CN101131141A - Pump nozzle oil supply system and method thereof - Google Patents
Pump nozzle oil supply system and method thereof Download PDFInfo
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- CN101131141A CN101131141A CNA2007101757447A CN200710175744A CN101131141A CN 101131141 A CN101131141 A CN 101131141A CN A2007101757447 A CNA2007101757447 A CN A2007101757447A CN 200710175744 A CN200710175744 A CN 200710175744A CN 101131141 A CN101131141 A CN 101131141A
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- plunger
- oil
- push rod
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Abstract
The present invention discloses one kind of oil supplying pump-oil nozzle system and method. The oil supplying pump-oil nozzle system has one first oil path and one second oil path connected to the hydraulic oil source system to provide back flow high pressure oil, one third oil path communicated to the oil passage inside the plunger sleeve, one two-position three-way solenoid valve connected to the first oil path, the second oil path and the third oil path, one first plunger inside the plunger sleeve, one jib with roller, one push rod hinged to one rocking arm, one second plunger connected to one oil injector and other parts. The oil supplying pump-oil nozzle system in the technological scheme of the present invention has no rotating part for driving pump-oil nozzle to spray oil and stable oil injecting pressure under different engine operation modes.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a pump nozzle oil supply system and method.
Background
In a conventional pump nozzle oil supply system, an engine crankshaft drives an oil injection pump to work through rotation of cams on an oil supply camshaft driven by a pair of oil supply timing gears. In the oil supply system with the structure, the oil injection time is ensured by the cam molded lines on the timing gear and the cam shaft, the oil injection rule is ensured by the cam molded lines, and the oil injection quantity is determined by the position of the plunger inclined groove driven by the plunger pull rod in the oil injection pump.
The hydraulic free piston engine is a new type of engine integrating a reciprocating piston type internal combustion engine and a plunger type hydraulic pump. The engine directly converts the reciprocating motion of a piston in a cylinder into hydraulic energy through a hydraulic plunger rigidly connected with the piston to drive a load to work. The main structural difference from the traditional crankshaft engine is as follows: the engine does not have a crank linkage mechanism, i.e., a rotating mechanism. Because a rotating mechanism is not provided, the driving of the oil supply system of the engine is difficult to realize if a pump nozzle structure driven by a traditional engine camshaft is adopted, and therefore the oil supply system driven by a non-rotating mechanism is required to realize the fuel supply of the hydraulic free piston engine.
Disclosure of Invention
The invention aims to provide an oil supply system and an oil supply method for a pump nozzle, which can drive the pump nozzle to supply oil without using a rotating part and can ensure that the oil injection pressure of an engine is stable under various working conditions.
In order to achieve the purpose, the invention adopts the following technical scheme:
a pump nozzle oil supply system is suitable for a hydraulic free piston engine and comprises a first oil duct 12, a second oil duct 15, a two-position three-way electromagnetic valve 2, a third oil duct 13, a plunger sleeve 4, a first plunger 3, a tappet 6, a push rod 7, a rocker arm 8, a second plunger 9, a return spring 10 and an oil injector 11, wherein the first oil duct and the second oil duct are respectively communicated with a hydraulic oil source system 1 of the hydraulic free piston engine and used for supplying and returning high-pressure oil, the two-position three-way electromagnetic valve and the plunger sleeve are installed on a machine body 14, two openings of the two-position three-way electromagnetic valve are respectively connected with the other ends of the first oil duct and the second oil duct, the other opening of the two-position three-way electromagnetic valve is connected with one end of the third oil duct, the other end of the third oil duct is communicated with an oil duct in the plunger sleeve, the first plunger is installed in the plunger sleeve, one end of the first plunger corresponds to a roller of the tappet, the lower end of the push rod is placed in the tappet, the upper end of the push rod is connected with one end of the rocker arm through a hinge, the other end of the second plunger sleeve is connected with the upper end of the tappet, and the lower end of the return spring is connected with the return spring of the tappet.
Also included is a gap adjustment screw 16, which is located on the push rod for adjusting the length of the push rod.
The first plunger and the second plunger are T-shaped, and the section diameter of the upper end of the first plunger is larger than that of the lower end of the second plunger.
The diameter of the first plunger and the provided high-pressure oil pressure, the return spring force and the oil injection pressure of the oil injector are in a relation
Wherein d represents the first plunger diameter, P represents the high oil pressure,
F 1 indicating the return spring force, F 2 Indicating the fuel injection pressure of a fuel injector;
the relationship between the length of the first plunger and the maximum stroke of the second plunger, namely the maximum circulating fuel injection quantity and the required height of the guide is
l is more than or equal to 1.5d, wherein Q max Representing the maximum fuel injection cycle, D representing the second plunger diameter, l representing the minimum length required for normal guiding of the first plunger, s representing the stroke of the first plunger, λ representing the rocker ratio, h = s · λ representing the maximum stroke of the second plunger, D representing the first plunger diameter, the plunger length then being max { s, l };
the flow of the oil outlet duct is not less than that of the two-position three-way electromagnetic valve.
The two-position three-way electromagnetic valve and the plunger sleeve are installed on the machine body through threads.
The plunger sleeve is of a tubular structure, the inner hole is matched with the cylindrical surface of the plunger, the outer part of the plunger sleeve is of a stepped shaft type structure, the upper part with the larger outer diameter is provided with an external thread, an inner hexagonal pit is arranged on the inner hole circle as an inscribed circle, a fastening thread is conveniently installed by a wrench, an internal thread is arranged at the corresponding position on the machine body, and the plunger sleeve is installed on the machine body through the thread.
A method of supplying oil to a pump nozzle, comprising the steps of:
A. the two-position three-way electromagnetic valve is electrified and opened;
B. high-pressure oil enters the plunger sleeve through the two-position three-way solenoid valve and the first oil duct;
C. the high-pressure oil pushes the first plunger piston to move upwards along the plunger sleeve;
D. the first plunger pushes the tappet to move upwards, and the tappet drives the push rod to move upwards;
E. the push rod pushes the rocker arm to rotate clockwise around the axis of the rocker arm, and the other end of the rocker arm moves downwards;
F. the rocker arm pushes the second plunger to drive the fuel injector to pressurize and spray fuel, and a return spring sleeved on the second plunger is compressed;
G. when the two-position three-way electromagnetic valve is powered off, high-pressure oil in the plunger sleeve flows back to the oil tank through the second oil duct through the two-position three-way electromagnetic valve;
H. the return spring extends to drive the second plunger to return, and the rocker arm rotates anticlockwise around the axis of the rocker arm;
I. the push rod, the tappet and the first plunger return to the original positions under the driving of the rocker arm.
By adjusting the gap adjusting screw, the pre-compression amount of the return spring in the initial installation state is enabled to exist.
By adopting the technical scheme of the invention, the oil supply system of the pump nozzle is driven by the electronic control hydraulic pressure, so that a rotating part can be avoided, the invention is very practical for an engine without a rotating mechanism, and the oil injection pressure is irrelevant to the rotating speed of the engine, so that the oil injection pressure of the engine can be ensured to be constant under various working conditions.
Drawings
FIG. 1 is a schematic diagram of a pump nozzle oil supply system in accordance with an embodiment of the present invention;
fig. 2 is a schematic view showing the structure of an oil supply system of a pump nozzle according to an embodiment of the present invention.
Detailed Description
The technical scheme of the invention is further explained by the specific implementation mode in combination with the attached drawings.
The general idea of the invention is: the hydraulic pressure is used for driving the hydraulic plunger to move in the plunger sleeve to replace the action of the cam driving force, the timing and the phase of the cam are replaced by the opening and closing time of a two-position three-way electromagnetic valve which is controlled electronically and connected in series in a hydraulic loop, and the oil supply quantity of the oil sprayer is controlled by controlling the electrifying time of the two-position three-way electromagnetic valve.
FIG. 1 is a schematic diagram of a pump nozzle oil supply system in accordance with an embodiment of the present invention. As shown in fig. 1, a hydraulic oil source system 1 is generated by hydraulic energy generated by a hydraulic free piston engine, and a two-position three-way electromagnetic valve 2 is connected in series in an oil passage. When the piston of the engine moves to a position needing oil injection, the two-position three-way electromagnetic valve is electrified to enable the ends a and b to be communicated, high-pressure oil enters the plunger sleeve 4 through the channel ab, the plunger 3 can overcome the elastic force of the return spring 10 to move upwards under the pushing of the high-pressure oil to push the tappet 6 to move upwards, the tappet pushes the push rod 7 to move upwards, the push rod moves upwards to enable the rocker arm 8 to rotate clockwise to compress the return spring, the plunger 9 of the oil injection pump moves downwards quickly to pressurize fuel oil, and the pressurized high-pressure fuel oil is injected into the cylinder through the oil injector 11.
When the two-position three-way electromagnetic valve is powered off, the two ends b and c of the electromagnetic valve are connected, high-pressure oil flows back to the oil tank through the bc channel, the oil injection pump plunger returns under the action of the return spring, the oil injector stops injecting oil, the oil injection process is finished, and one-time oil injection action is finished. The control of the oil injection amount in the system can be realized by changing the electrifying time of the two-position three-way electromagnetic valve, and the longer the electrifying time is, the more the oil injection amount is.
Fig. 2 is a schematic view showing the structure of an oil supply system of a pump nozzle according to an embodiment of the present invention. As shown in fig. 2, the two-position three-way electromagnetic valve 2 is connected in series to the corresponding positions of the high-pressure oil inlet duct 12 and the low-pressure oil outlet duct 15, and is fastened to the body 14 in a threaded connection manner, and the two-position three-way electromagnetic valve is a quick large-flow electromagnetic valve, the response time of which is not more than 3 milliseconds, and the flow rate of which is not less than 20 liters per minute. The high-pressure oil inlet duct 12 and the low-pressure oil outlet duct 15 are arranged at corresponding positions on the machine body in a drilling mode, the diameter of the high-pressure oil inlet duct 12 depends on the oil outlet pressure of an oil sprayer, the force of a return spring and the force of a push rod spring, the diameter of the high-pressure oil inlet duct is larger than that of an oil duct of an electromagnetic valve, the throttling effect is prevented from being generated, the timeliness of oil spraying is influenced, meanwhile, the diameter of the high-pressure oil inlet duct cannot be too large, a large volume effect can be generated, the timeliness of oil spraying can be influenced, and the diameter of the low-pressure oil outlet duct is larger than that of the high-pressure oil inlet duct. In addition, the diameter of the oil outlet passage depends on the flow of the used electromagnetic valve, namely the flow of the oil outlet passage is not less than the flow of the electromagnetic valve.
Plunger bushing 4 passes through the screw thread to be installed on the organism, and the plunger bushing is tubular structure, and the hole is high accuracy and plunger cooperation cylinder surface, and the outside is the shaft type structure of ladder, and the external screw thread is processed out on the great upper portion of external diameter to use the interior hole circle to process interior regular hexagon pit as the inscribed circle, be convenient for with spanner installation fastening screw thread, installation plunger bushing relevant position processes out the internal thread on the organism, and the plunger bushing passes through the screw thread to be installed on the organism, and plunger bushing axial position can pass through the gasket thickness adjustment on the plunger bushing bottom surface.
The oil path channel of the two-position three-way electromagnetic valve and the oil path channel in the plunger sleeve are communicated through an oil duct 13 processed in the engine body, the position of the plunger sleeve is corresponding to a roller of the tappet 6, the plunger 3 is arranged in the plunger sleeve 4 through clearance fit, and the diameter of the plunger 3 and the relation among the provided high-pressure oil pressure, the return spring force and the oil injection pressure of the oil injector are
Wherein d represents the diameter of the plunger 3, P represents the high pressure oil pressure,
F 1 indicating the return spring force, F 2 Indicating injector injection pressure.
The length of the plunger 3 is determined according to the maximum stroke of the plunger 9 of the injection pump and the required height of the guide, and the relationship between the length of the plunger 3 and the maximum stroke of the plunger 9 of the injection pump, namely the maximum circulating injection quantity and the required height of the guide is
Wherein Q max Representing the maximum fuel injection cycle, D the diameter of the injection pump plunger 9, l the minimum length required for normal guiding of the plunger 3, s the stroke of the plunger 3, λ the rocker ratio, h = s · λ the maximum stroke of the injection pump plunger 9, D the plunger diameter, the plunger length then being max { s, l }.
The diameter of the head of the plunger is larger than that of the lower part of the plunger, so that the plunger is convenient to contact with a tappet roller to transfer force, a certain pre-compression amount of a return spring is ensured in an initial installation state by adjusting a gap adjusting screw 16, the lower end of a push rod 7 is placed in the tappet, the upper end of the push rod is hinged with a rocker arm 8 through the gap adjusting screw, the other end of the rocker arm is pressed on an oil injection pump plunger 9, the diameter of the upper end of the oil injection pump plunger is larger, and the return spring is clamped between a protrusion of the oil injection pump plunger and an oil injector 11.
The concrete implementation steps of the electronic control hydraulic drive pump nozzle system on the hydraulic free piston engine comprise: when an engine piston moves to a position needing oil injection, the two-position three-way electromagnetic valve 2 is powered on and opened, a high-pressure oil inlet oil duct 12 is communicated with an oil path channel of the two-position three-way electromagnetic valve, high-pressure oil flows through the two-position three-way electromagnetic valve through the high-pressure oil inlet duct 12 and enters the plunger sleeve 4 through the oil duct 13, the high-pressure oil pushes the plunger 3 to move upwards along the plunger sleeve 4 and overcome the elastic force of the return spring 10, the plunger 3 pushes the tappet 6 to move upwards, the tappet drives the push rod 7 to move upwards, under the action of the push rod, the rocker arm 8 rotates clockwise around the axis of the rocker arm, the right end of the rocker arm moves downwards, the oil injection pump plunger 9 is pushed to move downwards to pressurize fuel, and high-pressure oil is injected through the oil injector 11. When the piston moves to the end of oil injection, the two-position three-way electromagnetic valve is powered off, the low-pressure oil outlet duct 15 and the oil path duct of the two-position three-way electromagnetic valve are communicated, high-pressure oil in the plunger sleeve flows back to the oil tank through the two-position three-way electromagnetic valve via the low-pressure oil outlet duct 15, the pressure is instantly reduced, the plunger of the oil injection pump starts to return under the action of a return spring, the oil injector stops oil injection, the rocker arm rotates anticlockwise around the axis of the rocker arm, the push rod, the tappet and the plunger return to the original positions under the driving of the rocker arm, the action of one-time oil injection is completed, and oil supply is realized.
The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the protection scope of the claims.
Claims (8)
1. The utility model provides a pump nozzle oil feeding system, is applicable to hydraulic pressure free piston engine, its characterized in that, includes first oil duct (12), second oil duct (15), two three way solenoid valve (2), third oil duct (13), plunger sleeve (4), first plunger (3), tappet (6), push rod (7), rocking arm (8), second plunger (9), return spring (10) and sprayer (11), first oil duct, the second oil duct respectively with hydraulic oil source system (1) intercommunication of hydraulic pressure free piston engine for provide, flow back high pressure oil, two three way solenoid valve with the plunger sleeve is installed on organism (14), two openings of two three way solenoid valve respectively with the other end of first oil duct, second oil duct is connected, another opening of two three way solenoid valve on the plug with the one end of third oil duct is connected, the other end of third oil duct with the plunger sleeve inner oil duct intercommunication, first plunger is installed in the sleeve, the one end of first plunger corresponds the one end of tappet, the lower extreme of push rod is placed in the tappet, the upper end of second plunger sleeve is connected through the return spring, the lower extreme of plunger is connected the second plunger is connected the return spring on the push rod.
2. The pump nozzle supply system of claim 1, further comprising a gap adjustment screw (16) on said push rod for adjusting the length of said push rod.
3. The system of claim 1, wherein said first plunger and said second plunger are T-shaped, having an upper end with a larger cross-sectional diameter than a lower end.
4. The system of claim 1, wherein the diameter of said first plunger is related to the pressure of the high pressure oil supplied, the return spring force, and the injector injection pressure
Wherein d represents the first plunger diameter, P represents the high oil pressure, F 1 Indicating return spring force, F 2 Indicating the fuel injection pressure of a fuel injector;
the relationship between the length of the first plunger and the maximum stroke of the second plunger, namely the maximum circulating fuel injection quantity and the required height of the guide is
l is more than or equal to 1.5d, wherein Q max Denotes the maximum circulating fuel injection quantity, DRepresenting the second plunger diameter, 1 representing the minimum length required for normal guidance of the first plunger, s representing the first plunger stroke, λ representing the rocker ratio, h = s · λ representing the second plunger maximum stroke, d representing the first plunger diameter, the plunger length then being max { s, l };
the flow of the oil outlet passage is not less than that of the two-position three-way electromagnetic valve.
5. The system as claimed in claim 1, wherein said two-position three-way solenoid valve and said plunger sleeve are threadedly mounted to said body.
6. The system as claimed in claim 5, wherein the plunger sleeve has a tubular structure, the inner hole has a cylindrical surface for engaging with the plunger, the outer portion has a stepped shaft structure, the upper portion having a larger outer diameter has an external thread, and has a hexagonal recess for receiving a fastening thread by a wrench, the body has an internal thread at a corresponding position, and the plunger sleeve is mounted on the body by the thread.
7. A method of supplying oil to a pump nozzle, comprising the steps of:
A. the two-position three-way electromagnetic valve is electrified and opened;
B. high-pressure oil enters the plunger sleeve through the two-position three-way electromagnetic valve and the first oil duct;
C. the high-pressure oil pushes the first plunger to move upwards along the plunger sleeve;
D. the first plunger pushes the tappet to move upwards, and the tappet drives the push rod to move upwards;
E. the push rod pushes the rocker arm to rotate clockwise around the axis of the rocker arm, and the other end of the rocker arm moves downwards;
F. the rocker arm pushes the second plunger to drive the fuel injector to pressurize and spray fuel, and a return spring sleeved on the second plunger is compressed;
G. when the two-position three-way electromagnetic valve is powered off, high-pressure oil in the plunger sleeve flows back to the oil tank through the second oil duct through the two-position three-way electromagnetic valve;
H. the return spring extends to drive the second plunger to return, and the rocker arm rotates anticlockwise around the axis of the rocker arm;
I. the push rod, the tappet and the first plunger return to the original positions under the driving of the rocker arm.
8. A method as claimed in claim 7, wherein the pre-compression of the return spring in the initial state of installation is provided by adjusting the gap adjustment screw.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007101757447A CN100510383C (en) | 2007-10-11 | 2007-10-11 | Pump nozzle oil supply system and method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2007101757447A CN100510383C (en) | 2007-10-11 | 2007-10-11 | Pump nozzle oil supply system and method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101131141A true CN101131141A (en) | 2008-02-27 |
| CN100510383C CN100510383C (en) | 2009-07-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2007101757447A Expired - Fee Related CN100510383C (en) | 2007-10-11 | 2007-10-11 | Pump nozzle oil supply system and method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100510383C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108757248A (en) * | 2018-07-09 | 2018-11-06 | 郑州航空工业管理学院 | Variable position adaptively switches the energy saving reciprocal fueller of two-way |
-
2007
- 2007-10-11 CN CNB2007101757447A patent/CN100510383C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108757248A (en) * | 2018-07-09 | 2018-11-06 | 郑州航空工业管理学院 | Variable position adaptively switches the energy saving reciprocal fueller of two-way |
| CN108757248B (en) * | 2018-07-09 | 2023-09-05 | 郑州航空工业管理学院 | Variable position self-adaptive switching double-path energy-saving reciprocating oil supply device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100510383C (en) | 2009-07-08 |
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Granted publication date: 20090708 Termination date: 20131011 |