C, and install wind-blowing heat-dissipating function additional, by the heating power of fuel temperature measurement feedback control heating system, it is achieved the thermostatic control of oil temperature；The power consumption cost that its shortcoming is experimental stand operation can be higher, need to prepare special hybrid detection medium machine oil to reach the viscosity coefficient needed, heating high temperature can cause medium engine oil viscosity coefficient to change and carbonization continuously, change detection medium machine oil with needing frequent, the operating cost of experimental stand is higher.
Summary of the invention
The purpose of the present invention is that provides a kind of machine oil without the low air pressure-loading fueller for piston cooling nozzle performance test stand of temperature rise and noise to solve the problems referred to above.
The present invention is achieved through the following technical solutions above-mentioned purpose:
A kind of air pressure-loading fueller for piston cooling nozzle performance test stand, including air tank, oil-supply valve, oil return valve, oil return fuel tank, air intake valve, drain tap, barostat and high-pressure air source, fuel feed pump between middle and lower part and the oil-in of described piston cooling nozzle of described air tank is provided with described oil-supply valve, described oil return fuel tank is installed on the lower section of the jet of described piston cooling nozzle and is positioned at the top of described air tank, described oil return valve is installed on the oil return pipe between described oil return fuel tank and described air tank, trachea between middle and upper part and the gas outlet of described barostat of described air tank is provided with described air intake valve, trachea between described air intake valve and described air tank interlinks and is connected to exhaustor, described drain tap is installed on described exhaustor, the air inlet of described barostat is connected with described high-pressure air source.
In said structure, air tank, air intake valve, drain tap, barostat and high-pressure air source constitute gas control equipment, for in air tank gas pressure be controlled, thus realizing the control to the engine oil pressure in air tank, and then realize the control to the engine oil pressure in piston cooling nozzle；Air tank, oil-supply valve, oil return valve and oil return fuel tank then constitute machine oil and control device, for providing machine oil to piston cooling nozzle and reclaiming the machine oil of ejection；Air tank is then gas circuit and oil circuit is mutually related tie, and the pressure of bottom machine oil is made machine oil enter piston cooling nozzle for testing by the gas in air tank internal upper part space；Owing to air has compressibility, so the machine oil output pressure of air tank will not produce to suddenly change, but a stable progressive formation, the output rising of charge oil pressure, fall off rate depend on the flow velocity that air injects, discharges；Barostat adopts the source of the gas treatment element of maturation application, and the gas pressure of the outer air supply source of 8bar is adjusted to 6.5bar on the one hand, can spray a small amount of mist of oil on the other hand, have lubricating function while supply.
Two sets that described air intake valve and described drain tap are respectively connected in parallel with each other；It is thus possible to realize the low rate to air inlet and aerofluxus and the control of two-forty better.
As preferably, often overlap described air intake valve and include air inlet electromagnetic valve and flow inlet angle seat valve, often overlap described drain tap and include exhaust solenoid valve and aerofluxus angle pedestal valve, described oil-supply valve includes for solenoid and delivery angle seat valve, described oil return valve includes oil return solenoid valve and oil return angle pedestal valve, the control input of described air inlet electromagnetic valve, the control input of described exhaust solenoid valve, the described input that controls controlling input and described oil return solenoid valve for solenoid is connected with the control output end of controller respectively, the air inlet of described air inlet electromagnetic valve, the air inlet of described exhaust solenoid valve, the air inlet of the described air inlet supplying solenoid and described oil return solenoid valve is connected with the gas outlet of described barostat respectively, the gas outlet of described air inlet electromagnetic valve is connected with the control end of described flow inlet angle seat valve, the gas outlet of described exhaust solenoid valve is connected with the control end of described aerofluxus angle pedestal valve, the described gas outlet for solenoid is connected with the control end of described delivery angle seat valve, the gas outlet of described oil return solenoid valve is connected with the control end of described oil return angle pedestal valve, described flow inlet angle seat valve is installed on the trachea between described air tank and described barostat, described aerofluxus angle pedestal valve is installed on described exhaustor, described delivery angle seat valve is installed on the fuel feed pump between described air tank and described piston cooling nozzle, described oil return angle pedestal valve is installed on the oil return pipe between described oil return fuel tank and described air tank.
In said structure, corresponding pneumatic angle pedestal valve is controlled by each electromagnetic valve, corresponding gas or oil flow rate is controlled again by angle pedestal valve, not only it is easy to control, and it can be avoided that adopt electromagnetic valve directly control flow produce gas or machine oil be heated heat up problem, ensure that gas and machine oil are temperature-resistant in transmitting procedure, thus being beneficial to the engine oil pressure more accurately controlled needed for piston cooling nozzle and obtaining experimental result more accurately.
In order to realize air inlet and gas exhaust inspecting better, often overlap on the trachea at described air intake valve place and often overlap on the exhaustor at described drain tap place and be connected in series with choke valve respectively.
In order to reduce exhaust noise, the steam vent of each described air inlet electromagnetic valve, the steam vent of each described exhaust solenoid valve, the described confession steam vent of solenoid, the steam vent of described oil return solenoid valve and the air vent of each described aerofluxus angle pedestal valve are separately installed with the deafener for eliminating exhaust sound.
For the ease of obtaining real-time charge oil pressure and the flow parameter of piston cooling nozzle more accurately, oil pipe between middle and lower part and the oil-in of described piston cooling nozzle of described air tank is also equipped with flow transducer and pressure transducer, the signal output part of described flow transducer and the signal output part of pressure transducer be connected with the signal input part of described controller respectively.
Specifically, described air inlet electromagnetic valve, described exhaust solenoid valve, described confession solenoid and described oil return solenoid valve are three mouthfuls of two electromagnetic valves.Three mouthfuls of two electromagnetic valves are the solenoid directional control valves of a kind of ripe application, traditional using method is from A mouth air inlet, to P mouth, R mouth switching supply under Electromagnetic Control, but the use of three mouthfuls of two electromagnetic valves is adopted following optimal way by the present invention: P mouth connects barostat as air inlet, R mouth runs in the deafener of gas, and A mouth is as gas outlet joint angle seat valve.So, angle pedestal valve is in normally off, and three mouthfuls two have only between electromagnetic valve with angle pedestal valve be connected one with pipeline, when three mouthfuls of two electromagnetic valves cut off supply, utilizes the spring automatic reset of angle pedestal valve.
Preferably, the space above machine oil in described air tank accounts for 1/to three/4th of the whole space in described air tank, above described air tank is positioned at the machine oil of described air tank with the position that described barostat is connected.
The beneficial effects of the present invention is:
Adopting air pressure-loading fueller of the present invention to provide machine oil for piston cooling nozzle, without conventional motors, compressor, machine oil, without temperature rise, controls more accurate, and experimental result is more accurate, more energy-conservation and environmental protection；Concrete advantage is as follows:
1, detection medium machine oil is without temperature rise, adopts room temperature detection medium machine oil, it is not necessary to configuring special hybrid detection medium machine oil to reach the viscosity coefficient needed, medium machine oil is relatively inexpensive.
2, without taking constant temperature measures, it is possible to decrease equipment runs power consumption cost.
3, without taking constant temperature measures, medium engine oil viscosity coefficient is relatively stable and will not produce carbonization, thus the frequency changing detection medium machine oil can be reduced, it is possible to decrease the operating cost of experimental stand.
4, experimental stand compressor-free, motor, detection operating environment noise level low.
5, experimental stand compressor-free, motor, the nearly source strength electromagnetic interference of experimental stand reduces, and test curve interference burr improves, and the repeatability of test result and repeatability evaluation index increase.
Accompanying drawing explanation
Fig. 1 be the piston cooling nozzle performance test stand of current germany volkswagen company provide pressure, traffic characteristic curve synoptic diagram；
Fig. 2 is the schematic diagram of the traditional structure one of adjustable pressure fueller；
Fig. 3 is the schematic diagram of the traditional structure two of adjustable pressure fueller；
Fig. 4 is the schematic diagram of the traditional structure three of adjustable pressure fueller；
Fig. 5 is the schematic diagram of the traditional structure four of adjustable pressure fueller；
Fig. 6 is the schematic diagram of the air pressure-loading fueller for piston cooling nozzle performance test stand of the present invention；
Fig. 7 be air pressure-loading fueller of the present invention for piston cooling nozzle performance test stand time main TV structure schematic diagram；
Fig. 8 be air pressure-loading fueller of the present invention for piston cooling nozzle performance test stand time right TV structure schematic diagram；
The pressure of gained, flow time dependent curve synoptic diagram when Fig. 9 is air pressure-loading fueller of the present invention application.
Detailed description of the invention
Below in conjunction with accompanying drawing, the invention will be further described:
As shown in Figure 6, air pressure-loading fueller for piston cooling nozzle performance test stand of the present invention, including air tank 13, oil-supply valve, oil return valve, oil return fuel tank 11, air intake valve, drain tap, barostat 16 and high-pressure air source 15, described air intake valve includes the first air inlet electromagnetic valve 22, first flow inlet angle seat valve 18, second air inlet electromagnetic valve 20, second flow inlet angle seat valve 21, described drain tap includes the first exhaust solenoid valve 31, first row air horn seat valve 17, second exhaust solenoid valve 33, second row air horn seat valve 19, described oil-supply valve includes for solenoid 34 and delivery angle seat valve 23, described oil return valve includes oil return solenoid valve 32 and oil return angle pedestal valve 12, the space above machine oil in air tank 13 accounts for 1/to three/4th of the whole space in air tank 13, general volume is 10 liters, fuel feed pump 28 between middle and lower part and the oil-in of piston cooling nozzle 5 of air tank 13 is provided with delivery angle seat valve 23, flow transducer 3 and pressure transducer 4, oil return fuel tank 11 is installed on the lower section of the jet of piston cooling nozzle 5 and is positioned at the top of air tank 13, oil return angle pedestal valve 12 is installed on the oil return pipe 29 between oil return fuel tank 11 and air tank 13, the trachea 30 between position and the gas outlet of barostat 16 above the upper position of air tank 13 machine oil in air tank 13 is provided with the first flow inlet angle seat valve 18 and the second flow inlet angle seat valve 21 being connected in parallel, trachea between first flow inlet angle seat valve 18 and the second flow inlet angle seat valve 21 and air tank 13 interlinks and is connected to two exhaustors (unmarked in figure), first row air horn seat valve 17 and second row air horn seat valve 19 are respectively arranged on two exhaustors, the air inlet of barostat 16 is connected with high-pressure air source 15, the signal output part of flow transducer 3 and the signal output part of pressure transducer 4 are connected with the signal input part of controller (not shown) respectively, the control input of the first air inlet electromagnetic valve 22, the control input of the second air inlet electromagnetic valve 20, the control input of the first exhaust solenoid valve 31, the control input of the second exhaust solenoid valve 33, the input that controls controlling input and oil return solenoid valve 32 for solenoid 34 is connected with the control output end of controller respectively, the air inlet of the first air inlet electromagnetic valve 22, the air inlet of the second air inlet electromagnetic valve 20, the air inlet of the first exhaust solenoid valve 31, the air inlet of the second exhaust solenoid valve 33, it is connected with the gas outlet of barostat 16 respectively for the air inlet of solenoid 34 and the air inlet of oil return solenoid valve 32, 22 gas outlets of the first air inlet electromagnetic valve are connected with the control end of the first flow inlet angle seat valve 18, the gas outlet of the second air inlet electromagnetic valve 20 is connected with the control end of the second flow inlet angle seat valve 21, the gas outlet of the first exhaust solenoid valve 31 is connected with the control end of first row air horn seat valve 17, the gas outlet of the second exhaust solenoid valve 33 is connected with the control end of second row air horn seat valve 19, gas outlet for solenoid 34 is connected with the control end of delivery angle seat valve 23, the gas outlet of oil return solenoid valve 32 is connected with the control end of oil return angle pedestal valve 12, first flow inlet angle seat valve 18, on the trachea at the second flow inlet angle seat valve 21 place and first row air horn seat valve 17, the exhaustor at second row air horn seat valve 19 place is connected in series with choke valve 8 respectively, the steam vent of the first air inlet electromagnetic valve 22, the steam vent of the second air inlet electromagnetic valve 20, the steam vent of the first exhaust solenoid valve 31, the steam vent of the second exhaust solenoid valve 33, steam vent for solenoid 34, the steam vent of oil return solenoid valve 32, the air vent of first row air horn seat valve 17 and the air vent of second row air horn seat valve 19 are separately installed with the deafener 14 for eliminating exhaust sound,
Above-mentioned first air inlet electromagnetic valve the 22, second air inlet electromagnetic valve the 20, first exhaust solenoid valve the 31, second exhaust solenoid valve 33, confession solenoid 34 and oil return solenoid valve 32 are three mouthfuls of two electromagnetic valves.Three mouthfuls of two electromagnetic valves are the solenoid directional control valves of a kind of ripe application, traditional using method is from A mouth air inlet, to P mouth, R mouth switching supply under Electromagnetic Control, but the use of three mouthfuls of two electromagnetic valves is adopted following optimal way by the present invention: P mouth connects barostat 16 as air inlet, R mouth run in gas deafener 14, A mouth as gas outlet connect each angle pedestal valve.So, each angle pedestal valve is in normally off, has only to connect one with corresponding pipeline, when three mouthfuls of two electromagnetic valves cut off supply, utilize the spring automatic reset of each angle pedestal valve between three mouthfuls of two electromagnetic valves and each angle pedestal valve.
As shown in Figure 7 and Figure 8, during application, each parts of this air pressure-loading fueller are installed on experimental stand 26, piston cooling nozzle 5 is installed on the fixture 25 on experimental stand 26, in Fig. 8 24 represent all electromagnetic valves being installed on experimental stand 26, also show target practice position measurement device 27 in Fig. 7 and Fig. 8, this device is unrelated with this air pressure-loading fueller, so not illustrating.
In conjunction with Fig. 6, Fig. 7 and Fig. 8, when utilizing this air pressure-loading fueller to provide machine oil to test for piston cooling nozzle 5, the main operational principle of this air pressure-loading fueller is as follows:
Boost at a high speed aerofluxus: control first exhaust solenoid valve the 31, second exhaust solenoid valve 33 by controller, oil return solenoid valve 32 is corresponding closes first row air horn seat valve 17, second row air horn seat valve 19, oil return angle pedestal valve 12, control first air inlet electromagnetic valve the 22, second air inlet electromagnetic valve 20 by controller, open first flow inlet angle seat valve the 18, second flow inlet angle seat valve 21, delivery angle seat valve 23 for solenoid 34 is corresponding, boost at a high speed setting pressure (higher than opening pressure, such as 300kPa)；
Low speed blood pressure lowering: close oil return angle pedestal valve the 12, first flow inlet angle seat valve the 18, second flow inlet angle seat valve 21, second row air horn seat valve 19 (or first row air horn seat valve 17), opens first row air horn seat valve 17 (or second row air horn seat valve 19), delivery angle seat valve 23.Low speed is depressurized to setting pressure (lower than closing presure, such as 100kPa)；
Low speed boosts: close oil return angle pedestal valve the 12, second flow inlet angle seat valve 21 (or first flow inlet angle seat valve 18), first row air horn seat valve 17, second row air horn seat valve 19, open the first flow inlet angle seat valve 18 (or second flow inlet angle seat valve 21), the first flow inlet angle seat valve 18, low speed boosts to setting pressure (higher than opening pressure, such as 250kPa)；
Boosting at a high speed: close first row air horn seat valve 17, second row air horn seat valve 19, oil return angle pedestal valve 12, open first flow inlet angle seat valve the 18, second flow inlet angle seat valve 21, delivery angle seat valve 23, boost at a high speed setting pressure (higher than dredge oil amount/target practice position detection pressure, such as 420kPa)；
High speed blood pressure lowering: close oil return angle pedestal valve the 12, first flow inlet angle seat valve the 18, second flow inlet angle seat valve 21, opens first row air horn seat valve 17, second row air horn seat valve 19, delivery angle seat valve 23, is depressurized to 0kPa at a high speed；
Oil return: close first flow inlet angle seat valve the 18, second flow inlet angle seat valve 21, delivery angle seat valve 23, opens first row air horn seat valve 17, second row air horn seat valve 19, oil return angle pedestal valve 12, and the detection medium machine oil in oil return fuel tank 11 returns air tank 13.
During detection operation, with flow transducer 3 test volume flow, test charge oil pressure with pressure transducer 4, the test curve of pressure, flow and time can be obtained, as it is shown in figure 9, required feature physical quantity can be obtained from this curve.
Illustrate: above-mentioned control method be this air pressure-loading fueller method is preferably used, not unique method, neither the protection scheme of the present invention.
Above-described embodiment is presently preferred embodiments of the present invention; it it is not the restriction to technical solution of the present invention; as long as without the technical scheme that creative work can realize on the basis of above-described embodiment, be regarded as falling within the scope of the rights protection of patent of the present invention.
Claims (8)
1. the air pressure-loading fueller for piston cooling nozzle performance test stand, it is characterized in that: include air tank, oil-supply valve, oil return valve, oil return fuel tank, air intake valve, drain tap, barostat and high-pressure air source, fuel feed pump between middle and lower part and the oil-in of described piston cooling nozzle of described air tank is provided with described oil-supply valve, described oil return fuel tank is installed on the lower section of the jet of described piston cooling nozzle and is positioned at the top of described air tank, described oil return valve is installed on the oil return pipe between described oil return fuel tank and described air tank, trachea between middle and upper part and the gas outlet of described barostat of described air tank is provided with described air intake valve, trachea between described air intake valve and described air tank interlinks and is connected to exhaustor, described drain tap is installed on described exhaustor, the air inlet of described barostat is connected with described high-pressure air source.
2. the air pressure-loading fueller for piston cooling nozzle performance test stand according to claim 1, it is characterised in that: two sets that described air intake valve and described drain tap are respectively connected in parallel with each other.
3. the air pressure-loading fueller for piston cooling nozzle performance test stand according to claim 1 and 2, it is characterized in that: often overlap described air intake valve and include air inlet electromagnetic valve and flow inlet angle seat valve, often overlap described drain tap and include exhaust solenoid valve and aerofluxus angle pedestal valve, described oil-supply valve includes for solenoid and delivery angle seat valve, described oil return valve includes oil return solenoid valve and oil return angle pedestal valve, the control input of described air inlet electromagnetic valve, the control input of described exhaust solenoid valve, the described input that controls controlling input and described oil return solenoid valve for solenoid is connected with the control output end of controller respectively, the air inlet of described air inlet electromagnetic valve, the air inlet of described exhaust solenoid valve, the air inlet of the described air inlet supplying solenoid and described oil return solenoid valve is connected with the gas outlet of described barostat respectively, the gas outlet of described air inlet electromagnetic valve is connected with the control end of described flow inlet angle seat valve, the gas outlet of described exhaust solenoid valve is connected with the control end of described aerofluxus angle pedestal valve, the described gas outlet for solenoid is connected with the control end of described delivery angle seat valve, the gas outlet of described oil return solenoid valve is connected with the control end of described oil return angle pedestal valve, described flow inlet angle seat valve is installed on the trachea between described air tank and described barostat, described aerofluxus angle pedestal valve is installed on described exhaustor, described delivery angle seat valve is installed on the fuel feed pump between described air tank and described piston cooling nozzle, described oil return angle pedestal valve is installed on the oil return pipe between described oil return fuel tank and described air tank.
4. the air pressure-loading fueller for piston cooling nozzle performance test stand according to claim 3, it is characterised in that: often overlap on the trachea at described air intake valve place and often overlap on the exhaustor at described drain tap place and be connected in series with choke valve respectively.
5. the air pressure-loading fueller for piston cooling nozzle performance test stand according to claim 3, it is characterised in that: the steam vent of each described air inlet electromagnetic valve, the steam vent of each described exhaust solenoid valve, the described confession steam vent of solenoid, the steam vent of described oil return solenoid valve and the air vent of each described aerofluxus angle pedestal valve are separately installed with the deafener for eliminating exhaust sound.
6. the air pressure-loading fueller for piston cooling nozzle performance test stand according to claim 3, it is characterized in that: the oil pipe between middle and lower part and the oil-in of described piston cooling nozzle of described air tank is also equipped with flow transducer and pressure transducer, the signal output part of described flow transducer and the signal output part of pressure transducer and is connected with the signal input part of described controller respectively.
7. the air pressure-loading fueller for piston cooling nozzle performance test stand according to claim 3, it is characterised in that: described air inlet electromagnetic valve, described exhaust solenoid valve, described confession solenoid and described oil return solenoid valve are three mouthfuls of two electromagnetic valves.
8. the air pressure-loading fueller for piston cooling nozzle performance test stand according to claim 1, it is characterized in that: the space above machine oil in described air tank accounts for 1/to three/4th of the whole space in described air tank, above described air tank is positioned at the machine oil of described air tank with the position that described barostat is connected.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107402129A (en) * | 2017-08-28 | 2017-11-28 | 机科发展科技股份有限公司 | Piston cooling nozzle measuring system and measuring method |
| CN109162971A (en) * | 2018-11-12 | 2019-01-08 | 燕山大学 | Constant-pressure pressure fuel tank and its control method |
| CN112648538A (en) * | 2020-12-11 | 2021-04-13 | 安徽宝隽机车部件有限公司 | Oil supply pressure adjusting device |
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| CN107402129B (en) * | 2017-08-28 | 2023-09-12 | 机科发展科技股份有限公司 | Piston cooling nozzle measuring system and measuring method |
| CN109162971A (en) * | 2018-11-12 | 2019-01-08 | 燕山大学 | Constant-pressure pressure fuel tank and its control method |
| CN112648538A (en) * | 2020-12-11 | 2021-04-13 | 安徽宝隽机车部件有限公司 | Oil supply pressure adjusting device |
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|---|---|
| CN105715595B (en) | 2018-01-16 |
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