CN113503216A - Diesel engine fuel supply system and testing method thereof - Google Patents
Diesel engine fuel supply system and testing method thereof Download PDFInfo
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- CN113503216A CN113503216A CN202110980616.XA CN202110980616A CN113503216A CN 113503216 A CN113503216 A CN 113503216A CN 202110980616 A CN202110980616 A CN 202110980616A CN 113503216 A CN113503216 A CN 113503216A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/04—Feeding by means of driven pumps
- F02M37/041—Arrangements for driving gear-type pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0047—Layout or arrangement of systems for feeding fuel
- F02M37/0052—Details on the fuel return circuit; Arrangement of pressure regulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/22—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system
- F02M37/32—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system characterised by filters or filter arrangements
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- 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
- F04B51/00—Testing machines, pumps, or pumping installations
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention relates to the technical field of testing, and discloses a diesel engine fuel supply system and a testing method thereof. The fuel supply system of the diesel engine comprises a fuel tank, a fuel delivery pump assembly and a fuel injector, wherein fuel is arranged in the fuel tank; the oil delivery pump assembly comprises a rotor pump, an oil inlet of the rotor pump is communicated with the fuel tank, an oil outlet of the rotor pump is communicated with a low-pressure fuel oil delivery pipe, and the rotor pump is configured to pump the fuel oil in the fuel tank to the low-pressure fuel oil delivery pipe after the fuel oil in the fuel tank is pressurized to a preset pressure; the fuel injector is communicated with the low-pressure fuel delivery pipe, the fuel injector is configured to inject fuel to a combustion chamber of the engine, and the fuel injector is also communicated with an oil return pipe which is communicated with the fuel tank. The oil delivery pump assembly comprises the rotor pump, the oil pumping process of the rotor pump is stable, the impact on a diesel engine fuel oil supply system is small, and meanwhile, the rotor pump has higher oil delivery pressure and can effectively ensure that fuel oil entering an injector has proper oil delivery pressure.
Description
Technical Field
The invention relates to the technical field of testing, in particular to a diesel engine fuel supply system and a testing method thereof.
Background
The fuel supply system in the diesel engine is the heart and the aorta of the engine, and plays an extremely important role in the engine and the whole vehicle. The fuel delivery pump assembly in the fuel supply system plays a leading role in the system, is a prerequisite for achieving good starting and operating characteristics of the engine, determines whether the system can normally operate or not, and is a key component of the fuel supply system.
In the prior art, the fuel delivery pump in the fuel supply system is usually a plunger type fuel delivery pump, which pumps fuel by driving a plunger to reciprocate by rotation of a cam, which generates one fuel supply at a time. Because the plunger pump is greatly influenced by the restriction of space and structure, the insufficient fuel supply can be caused by the over-less pumping oil quantity of the plunger pump, and the full-function exertion of the power of the engine is seriously influenced; meanwhile, due to intermittent oil pumping, the generated pressure fluctuation is large, and the fuel supply system is easy to be impacted; in addition, the plunger type fuel delivery pump has a low fuel delivery pressure and cannot be adapted to a fuel supply system requiring a higher fuel delivery pressure.
Therefore, a diesel fuel supply system is needed to solve the above problems.
Disclosure of Invention
In view of the above, an object of the present invention is to provide a diesel engine fuel supply system and a test method thereof, which can efficiently and stably supply fuel to an engine.
In order to achieve the purpose, the invention adopts the following technical scheme:
a diesel fuel supply system comprising:
a fuel tank in which fuel is disposed;
the fuel delivery pump assembly comprises a rotor pump, wherein an oil inlet of the rotor pump is communicated with the fuel tank, an oil outlet of the rotor pump is communicated with a low-pressure fuel delivery pipe, and the rotor pump is configured to pump fuel in the fuel tank to the low-pressure fuel delivery pipe after the fuel is pressurized to a preset pressure;
the fuel injector is communicated with the low-pressure fuel delivery pipe and is configured to inject fuel into a combustion chamber of the engine, and the fuel injector is also communicated with a fuel return pipe which is communicated with the fuel tank.
As a preferred scheme of the diesel engine fuel supply system, the fuel delivery pump assembly further comprises a bypass valve connected with the rotor pump in parallel, and the rotor pump is provided with a pressure limiting valve.
As a preferred scheme of the diesel engine fuel supply system, the diesel engine fuel supply system further comprises a coarse filter and a fine filter, the coarse filter is arranged between the fuel tank and the fuel delivery pump assembly, and the fine filter is arranged between the fuel delivery pump assembly and the fuel injector.
As a preferable aspect of the fuel supply system for a diesel engine, the rotary pump includes:
the oil inlet and the oil outlet are arranged on the pump body;
rotate set up in internal inner rotor and the outer rotor of pump, the inner rotor with outer rotor eccentric settings just the tooth ratio of inner rotor the tooth number of outer rotor is few one, works as the inner rotor with when the outer rotor intermeshing, can with the fuel pressurization of fuel tank is pumped extremely low pressure fuel oil pipeline.
A diesel engine fuel supply system testing method is used for testing the diesel engine fuel supply system according to any one of the above schemes, and comprises the step of measuring parameters of the rotor pump under the working conditions of starting, maximum torque and maximum rotating speed.
As a preferable scheme of the testing method of the diesel engine fuel supply system, the method comprises the following steps: and calculating the oil output of the rotor pump under the starting working condition and the highest rotating speed working condition.
As a preferable scheme of the testing method of the diesel engine fuel supply system, the method comprises the following steps: and testing the relation between the rotating speed of the rotor pump and the oil output under the constant oil outlet pressure.
As a preferable scheme of the testing method of the diesel engine fuel supply system, the method comprises the following steps: and calculating the minimum oil output of the rotor pump under the starting working condition, the maximum torque working condition and the highest rotating speed working condition, and comparing the minimum oil output under the starting working condition, the maximum torque working condition and the highest rotating speed working condition with the oil consumption under the corresponding working condition of the engine.
As a preferable scheme of the testing method of the diesel engine fuel supply system, the method comprises the following steps: and calculating the oil outlet pressure of the rotor pump under the starting working condition, the maximum torque working condition and the highest rotating speed working condition.
The preferable scheme of the testing method of the diesel engine fuel supply system is characterized by further comprising a preset time load cycle test of the rotor pump, wherein the preset time is 1800 hours.
The invention has the beneficial effects that:
the fuel tank for containing fuel oil and the fuel oil injector for injecting the fuel oil to the combustion chamber of the engine are arranged; the fuel delivery pump assembly is arranged between the fuel tank and the fuel injector and comprises the rotor pump, the rotor pump can pressurize fuel in the fuel tank to a pressure suitable for the fuel injector, and pump the fuel with a suitable and stable pressure into the fuel injector through the low-pressure fuel delivery pipe, the fuel pumping process of the rotor pump is stable, the impact on a fuel supply system of the diesel engine is small, meanwhile, the rotor pump has high fuel delivery pressure, and the fuel pressure in the low-pressure fuel delivery pipe can be effectively ensured to meet the requirement of the injector; in addition, the oil return pipe is arranged and used for returning fuel which is not sprayed into the combustion chamber by the fuel injector to the fuel tank.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments of the present invention will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the contents of the embodiments of the present invention and the drawings without creative efforts.
FIG. 1 is a schematic diagram of a diesel fuel delivery system according to one embodiment of the present invention;
fig. 2 is an exploded view of a gerotor pump of a diesel fuel delivery system in accordance with an embodiment of the present invention.
In the figure:
100. a fuel tank; 101. a low pressure fuel delivery pipe; 110. an oil transfer pump assembly; 111. a rotor pump; 112. a bypass valve; 113. a pressure limiting valve; 120. an oil injector; 121. a high pressure fuel delivery pipe; 122. an injection pump; 123. a nozzle; 130. an oil return pipe; 140. a coarse filter; 150. a fine filter;
1. a belt pulley; 2. a drive shaft; 3. a nut; 4. a gasket; 5. a retainer ring; 6. a bearing; 7. framework oil seal; 8. a pump body; 9. an outer rotor; 10. an inner rotor; 11. a flat bond; 12. a pump cover; 13. an O-shaped ring; 14. self-tapping self-locking screws; 15. a shaft sleeve; 16. plugging by screwing; 17. a gasket; 18. a plunger spring; 19. a steel ball; 20. a plunger; 21. the plunger balances the spring.
Detailed Description
In order to make the technical problems solved, technical solutions adopted and technical effects achieved by the present invention clearer, the technical solutions of the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all 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.
Example one
As shown in fig. 1 and 2, the present embodiment provides a diesel fuel supply system including a fuel tank 100, a fuel delivery pump assembly 110, and a fuel injector 120, fuel being disposed in the fuel tank 100; the fuel delivery pump assembly 110 comprises a rotor pump 111, an oil inlet of the rotor pump 111 is communicated with the fuel tank 100, an oil outlet of the rotor pump 111 is communicated with the low-pressure fuel delivery pipe 101, and the rotor pump 111 is configured to pump the fuel in the fuel tank 100 to the low-pressure fuel delivery pipe 101 after the fuel is pressurized to a preset pressure; the injector 120 is communicated with the low-pressure fuel delivery pipe 101, the injector 120 is configured to inject fuel into a combustion chamber of the engine, the injector 120 is further communicated with a return pipe 130, and the return pipe 130 is communicated with the fuel tank 100.
The fuel tank 100 is used for containing fuel oil; by providing an injector 120 for injecting fuel into the combustion chamber of the engine; the fuel delivery pump assembly 110 is arranged between the fuel tank 100 and the fuel injector 120, the fuel delivery pump assembly 110 comprises the rotor pump 111, the rotor pump 111 can pressurize fuel in the fuel tank 100 to a pressure suitable for the fuel injector 120, the fuel with the suitable and stable pressure is pumped into the fuel injector 120 through the low-pressure fuel delivery pipe 101, the fuel pumping process of the rotor pump 111 is stable, the impact on a diesel engine fuel supply system is small, meanwhile, the rotor pump 111 has high fuel delivery pressure, and the fuel pressure in the low-pressure fuel delivery pipe 101 can be effectively ensured to meet the requirement of the injector; further, by providing the return pipe 130, the fuel injected into the combustion chamber without the fuel injector 120 is returned to the fuel tank 100.
It should be noted that the fuel injector 120 includes a fuel injection pump 122 and a nozzle 123, an oil inlet of the fuel injection pump 122 is communicated with the low-pressure fuel delivery pipe 101, an oil outlet is provided with a high-pressure fuel delivery pipe 121, and the nozzle 123 is disposed at the other end of the high-pressure fuel delivery pipe 121, and since the fuel delivery amount of the fuel delivery pump assembly 110 is much greater than the fuel delivery amount of the fuel injection pump 122, the fuel return pipe 130 is disposed, so that the excessive fuel can flow back to the fuel tank 100 through the fuel return pipe 130.
In addition, the oil pressure in the section of oil path from the oil delivery pump assembly 110 to the oil inlet of the oil injection pump 122 is established by the rotor pump 111, and the oil outlet pressure of the rotor pump 111 is generally (400-500) kPa, so the section of oil path is called a low-pressure fuel oil delivery pipe 101. The oil pressure in the section of the oil path from the injection pump 122 to the nozzle 123 is established by the injection pump 122, and is generally above 150MPa, so that the section of the oil path is a high-pressure fuel delivery pipe 121. The high-pressure fuel in the high-pressure fuel delivery pipe 121 is sprayed into the combustion chamber in a mist form through the nozzle 123, and is mixed with air to form combustible mixed gas, so that the engine piston is further driven to do work.
Specifically, the diesel fuel supply system further includes a coarse filter 140 and a fine filter 150, the coarse filter 140 is disposed between the fuel tank 100 and the fuel delivery pump assembly 110, and is used for filtering the fuel to ensure the cleanliness of the fuel entering the rotor pump 111; the fine filter 150 is disposed between the fuel delivery pump assembly 110 and the fuel injector 120, and is used for further filtering the fuel, so as to ensure cleanliness of the fuel entering the fuel injection pump 122, and effectively ensure reliability of fuel injection from the nozzle 123. Optionally, the oil pump further comprises a bypass valve 112 connected in parallel with the rotodynamic pump 111, the bypass valve 112 connecting a coarse filter 140 and a fine filter 150, facilitating the further function of discharging the excess impurities.
In this embodiment, as shown in fig. 2, the rotor pump 111 includes a pump body 8, and an oil inlet and an oil outlet of the rotor pump 111 are disposed on the pump body 8; the fuel oil pump further comprises an inner rotor 10 and an outer rotor 9 which are rotatably arranged in the pump body 8, the inner rotor 10 and the outer rotor 9 are eccentrically arranged, the number of teeth of the inner rotor 10 is one less than that of the outer rotor 9, and when the inner rotor 10 and the outer rotor 9 are meshed with each other, fuel oil in the fuel oil tank 100 can be pressurized and pumped to the low-pressure fuel oil delivery pipe 101. When the rotor pump 111 works, the inner rotor 10 is a driving wheel which drives the outer rotor 9 to rotate in the same direction at different speeds, and two independent sealing cavities are formed by the inner rotor 10, the outer rotor 9, the pump body 8, the pump cover 12 and other parts. With the rotation of the inner rotor 10 and the outer rotor 9, teeth on one side are disengaged, the volume of a low-pressure cavity is increased to form a certain vacuum degree, oil absorption is realized, and the cavity is called as an oil absorption cavity; the other side tooth is engaged, the volume of a pressure oil cavity is reduced, the oil pressure is increased, and oil pumping is realized, and the cavity is called a pressure chamber.
Specifically, the inner rotor 10 is coupled with the drive shaft 2 by a flat key 11. The drive shaft 2 is supported by the pump body 8 via a bearing 6 and a sleeve 15. The pump cover 12 is fastened to the pump body 8 by three self-tapping self-locking screws 14. The end face of the pump body 8 is provided with a sealing groove, and an O-shaped ring 13 is arranged in the sealing groove and used for preventing the internal combustion oil of the pump from leaking from the joint surface of the pump body 8 and the pump cover 12. A framework oil seal 7 is arranged in the pump body 8 to prevent fuel oil from leaking from the driving shaft 2. A lubricating oil hole is arranged between the low-pressure cavity and the oil seal, and an overflow hole is arranged on the pump body 8.
Further, a pressure limiting valve 113 is provided between the oil absorption chamber and the pressure chamber in the pump body 8. The pressure limiting valve 113 is composed of a plug 16, a gasket 17, a plunger spring 18, a plunger 20, a steel ball 19 and a plunger balance spring 21. The bearing 6 mounted in the pump body 8 is clamped with a collar 5. Pulley 1 is fixed to drive shaft 2 by spacer 17 and nut 3. When the oil pressure of the pressure chamber is higher than the opening pressure of the pressure limiting valve 113, the steel ball 19 compresses the plunger spring 18 through the plunger 20, and the pressure chamber is communicated with the oil suction chamber to realize pressure relief.
Example two
The embodiment further discloses a diesel engine fuel supply system testing method, which is used for testing the diesel engine fuel supply system in the first embodiment and comprises the step of measuring parameters of the rotor pump 111 under the starting working condition, the maximum torque working condition and the highest rotating speed working condition.
Since the fuel delivery pump assembly 110 is a secondary development component with respect to diesel fuel delivery systems, where the gerotor pump 111 is a key component with respect to diesel fuel delivery systems, whether the performance of the gerotor pump 111 meets standards directly affects engine starting and power. Therefore, to meet the engine development requirements, the performance of the fuel delivery pump assembly 110, and particularly the gerotor pump 111, needs to be tested to ensure that the gerotor pump 111 is capable of providing a stable and appropriate pressure and quantity of fuel to the fuel injector 120 under various engine operating conditions.
In the prior art, the diesel fuel supply system is usually evaluated by measuring parameters at the injection pump 122, and the importance of the gerotor pump 111 to the diesel fuel supply system is ignored. In the embodiment, the evaluation of the diesel fuel supply system is more accurate by detecting the rotor pump 111.
The following description will be made of a diesel fuel supply system provided with an engine of the BF6M1013-28 type as an example, and a diesel fuel supply system test method will be described. In model BF6M1013-28, B represents a supercharger model, F represents a high-speed four-stroke engine model, 6 represents six cylinders, M represents water cooling, 10 represents a product serial number, 13 represents a piston stroke, the cylinder diameter x the stroke of 1013 is 108 x 130(mm), and the rear-28 means that the power is 280 horsepower. In this embodiment, the rotor pump 111 is mounted at the front end of the engine through a tension connection plate, and is directly driven by the crankshaft of the engine through belt transmission of the belt pulley 1. The rotor pump 111 speed is 2.118 times the crankshaft speed. The parameters of the engine of the BF6M1013-28 type are known as follows: the number of cylinders is 6; the cylinder diameter is 108 mm; the stroke is 130 mm; total displacement 7.146L; the cylinder center distance is 132 mm; the firing sequence among all cylinders is 1-5-3-6-2-4; the rotation direction of the crankshaft is clockwise along the front view; the air suction mode is supercharging air-to-air intercooling; the rated air inlet temperature is less than or equal to 50 ℃; rated power (kW)/rotating speed (r/min) is 206/2300; net power (kW)/rotational speed (r/min) is 206/2300; the piston mean velocity was 9.97 (m/s); the power per liter was 28.82 (kW/L); the average effective pressure at the rated power point is 1504 kPa; the maximum torque is 1050/1400 (N.m/r/min); the torque reserve coefficient is 22.76%; the maximum torque point average effective pressure is 1846 kPa; the torque is 650 N.m at 800 r/min; the average effective pressure of 800r/min is 1143 kPa; the idle speed is 800 +/-50 (r/min); the fuel consumption rate under the rated working condition is (230 +/-2%) (g/kW.h); the lowest fuel consumption rate of the external characteristics is (203 +/-1%) (g/kW.h); the weighted oil consumption rate under 13 working conditions is 220 (g/kW.h); the highest rotating speed of the BF6M1013-28 engine is (2500 +/-50) r/min, and the starting rotating speed is 280 r/min.
Specifically, the diesel fuel supply system test method comprises the steps of estimating the fuel delivery amount of the rotor pump 111, particularly calculating the fuel delivery amount of the rotor pump 111 under the starting working condition and the highest rotating speed working condition, and detecting the fuel delivery amount of the rotor pump 111 under the starting working condition because the rotor pump 111 has large leakage at low speed so as to reduce the influence of the rotor pump 111 on the diesel fuel supply system. The oil transfer capacity reflects the wear resistance of the materials of the internal parts of the rotor pump 111, such as the oil seal, the inner rotor 10 and the outer rotor 9, and determines the distance between the oil transfer tank and the inlet of the rotor pump 111 when the whole vehicle is designed, and the farther the distance between the oil transfer tank and the inlet of the rotor pump 111, the larger the wear degree of the oil seal, the inner rotor 10 and the outer rotor 9 of the internal parts of the rotor pump 111.
The oil delivery amount of the rotor pump 111 is qth × η × n, where qth is the displacement per revolution and the unit is liter per revolution (L/r); η is the volumetric efficiency; and n is the working rotating speed of the oil transfer pump, and the unit is revolution per minute (r/min). Wherein qth ═ pi B x [ D-D]×10-6(L/r), wherein B is the thickness of the rotor and the unit is mm; d is the minor diameter of the inner rotor 10 in mm; d is the major diameter of the outer rotor 9, and the unit is mm. Illustratively, the rotor thickness B of the rotor pump 111 is 11.5mm, the small diameter D of the inner rotor 10 is 23.82mm, the large diameter D of the outer rotor 9 is 33.62mm, nmax is 5375r/min (the rotation speed of the rotor pump 111 under the condition of the highest engine rotation speed), nmin is 593r/min (the rotation speed of the oil transfer pump under the condition of the engine starting), and the inner rotor is arranged in the oil transfer pumpThe rotor 10 is 8 teeth, the outer rotor 9 is 9 teeth, and the eccentric distance between the inner rotor 10 and the outer rotor 9 is 2.235 mm. So qth is 0.25 pi × 11.5 × [ 33.622-23.822 × ]]×10-6(L/r)＝5082×10-6(L/r), accordingly, the oil delivery Q of the rotor pump 111 is 5082 × 10 in the engine start condition-6X 40% x 593 is 1.2L/min, and the oil delivery quantity Q of the rotor pump 111 is 5082 x 10 under the working condition of the highest rotating speed of the engine-6×60％×5375＝16L/min。
Further, the method for testing the diesel engine fuel supply system comprises a performance test of the rotor pump 111, and the test conditions of the performance test comprise: the test oil is required to be executed according to ISO4113, and the test temperature is (40 +/-3) ° C; the oil transportation height is required, namely the center of the rotor pump 111 is 1500mm higher than the liquid level of the test bed; the internal diameter phi of the oil suction pipe is 10mm, the length is 2000mm, and a transparent oil suction pipe is adopted; the oil outlet pipe has an inner diameter phi 7mm and a length of 1500mm, and adopts a transparent oil conveying pipe.
The performance test of the rotor pump 111 specifically includes: first, the free-rotation of the inner rotor 10 and the outer rotor 9 of the rotor pump 111 is tested by rotating the pulley 1 for a minimum of 7 rotations and a torque of not more than 0.5N · m for flexibility in controlling the cooperation of the inner rotor 10 and the outer rotor 9.
Secondly, testing the oil absorption capacity of the rotor pump 111 assembly, wherein the testing method comprises the steps of installing the oil delivery pump assembly 110 on a testing device meeting the testing conditions, opening an oil absorption pipe, and idling for 10s at the rotating speed of more than or equal to 3000r/min (ensuring that an oil absorption chamber is empty); the fuel oil is output from the oil outlet within a time period of less than or equal to 30s when the rotating speed of the rotor pump 111 is 250r/min and the back pressure of (0-10) kPa is reduced, so that the radial clearance between the inner rotor 10 and the outer rotor 9 and the end surface clearance between the inner rotor 10, the outer rotor 9 and the pump cover 12 are controlled to meet the use requirement.
Third, the pressure characteristic of the gerotor pump 111, i.e., the ability to adjust the amount of oil delivered by the gerotor pump 111 as a function of rotational speed. The testing method comprises the steps of installing the rotor pump 111 according to the testing condition requirements, measuring the rotating speed of the rotor pump 111 by using a tachometer, and detecting the pressure at the oil inlet and the oil outlet of the rotor pump 111. According to the measurement result, a characteristic curve of the rotating speed and the oil transportation amount of the rotor pump 111 under the condition of constant oil outlet pressure of the rotor pump 111 is obtained. For example, the qualified rotor has a qualified curve in the table of the rotation speed and the oil delivery amount, and if the characteristic curve of the rotation speed and the oil delivery amount measured according to the above-mentioned detection method falls on the upper left of the qualified curve, the qualified rotor is a qualified product.
Fourthly, the flow characteristic of the rotor pump 111, similarly, under the condition of a constant rotation speed, the qualified rotor pump 111 has a qualified curve in the table of the oil outlet pressure and the oil output, and if the rotation speed of the rotor pump 111 is constant, the curve of the oil outlet pressure and the oil output falls on the upper right of the qualified curve, and the qualified product is only obtained.
Fifth, pressure limiting valve 113 of gerotor pump 111 opens pressure verification. In the practical use process, the opening pressure of the pressure limiting valve 113 is required to be more than 500kPa, so as to control the fuel pressure of the low-pressure oil transportation pipe. If the pressure of the low pressure oil line is below 500kPa, the power of the engine is affected. The testing method comprises the steps of under different rotating speeds of the rotor pump 111, constantly changing the oil outlet pressure of the rotor pump 111 under a constant rotating speed, measuring the oil delivery amount, and obtaining the opening pressure of the pressure limiting valve 113 at the point of sudden drop of the oil delivery amount.
Sixthly, the minimum oil output of the rotor pump 111 is calculated under the starting working condition, the maximum torque working condition and the highest rotating speed working condition of the rotor pump 111, and the minimum oil output under the starting working condition, the maximum torque working condition and the highest rotating speed working condition is compared with the oil consumption under the corresponding working condition of the engine. So as to check whether the oil quantity of the rotor pump 111 under the working conditions of engine starting, maximum torque and maximum rotating speed can meet the requirements of the engine. The rotating speed of the rotor pump 111 under the starting working condition is 600r/min, the oil outlet pressure is 100kPa, and the minimum oil output is 1.6L/min; the rotating speed under the working condition of maximum torque is 3000r/min, the oil outlet pressure is 500kPa, and the minimum oil output is 6L/min; the rotating speed under the working condition of the highest rotating speed is 5375r/min, the oil outlet pressure is 500kPa, and the minimum oil output is 10L/min. Accordingly, the development target of the fuel consumption rate of the engine under the rated working condition is as follows: 230 g/kWh and a rated power of 206kW/2300 r/min. Rated fuel consumption under the starting working condition of the engine is
Thus a volume flow of
Namely, the volume flow is 0.95L/min, and the fuel consumption of the engine under the starting working condition is 120 percent of the rated working condition; therefore, the fuel consumption of the engine under the starting working condition is 1.2 multiplied by 0.95 to 1.16L/min, which is less than the minimum oil delivery amount of the rotor pump 111 under the starting working condition of 1.6L/min. Similarly, the fuel consumption of the engine under the maximum torque working condition is 0.61L/min, the fuel consumption of the engine under the maximum rotating speed working condition is 0.99L/min, the minimum oil output of the rotor pump 111 under the maximum torque working condition is 6L/mina, the minimum oil output of the rotor pump 111 under the maximum rotating speed working condition is 10L/min, and the minimum oil output is respectively greater than the fuel consumption of the engine under the corresponding working conditions, so that the rotor pump 111 can completely meet the development requirements of an oil supply system and the engine.
Seventhly, the diesel engine fuel supply system test method comprises the step of calculating the oil outlet pressure of the rotor pump 111 under the starting working condition, the maximum torque working condition and the highest rotating speed working condition. The testing method comprises the steps of blocking the oil outlet of the rotor pump 111, and when the rotating speed of the rotor pump 111 is 5375r/min, the pressure of the oil outlet of the rotor pump 111 does not exceed 900kPa, namely the pressure is qualified. The purpose is to control the discharge pressure of the gerotor pump 111 at the highest rotational speed. It is worth noting that if the fuel pressure pumped by the rotary pump 111 is greater than 900kPa at the maximum engine speed, other parts of the diesel fuel supply system may be damaged, for example, the fine filter 150 in the diesel fuel supply system may be damaged at 900 kPa.
Further, the diesel fuel supply system test method includes a stability test of the gerotor pump 111. The test method comprises the following steps: firstly, the stability test solution meets the ISO4113 standard, the temperature of the test solution is 40 +/-3 ℃, and the solution is replaced after 3000 hours. The inner diameter phi of the oil delivery pipe is 10mm, the length of the oil delivery pipe is 2000mm, and the center of the rotor pump 111 is 750mm higher than the liquid level of the test bed. The oil outlet pressure of the oil outlet of the rotor pump 111 is (500 +/-20) kPa. V-belt drive radial load (450 ± 50) N. The test ensures that the rotary pump 111 rotates at 6250r/min and runs for 600 h. Under the above test conditions, the stable operation of the rotary pump 111 is completed, and then the rotary pump 111 is cooled to room temperature; rotating the inner rotor 10 or the outer rotor 9 of the rotor pump 111 for at least 7 circles, wherein the maximum torque is 0.5 N.m; when the rotating speed of the rotor pump 111 is 250r/min and the back pressure is (0-10) kPa, whether the fuel oil is output from the oil outlet by the fuel delivery pump within 45s or not is judged; whether the oil delivery is reduced by more than 10% from the corresponding index reduction of the rotor pump 111; whether the tightening torque of the fastening bolt of the pump cover 12 is greater than 90% of the original minimum value; whether there is visible surface wear in the rotor cavity of the pump body 8; whether the rotor pump 111 is sealed or not and whether there is visible oil stain on the outer surface of the pump body 8 or not. The stability of the gerotor pump 111 was evaluated by the above criteria.
The testing method of the diesel engine fuel supply system further comprises a preset time load cycle test of the rotor pump 111, wherein the preset time is 1800 hours, and the preset time is used for checking the reliability and the durability of the rotor pump 111. After the rotor pump 111 works for a preset time, the parts of the oil transfer pump assembly 110 are disassembled, and meanwhile, the abrasion conditions of the inner rotor 10, the outer rotor 9, the oil seal, the driving shaft 2 and the plunger 20 are observed.
After the test is finished, the test method of the diesel engine fuel supply system further comprises an engine performance test and a finished automobile user test so as to detect the influence of the diesel engine fuel supply system adopting the rotor pump 111 on the engine and even the finished automobile. The test mode is that the rotor pump 111 is installed on the whole vehicle along with the diesel engine fuel supply system, and the vehicle is driven for 5 kilometers in a test mode so as to test the service life of the rotor pump 111.
The invention tests the oil transfer pump assembly 110 in the diesel engine fuel supply system to obtain the oil transfer characteristic and the oil outlet pressure characteristic which are required to be possessed by the rotor pump 111 under the working conditions of starting, maximum torque and maximum rotating speed, and the reliability and the durability of the engine. Meanwhile, the quantized values of the freely rotatable performance, the oil transportation performance, the opening pressure of the pressure limiting valve 113, and the like of the rotor pump 111 are also obtained. By adopting the testing method of the diesel engine fuel supply system, particularly the rotor pump 111 can meet the development requirements of the engine, and the diesel engine fuel supply system becomes a qualified product.
It is to be noted that the foregoing is only illustrative of the preferred embodiments of the present invention and the technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. Wherein the terms "first position" and "second position" are two different positions.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Claims (10)
1. A diesel fuel supply system, comprising:
a fuel tank (100) in which fuel is placed;
the fuel delivery pump assembly (110) comprises a rotor pump (111), an oil inlet of the rotor pump (111) is communicated with the fuel tank (100), an oil outlet of the rotor pump is communicated with a low-pressure fuel delivery pipe (101), and the rotor pump (111) is configured to pump fuel in the fuel tank (100) to the low-pressure fuel delivery pipe (101) after the fuel is pressurized to a preset pressure;
the fuel injector (120) is communicated with the low-pressure fuel delivery pipe (101), the fuel injector (120) is configured to be capable of injecting fuel into a combustion chamber of an engine, the fuel injector (120) is further communicated with a fuel return pipe (130), and the fuel return pipe (130) is communicated with the fuel tank (100).
2. The diesel fuel supply system of claim 1, characterized in that the fuel delivery pump assembly (110) further comprises a bypass valve (112) connected in parallel with the gerotor pump (111), the gerotor pump (111) being provided with a pressure limiting valve (113).
3. The diesel fuel supply system of claim 1, further comprising a coarse filter (140) and a fine filter (150), the coarse filter (140) being disposed between the fuel tank (100) and the fuel delivery pump assembly (110), the fine filter (150) being disposed between the fuel delivery pump assembly (110) and the fuel injector (120).
4. The diesel fuel supply system of claim 1, characterized in that the gerotor pump (111) comprises:
the pump body (8), the oil inlet and the oil outlet are arranged on the pump body (8);
rotate set up in inner rotor (10) and outer rotor (9) in the pump body (8), inner rotor (10) with outer rotor (9) eccentric settings just the tooth ratio of inner rotor (10) one less than the tooth number of outer rotor (9), work as inner rotor (10) with when outer rotor (9) intermeshing, can with the fuel pressurization of fuel tank (100) and pump extremely low pressure fuel oil pipeline (101).
5. A diesel fuel supply system testing method, for testing a diesel fuel supply system according to any of claims 1-4, comprising measuring parameters of the gerotor pump (111) at start-up, maximum torque and maximum speed conditions.
6. The method for testing a fuel supply system of a diesel engine according to claim 5, comprising: and calculating the oil delivery amount of the rotor pump (111) under the starting working condition and the highest rotating speed working condition.
7. The method for testing a fuel supply system of a diesel engine according to claim 5, comprising: and testing the relation between the rotating speed of the rotor pump (111) and the oil output under the constant oil outlet pressure.
8. The method for testing a fuel supply system of a diesel engine according to claim 5, comprising: and calculating the minimum oil output of the rotor pump (111) under the starting working condition, the maximum torque working condition and the highest rotating speed working condition, and comparing the minimum oil output under the starting working condition, the maximum torque working condition and the highest rotating speed working condition with the oil consumption under the corresponding working condition of the engine.
9. The method for testing a fuel supply system of a diesel engine according to claim 5, comprising: and calculating the oil outlet pressure of the rotor pump (111) under the starting working condition, the maximum torque working condition and the highest rotating speed working condition.
10. A diesel fuel supply system test method as set forth in any of claims 5-9, further comprising a preset time duty cycle test of the gerotor pump (111), the preset time being 1800 hours.
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| CN202110980616.XA CN113503216A (en) | 2021-08-25 | 2021-08-25 | Diesel engine fuel supply system and testing method thereof |
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| CN202110980616.XA CN113503216A (en) | 2021-08-25 | 2021-08-25 | Diesel engine fuel supply system and testing method thereof |
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