CN111608835B - Gas-liquid double-control booster pump - Google Patents
Gas-liquid double-control booster pump Download PDFInfo
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- CN111608835B CN111608835B CN202010471723.5A CN202010471723A CN111608835B CN 111608835 B CN111608835 B CN 111608835B CN 202010471723 A CN202010471723 A CN 202010471723A CN 111608835 B CN111608835 B CN 111608835B
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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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
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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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The scheme relates to a gas-liquid double-control booster pump, which is characterized in that low-pressure gas or liquid is introduced into a gas-liquid double-control valve component to conduct a high-pressure fuel oil drainage oil duct in the booster pump, so that the boosting effect of the booster pump is improved. It includes: a booster pump body; a control cavity and a pressurization cavity are formed between the pressurization plunger and the pressurization pump body; a cone valve; an oil passage for allowing fuel oil passing through the cone valve to flow into the pressurizing cavity is arranged in the pressurizing plunger and is communicated with the control cavity through a throttling hole; the booster pump body is provided with a fuel outlet and a drainage oil duct; the gas-liquid double control valve assembly can realize the connection or disconnection between the drainage oil passage and the control cavity; when in pressurization, a low-pressure control medium (gas or liquid) is introduced into the gas-liquid double-control valve component to communicate the drainage oil duct and the control cavity, and the fuel oil entering the control cavity flows out through the drainage oil duct; in the fuel oil discharge process in the control cavity, the pressurizing plunger moves to block the fuel oil from flowing into the control cavity, and the fuel oil entering the pressurizing cavity is pressurized under the extrusion of the pressurizing plunger.
Description
Technical Field
The invention belongs to the field of booster pumps for ships, and particularly relates to a gas-liquid double-control booster pump.
Background
For a booster pump for a ship, in the prior art, fuel oil pressurization is usually realized by adopting an electric control booster pump, that is, a boosting cavity of fuel oil in the booster pump is driven to be pressurized when an electromagnetic valve is electrified. Specifically, as shown in fig. 1, the publication numbers are: CN110397533A discloses an electrically controlled booster pump, in which high-pressure fuel enters an oil inlet chamber through an oil inlet 242 at the upper end of an oil inlet joint 24 via an oil inlet channel 241; the steel ball 232 moves downwards under the action of hydraulic pressure, and the one-way valve 23 is opened; one part of the high-pressure fuel in the oil inlet cavity enters the pressurizing cavity 26 through the one-way valve fixing cavity 222 and flows out of the oil outlet channel 213, and the other part of the high-pressure fuel enters the pressurizing plunger cavity 25 through the throttling hole 221; when pressurization is needed, magnetic force is generated by electrifying the electromagnetic valve body 31, the armature 45 is attracted to move rightwards, the armature 45 drives the valve core 42 to overcome the elastic force of the electromagnetic valve spring 33 to move rightwards, so that the left end face of the pressure release valve 44 is separated from the right end port of the pressure release channel 211, and a gap is generated; at this time, the pressure relief passage 211 is communicated with the oil return passage 212, the high-pressure fuel in the pressurizing plunger cavity 25 flows out through the oil return passage 212, and the pressure in the pressurizing plunger cavity 25 is reduced; the pressure drop within the booster piston chamber 25 causes the booster piston 22 to move downward to continuously compress the booster chamber 27, thereby causing the fuel within the booster chamber 27 to be pressurized. The defect of the technical scheme is that, to the draining process and the pressurizing process before pressurizing, because the high-pressure fuel in the pressurizing plunger cavity 25 is from the oil inlet cavity, in the pressurizing process, the ball valve 232 forms a seal with the oil inlet valve seat 233 under the action of the spring 231, namely, the check valve 23 is closed, the high-pressure fuel in the oil inlet cavity completely and continuously enters the pressurizing plunger cavity 25, because the fuel in the oil inlet cavity has certain pressure, the continuous oil inlet in the pressurizing plunger cavity 25 can play a role in blocking the descending of the pressurizing plunger 22, the quick descending of the pressurizing plunger 22 is influenced, and the pressurizing effect of the electronic control pressurizing pump is poor.
Disclosure of Invention
The invention provides a gas-liquid double-control booster pump, which aims to improve the boosting effect of the booster pump.
The technical scheme of the invention is as follows:
the invention provides a gas-liquid double-control booster pump, which comprises:
a booster pump body;
the pressurizing plunger is movably arranged in an inner hole of the pressurizing pump body, and a control cavity and a pressurizing cavity are formed between the pressurizing plunger and the pressurizing pump body;
a cone valve mounted within the bore of the booster plunger;
an oil passage for enabling the fuel oil passing through the cone valve to flow into the pressurizing cavity is formed in the pressurizing plunger, and the oil passage can be communicated with the control cavity; the supercharging pump body is provided with a fuel outlet which enables the supercharged high-pressure fuel to flow out of the supercharging cavity and a leakage oil channel which enables the fuel in the control cavity to leak outwards;
the gas-liquid double control valve assembly is arranged on one side of the pressurizing pump body and can realize the connection or disconnection between the drainage oil passage and the control cavity;
before pressurization, a low-pressure control medium is not introduced into the gas-liquid double-control valve component, the control cavity is disconnected from the drainage oil duct, and fuel oil enters the pressurization cavity and the control cavity through an oil inlet duct in the cone valve and an oil duct of the pressurization plunger in sequence;
during pressurization, a low-pressure control medium is introduced into the gas-liquid double-control valve assembly to realize communication between the drainage oil duct and the control cavity, and the fuel oil entering the control cavity flows out through the drainage oil duct; meanwhile, in the process of discharging the fuel in the control cavity, the booster plunger moves towards one side of the booster cavity, the fuel is blocked from flowing into the control cavity from a flow passage in the booster plunger, and the fuel entering the booster cavity is pressurized under the extrusion of the booster plunger;
after pressurization, the high-pressure fuel in the pressurization cavity flows out through a fuel outlet of the pressurization pump body.
Preferably, the gas-liquid double-control booster pump further comprises:
the oil inlet joint is installed on one side of the booster pump body, the oil inlet joint gland fastens the oil inlet joint on the booster pump body in a threaded connection mode, and a fuel oil inlet channel communicated with the oil inlet channel in the cone valve is arranged on the oil inlet joint.
Preferably, the inner hole of the pressurizing pump body is a three-stage stepped hole arranged along the central axis direction of the pressurizing pump body, and the outer wall of the pressurizing plunger is formed into a step shape; the control cavity is formed between the first-stage step of the outer wall of the booster plunger and the first-stage inner hole of the booster pump body, the booster cavity is formed between the second-stage step of the outer wall of the booster plunger and the second-stage inner hole of the booster pump body, and the fuel outlet is formed in the third-stage inner hole of the booster pump body;
the double-control air flow booster pump further comprises:
the plunger spring is installed in the pressurization cavity, the plunger spring is partially sleeved on the outer wall of the pressurization plunger and forms a butt joint relation with the second-stage step of the outer wall of the pressurization plunger, and the plunger spring can be compressed or reset along with the movement of the pressurization plunger.
Preferably, the pressurizing plunger is provided with a two-step stepped hole therein along an axial direction thereof, and the cone valve includes:
the conical valve seat is fixedly arranged in a first-stage stepped hole in the pressurizing plunger, and an oil inlet channel for fuel oil to enter is formed in the conical valve seat;
the conical valve core can move in the first-stage stepped hole of the pressurizing plunger and the oil inlet channel of the conical valve seat, and a conical surface seal or a conical flow channel for fuel oil to pass through is formed between the conical valve core and the oil inlet channel of the conical valve seat;
and the cone valve spring is arranged between the first-stage stepped hole of the pressurizing plunger and the cone valve core and can be compressed or reset along with the movement of the cone valve core.
Preferably, an orifice hole for communicating the control chamber with the oil passage is provided in a hole wall of the second-stage stepped hole of the booster plunger.
Preferably, the gas-liquid double control valve assembly comprises:
the valve cover is fixed on one side of the booster pump body, and an accommodating cavity is formed between the valve cover and the booster pump body;
the valve core is movably arranged in the booster pump body and is used for realizing the connection or disconnection between the drain oil passage and the control cavity;
the piston is partially arranged in the accommodating cavity and is used for driving the valve core to move;
the pressure regulating spring is arranged in the accommodating cavity and is compressed or reset when the piston moves;
a low-pressure control medium flow passage for introducing a low-pressure control medium is formed on the valve cover and the pressurizing pump body, and the introduced low-pressure control medium is used for jacking the piston to drive the valve core to move so as to realize the communication between the drainage oil passage and the control cavity; when a low-pressure control medium is introduced into the control chamber through the low-pressure control medium flow passage, the low-pressure control medium entering below the piston pushes the piston to compress the pressure regulating spring, the piston drives the valve core to move in the forward direction, communication between the drainage oil passage and the control chamber is realized, and fuel oil entering the control chamber flows out through the drainage oil passage;
when the low-pressure control medium stops flowing in the low-pressure control medium flow passage or is not introduced, the pressure regulating spring in a compressed state rebounds to push the piston to move in the reverse direction, so that the valve core is driven to move in the reverse direction, the leakage oil passage is disconnected from the control cavity, and the fuel in the control cavity is blocked from flowing out.
Preferably, the low pressure control medium flow passage includes:
the first low-pressure control medium flow channel is formed on the valve cover, the second low-pressure control medium flow channel is formed on the booster pump body, and the first low-pressure control medium flow channel is communicated with the second low-pressure control medium flow channel;
and an outlet of the second low-pressure control medium flow passage is arranged at one end, close to the piston and far away from the pressure regulating spring, of the accommodating cavity.
Preferably, the valve cover is further provided with a vent hole which is used for communicating with the accommodating cavity so as to keep the constant atmospheric pressure in the accommodating cavity.
The invention has the beneficial effects that:
in the boosting process, when the fuel entering the control cavity in the oil charging stage is drained through the drainage oil duct, the boosting plunger moves towards one side of the boosting cavity synchronously so as to block the high-pressure fuel from continuing to enter the control cavity and compress the fuel in the boosting cavity, the high-pressure fuel in the boosting cavity is further pressurized, and when the control cavity is communicated with the oil tank through the drainage oil duct, the high-pressure fuel blocking the boosting plunger from descending is not continuously charged in the control cavity, so that the boosting plunger can be rapidly moved in place, and the boosting effect of the booster pump is improved. The control medium can be low-pressure hydraulic oil, water or compressed air, nitrogen, water vapor, natural gas and the like, and the range of the driving medium is wider. And the gas-liquid drive, no electric arc and spark, can use in the dangerous place, the operation is safe.
Drawings
FIG. 1 is a schematic diagram of a prior art electrically controlled booster pump;
FIG. 2 is a schematic sectional view of the gas-liquid double-control booster pump according to the present invention;
FIG. 3 is a schematic structural diagram of a gas-liquid double-control booster pump according to the present invention;
FIG. 4 is a view showing the structure of oil drainage between the pressurizing plunger and the pressurizing pump body according to the present invention;
FIG. 5 is an enlarged view of FIG. 4 at A;
fig. 6 is a schematic structural diagram of the gas-liquid double-control booster pump in the invention.
Detailed Description
Exemplary embodiments of the present invention will be described in more detail below with reference to the accompanying drawings. While exemplary embodiments of the invention are shown in the drawings, it should be understood that the invention can be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art.
The invention provides a gas-liquid double-control booster pump which is suitable for a high-pressure fuel system injection system of a high-power diesel engine and meets the requirements of the high-pressure fuel system of the diesel engine, wherein the rated rotating speed of the diesel engine is 1000-2000 r/min, the injection pressure is 90 MPa-150 MPa, and the flow rate is 0.5ml/cyl, and belongs to the field of high-pressure fuel booster pumps.
As shown in fig. 2 to 6, the gas-liquid double-control booster pump includes: a booster pump body 1; the booster pump comprises a booster plunger 2 movably arranged in an inner hole of a booster pump body 1, wherein a control cavity 101 and a booster cavity 102 are formed between the booster plunger 2 and the booster pump body 1; a cone valve mounted in the inner bore of the booster plunger 2; an oil channel 201 for enabling the fuel oil passing through the cone valve to flow into the pressurizing cavity 102 is arranged in the pressurizing plunger 2, and the oil channel 201 can be communicated with the control cavity 101; the booster pump body 1 is provided with a fuel outlet 104 for allowing the boosted high-pressure fuel to flow out of the booster cavity 102 and a drain oil passage 103 for draining the fuel in the control cavity 101 outwards; the gas-liquid double control valve assembly is arranged on one side of the pressurizing pump body 1 and can realize the connection or disconnection between the drainage oil passage 103 and the control cavity 101; before pressurization, a low-pressure control medium is not introduced into the gas-liquid double control valve assembly, the control cavity 101 and the drainage oil passage 103 are disconnected, and fuel oil enters the pressurization cavity 102 and the control cavity 101 through an oil inlet passage in the cone valve and an oil passage 201 of the pressurization plunger 2 in sequence; during pressurization, a low-pressure control medium is introduced into the gas-liquid double control valve assembly to realize communication between the drainage oil duct 103 and the control cavity 101, and fuel oil entering the control cavity 101 flows out through the drainage oil duct 103; meanwhile, in the process of discharging the fuel in the control cavity 101, the booster plunger 2 moves towards one side of the booster cavity 102, the fuel is blocked from flowing into the control cavity 101 from the oil passage 201 in the booster plunger 2, and the fuel entering the booster cavity 102 is pressurized under the extrusion of the booster plunger 2; after pressurization, the high-pressure fuel in the pressurization cavity 102 flows out through the fuel outlet 104 of the pressurization pump body 1.
The gas-liquid double-control booster pump takes gas (such as compressed air) or liquid (low-pressure water, oil and the like) as a control medium, the adopted medium is flexible, and a proper low-pressure control medium can be flexibly selected in the actual use based on the product of a ship.
When oil is filled, the oil duct 201 in the booster plunger 2 is communicated with the control cavity 101, fuel oil with certain pressure enters the booster pump body 1, the fuel oil is divided into two paths through the oil duct 201 in the booster plunger 2, one path of fuel oil flows into the booster cavity 202, the other path of fuel oil flows into the control cavity 101, at the moment, the fuel oil in the control cavity 101 does not leak outwards, and the oil inlet end and the oil outlet end of the booster plunger 2 are stressed to keep a balanced state.
When pressurization is needed, a low-pressure control medium with a certain pressure is introduced into the gas-liquid double control valve assembly, under the action of the low-pressure control medium, the state of the interior of the gas-liquid double control valve assembly is changed, fuel oil is blocked from flowing into the control cavity 101 from the oil duct 201 in the pressurization plunger, meanwhile, the fuel oil in the control cavity 101 is leaked outwards through the leakage oil duct 103, the fuel oil pressure in the control cavity 101 is reduced, and for the pressurization plunger 2, as the fuel oil pressure in the control cavity 101 is rapidly reduced, the stress at the oil outlet end of the pressurization plunger 2 is reduced, and the pressurization plunger 2 can not keep a balanced state any more and moves under the oil inlet pressure. In the process of the position movement of the pressurizing plunger 2, the oil passage 201 inside the pressurizing plunger 2 and the fuel oil in the control cavity 101 are blocked from flowing, and meanwhile, for the cone valve, when the position of the pressurizing plunger 2 moves, a closed state is formed, so that the high-pressure fuel oil can not enter the pressurizing plunger 2 any more. That is to say, in this embodiment, during the pressurization process, while the fuel entering the control cavity 101 at the oil filling stage is drained through the drainage oil duct 103, the pressurization plunger 2 moves towards one side of the pressurization cavity 102 synchronously, and simultaneously, the high-pressure fuel is blocked from entering the control cavity 101 and squeezing the pressurization cavity 102, the high-pressure fuel in the pressurization cavity 102 is further pressurized, when the control cavity 101 is communicated with the oil tank through the drainage oil duct 103, the control cavity 101 is not filled with the high-pressure fuel blocking the downward movement of the pressurization plunger 2 any more, so that the pressurization plunger 2 can move in place quickly, and the pressurization effect of the pressurization pump is further improved.
Meanwhile, the improvement of the present embodiment has a technical effect that the service life of the pressurizing plunger 2 can be prolonged, which is not existed in the prior art. The technical effect is caused because in the prior art, because the throttling hole is punched on the booster plunger, the booster plunger is always in a radial stress unbalanced state under the action of high-pressure fuel oil; because the coupling working surfaces of the booster plunger and the booster pump body belong to precise coupling, the unbalanced radial stress of the booster plunger can cause the coaxiality of the booster plunger and the booster pump body to be poor, the abrasion of the contact surfaces of the working sections of the booster plunger and the booster pump body can be accelerated, and the service life of the booster plunger is greatly shortened; meanwhile, in the prior art, the fuel entering the pressurizing plunger cavity and the pressurizing cavity is realized by respectively arranging one oil duct on the plunger, namely, the high-pressure fuel entering from the oil inlet joint is divided into two parts at the inlet of the pressurizing plunger, and the flow of the fuel entering the pressurizing plunger cavity through the throttling hole is far smaller than the flow of the fuel flowing into the plunger cavity through the one-way valve; in the prior art, after the one-way valve is closed, all high-pressure fuel entering the oil inlet joint flows into a pressurizing plunger cavity through the throttle hole, so that the problem of unbalanced radial stress of the pressurizing plunger is further solved, the abrasion between the pressurizing plunger and a pressurizing pump body is further increased, and the service life of the pressurizing plunger is further shortened. In the embodiment, the high-pressure fuel enters the oil passage 201 in the booster plunger 2 through the cone valve and then is divided into the control cavity 101 and the booster cavity 102; in the pressure boost in-process, the cone valve blocks that high-pressure fuel enters into pressure boost plunger 2 inside oil duct 201, and this can make in the pressure boost in-process, does not have high-pressure fuel and enters into pressure boost plunger 2 inside, does not have the radial unbalanced stress problem that exists among the prior art certainly, just also can avoid the wearing and tearing problem that leads to because of radial unbalanced stress, reaches the effect of extension pressure boost plunger 2's life.
Meanwhile, the improvement of the embodiment can also reduce the waste effect of high-pressure fuel in the pressurization process. The reason is that in the scheme in the prior art, in the pressurization process, although high-pressure fuel oil can not enter the pressurization cavity through the check valve, the high-pressure fuel oil which continuously enters all enters the pressurization plunger cavity through the throttle hole, and the high-pressure fuel oil in the pressurization plunger cavity can be continuously discharged to the outside in a pressure relief manner to the oil return tank because the electromagnetic valve is in the power-on state. For the booster pump, the fuel oil entering the oil inlet joint of the booster pump needs to be boosted to a certain extent, and in the prior art, the boosted fuel oil is completely wasted in the boosting stage, so that great energy loss is caused. That is, the prior art has the problem that oil is not completely filled and oil is not drained and is not crisp. The opening and closing of the oil drainage oil way are not realized by direct driving of the electromagnetic valve, the oil drainage oil way has the action factor depending on the self gravity of the sealing block, the working environment of the sealing block is not simple (high-pressure and low-pressure fuel oil is mixed), and the reliability of the system can be reduced by the design. In the embodiment, high-pressure fuel enters the oil passage 201 in the booster plunger 2 through the cone valve and then is distributed into the control cavity 101 and the booster cavity 102; in the pressurization process, the cone valve blocks high-pressure fuel oil from entering the oil duct 201 in the pressurization plunger 2, so that no high-pressure fuel oil enters the pressurization plunger 2 in the pressurization process; meanwhile, in the process of pressing the pressurizing cavity 102 by the pressurizing plunger 2, the communication between the oil passage 201 and the control cavity 101 is blocked, and the high-pressure fuel in the oil passage 201 can be prevented from being discharged and wasted. In summary, in the embodiment, in the pressurization process, the high-pressure fuel oil does not enter the control cavity 101 through the pressurization plunger 2 any more to be discharged in a pressure relief manner, so that the energy waste of the high-pressure fuel oil can be avoided, and the functions of complete oil filling and crisp oil drainage are achieved.
In addition, in the scheme of the prior art, the pressurizing plunger is stressed by a large amount and is complex, and the requirement on the strength of the used material is extremely high. The new design scheme transfers partial stress to the pressurizing pump body 1 with relatively simple stress condition, optimizes the working environment of the pressurizing plunger 2 on the premise of meeting the pressurizing effect, can prolong the service life of the pressurizing plunger 2, and further prolongs the service life of the whole system. The pressurizing plunger 2 after the working environment is optimized can save the cost on material selection and reduce the processing difficulty.
Of course, in this embodiment, in order to realize the entry of the high-pressure fuel, as shown in fig. 2, the gas-liquid dual-control booster pump further includes: install the oil feed joint 5 of the booster pump body 1 one side, oil feed joint gland 6 will through the threaded connection mode the fastening of oil feed joint 5 is in on the booster pump body 1, be provided with on the oil feed joint 5 with the fuel oil inlet 501 of the inside oil inlet intercommunication of cone valve.
In order to achieve the above technical effects, in the present embodiment, specific technical means for achieving the technical effects are provided.
As shown in fig. 2, 4 and 5, preferably, the inner hole of the pressurizing pump body 1 is a three-step stepped hole arranged along the central axis direction thereof, and the outer wall of the pressurizing plunger 2 is formed in a step shape; the control cavity 101 is formed between the first-stage step of the outer wall of the booster plunger 2 and the first-stage inner hole of the booster pump body 1, the booster cavity 102 is formed between the second-stage step of the outer wall of the booster plunger 2 and the second-stage inner hole of the booster pump body 1, and the fuel outlet 104 is formed in the third-stage inner hole of the booster pump body 1; the double-control air flow booster pump further comprises: and the plunger spring 7 is installed in the pressurization cavity 102, part of the plunger spring 7 is sleeved on the outer wall of the pressurization plunger 2 and forms an abutting relation with the second-stage step of the outer wall of the pressurization plunger 2, the plunger spring 7 can be compressed or reset along with the movement of the pressurization plunger 2, and for the pressurization plunger 2, a throttling hole 202 for communicating the control cavity 101 with the oil channel 201 is arranged on the hole wall of the second-stage step hole of the pressurization plunger 2. Along its axial direction be provided with two-stage shoulder hole in the pressure boost plunger 2, the cone valve includes: the conical valve seat 31 is fixedly arranged in a first-stage stepped hole in the pressurizing plunger 2, and the oil inlet channel for fuel oil to enter is formed in the conical valve seat 31; the conical valve core 32 can move in the first-stage stepped hole of the booster plunger 2 and the oil inlet channel of the conical valve seat 31, and a conical surface seal or a conical flow channel for fuel oil to pass through can be formed between the conical valve core 32 and the oil inlet channel of the conical valve seat 31; and a cone valve spring 33 installed between the first-stage stepped hole of the boost plunger 2 and the cone valve core 32, wherein the cone valve spring 33 can be compressed or reset along with the movement of the cone valve core 32.
Specifically, during oil filling, high-pressure fuel enters through the fuel inlet channel 501 of the fuel inlet joint 5, and then reaches the cavity formed among the booster plunger 2, the fuel inlet joint 5 and the cone valve seat 31, and then enters into the oil inlet channel of the cone valve seat 31, due to the fuel inlet pressure of the high-pressure fuel, the cone valve core 32 in a sealing state with the oil inlet channel of the cone valve seat 31 moves forward and compresses the cone valve spring 33, in the process, a cone flow channel is formed between the cone valve core 32 and the oil inlet channel of the cone valve seat 31 gradually, the high-pressure fuel further enters into the oil channel 201 of the booster plunger 2 through the cone flow channel, and is divided into two parts, one part of the high-pressure fuel flows into the booster cavity 102, and the other part of the high-pressure fuel flows into the control cavity 101 through the throttle hole. At this time, for the booster plunger 2, the booster plunger 2 is kept in a balanced state because the force applied to the oil inlet end of the booster plunger 2 is kept consistent with the force applied to the oil outlet end. In the pressurizing process, after the gas-liquid double control valve assembly conducts the control cavity 101 and the drainage oil duct 103, the high-pressure fuel in the control cavity 101 is gradually decompressed and discharged into the oil tank, the fuel pressure in the control cavity 101 is continuously reduced, the fuel pressure in the control cavity 101 is rapidly reduced, so that the stress of the oil outlet end of the pressurizing plunger 2 is smaller than that of the oil inlet end, the pressurizing plunger 2 moves towards one side of the plunger spring 7 under the oil pressure effect of the oil inlet end, the pressurizing cavity 102 is squeezed, and the high-pressure fuel stored in the pressurizing cavity is pressurized. Meanwhile, in the process that the booster plunger 2 extrudes the booster cavity 102, the cone valve core 32 reversely moves and is positioned between the cone valve seats 31 to form sealing under the action of the ultrahigh-pressure fuel oil pressure and the compressed cone valve spring 33, and the backflow of the high-pressure fuel oil in the booster cavity 102 is blocked.
Meanwhile, for the cone valve in the embodiment of the invention, the cone valve seat 31 and the cone valve core 32 form a cone sealing mode, which has a special effect as the prior art. In the prior art, the inside of the check valve is sealed by adopting a check ball valve. The ball valve seal belongs to line seal, and the sealing effect is poor; and because the rotation of the steel ball, the sealing line of the steel ball is constantly changed, which is very unfavorable for the work under the high-frequency and high-pressure environment and the uneven abrasion of the steel ball is caused, and the leakage is increased. In the embodiment, the cone valve check valve is used as the cone valve, the cone valve core 32 and the cone valve seat 31 form a cone surface seal, and the seal reliability can be ensured by the cone surface seal mode, so that the service life of the booster pump is prolonged while the reliability of the whole booster pump system is enhanced.
As shown in fig. 2 and 6, the gas-liquid dual control valve assembly includes: a valve cover 41 fixed to one side of the booster pump body 1 by a bolt 411, and an accommodating cavity 401 is formed between the valve cover 41 and the booster pump body 1; a valve spool 42 movably mounted in the booster pump body 1 for effecting communication or disconnection between the drain oil passage 103 and the control chamber 101; the piston 43 is partially arranged in the accommodating cavity 401 and is used for driving the valve core 42 to move; a pressure-regulating spring 44 installed in the housing chamber 401 and compressed or restored when the piston 43 moves; the valve cover 41 and the booster pump body 1 are provided with a low-pressure control medium which is introduced into a low-pressure control medium flow passage for introducing a low-pressure control medium into the accommodating cavity 401 and is used for jacking up the piston 43 to drive the valve core 42 to move, so that the communication between the leakage oil passage 103 and the control cavity 101 is realized; when a low-pressure control medium is introduced through the low-pressure control medium flow passage, gas or liquid entering the lower part of the piston 43 pushes the piston 43 to compress the pressure regulating spring 44, the piston 43 drives the valve core 42 to move in the forward direction, communication between the leakage flow oil passage 103 and the control cavity 101 is realized, and fuel oil entering the control cavity 101 flows out through the leakage flow oil passage 103; when the low-pressure control medium stops flowing or is not introduced into the low-pressure control medium flow passage, the pressure regulating spring 44 in a compressed state rebounds to push the piston 43 to move in the reverse direction, so that the valve core 42 is driven to move in the reverse direction, the leakage oil passage 103 is disconnected from the control cavity 101, and the fuel oil in the control cavity 101 is blocked from flowing outwards.
Specifically, a low-pressure control medium enters the position below the piston 43 through the control flow channel 402, the piston 43 is jacked up under the action of pressure, the piston 43 moves upwards to drive the valve core 42 to move upwards, the drain oil channel 103 is opened, the control cavities 101 and 103 are communicated, and then the two ends of the pressurizing plunger 2 are unbalanced in stress and move towards the pressurizing cavity 102. The control flow channel 402 on the gas-liquid double control valve is both an inlet flow channel and a return flow channel. When the low-pressure control medium flows back, the piston 43 returns quickly under the action of the force of the pressure regulating spring 43 and the gravity of the piston. The communication between the leakage oil passage 103 and the control cavity 101 is blocked, the pressurizing plunger 2 returns under the action of the plunger spring 7, and the control cavity 101 starts to build pressure. In the whole working process of the gas-liquid double control valve, the accommodating cavity 401 is always communicated with the external part through the vent hole 403, and the constant atmospheric pressure is kept.
Specifically, as shown in fig. 6, the low pressure control medium flow path includes: a first low-pressure control medium flow passage 402 formed in the valve cover 41 and a second low-pressure control medium flow passage 105 formed in the booster pump body 1, the first low-pressure control medium flow passage 402 and the second low-pressure control medium flow passage 105 being communicated; the outlet of the second low-pressure control medium flow passage 105 is disposed in the housing chamber 401 near an end of the piston 43 remote from the pressure regulating spring 44.
Meanwhile, as shown in fig. 6, the valve cover 41 is further provided with a vent hole 403 for discharging gas or liquid entering the accommodating chamber 401.
When a low-pressure control medium is not introduced, the piston 43 pushes the valve core 42 to block the control cavity 101 and the leakage oil passage 103 under the force of the pressure regulating spring 44; after the medium is introduced, the medium enters through the first low-pressure control medium flow channel 402 and the second low-pressure control medium flow channel 105, the end surface of the piston 43 compresses the pressure regulating spring 44 under the acting force of the low-pressure medium, and simultaneously, the valve core 42 is driven to move, so that the control cavity 101 is communicated with the leakage oil channel 103, and the high-pressure fuel oil in the control cavity 101 is discharged in a pressure and discharged outside. After pressurization is completed, the low-pressure control medium stops being introduced, the low-pressure control medium in the accommodating cavity 401 is discharged through the vent hole 403, the compressed pressure regulating spring 44 pushes the piston 43 to move, and then the valve core 42 is driven to block the control cavity 101 and the drainage oil passage 103, so that resetting is realized.
The gas-liquid double-control booster pump in the embodiment of the invention mainly comprises a booster pump body 1, an oil inlet joint 5, an oil inlet joint gland 6, a booster coupling part, a gas-liquid double-control valve component, a cone valve seat 31, a cone valve core 32 and a cone valve spring 33. The pressurizing matching part comprises a pressurizing plunger 2 and a plunger spring 7. The gas-liquid double control valve assembly comprises a valve core 42, a piston 43, a pressure regulating spring 44, a valve cover 41, a sealing ring 45 and a threaded plug 46.
Wherein, the end surface where the piston 43 is matched with the booster pump body 1 and the end surface where the booster pump body 1 is matched with the valve cover 41 are respectively provided with a sealing ring 45.
The oil inlet joint 5 and the booster pump body 1 adopt a plane compression sealing design, and the booster pump body 1, the conical valve seat 31 and the conical valve core 32 adopt a conical surface sealing design, so that the sealing of high-pressure fuel can be ensured.
The booster pump body 1 and the booster plunger 2 are designed by adopting two-stage hole shafts, the diameter ratio of the two-stage hole shafts is the designed boosting ratio of the gas-liquid double-control booster pump, different ratios can be designed according to the boosting requirements of different diesel engine high-pressure fuel systems, and the gas-liquid double-control booster pump can be suitable for high-pressure fuel systems with different boosting ratio requirements.
The booster plunger 2 and the booster pump body 1 are internally provided with inner holes as high-pressure oil passages, the plunger spring 7 is arranged in the second-stage inner hole of the booster pump body 1, and the cone valve core 32 and the cone valve spring 23 are arranged in the middle hole of the booster plunger 2. Two-stage design with different cross-sectional areas is adopted in the pressurizing pump body 1 and the pressurizing plunger 2, a control cavity 101 is arranged at one end of a large cross-sectional hole of the pressurizing pump body 1, the pressurizing plunger 2 is additionally provided with four throttling holes 202 for oil filling of the control cavity 101, and the pressurizing pump body 1 is additionally provided with a drainage oil passage 103 for oil drainage of the control cavity 101.
The gas-liquid double control valve assembly comprises a valve core 42, a piston 43, a pressure regulating spring 44, a valve cover 41, a sealing ring 45 and a threaded plug 46. The design has the advantages of high working pressure and reliability, simple and convenient installation and debugging and the like. The two-stage injection pressure and flexible oil injection rate can be realized in one-time oil injection process.
The oil inlet joint gland 6 fastens the oil inlet joint 5 on the booster pump body 1 in a threaded connection mode. The pressurizing plunger spring 7 and the pressurizing plunger 2 are arranged in the hole of the pressurizing pump body 1. The cone valve spring 33 and the cone valve core 32 are arranged in the pressurizing plunger 2, the cone valve seat 31 is coated with loctite glue through threads, and the pressurizing plunger 2 is screwed in to press the cone valve core 32 through the threaded connection.
One end of a valve core 42 of the gas-liquid double control valve is tightly pressed against a drainage oil channel 103 on the pressurizing pump body 41 to ensure sealing, one end of the valve core is connected with a piston 43 through threads, a pressure regulating spring 44 is installed at the top of the piston 43, the piston 43 is installed in a middle hole of a valve cover 41, the valve cover 41 is tightly connected with the pressurizing pump body 1 through a bolt 411, the lower part of the piston 43 is communicated with a low-pressure control medium through a hole system of the valve cover 41 and the pressurizing pump body 1, and a hole system processing hole of the low-pressure control.
The gas-liquid double-control booster pump is a high-pressure fuel oil gas-liquid double-control booster pump, and the valve core 42 is driven to reciprocate through the on-off of a gas-liquid double-control valve and the action of the piston 43, so that the opening and closing of an oil charging process and an oil discharging process of the control cavity 101 on the booster pump body 1 are controlled. The on-off frequency of the gas-liquid double control valve is controlled, so that the fuel oil supercharging frequency is accurately controlled, the matching with the rotating speed of the diesel engine is guaranteed, and the requirements of the diesel engine on various working conditions are met.
Oil filling stage: high-pressure fuel enters the pressurizing pump body 1 through the fuel inlet channel 501 of the fuel inlet joint 5, the conical valve core 32 in the pressurizing plunger 2 is opened under the action of hydraulic pressure, and the high-pressure fuel flows into the pressurizing cavity 102 at the other end of the pressurizing pump body 1 and flows out through the fuel outlet 104. At the same time, high-pressure fuel enters the control chamber 101 through the upper orifice 202 of the booster plunger 2. At this time, the pressures at the oil inlet end and the oil outlet end of the booster plunger 2 are kept balanced.
A pressurization stage: the gas-liquid double control valve is filled with compressed air or working oil to push the piston 43 to drive the valve core 42 to move upwards, the drainage oil passage is opened and communicated with the oil tank, high-pressure fuel oil in the control cavity 101 flows out through the drainage oil passage 103, the hydraulic pressure in the control cavity 101 is reduced, and the hydraulic pressure of the upper end surface and the lower end surface of the large section of the booster plunger 2 (namely the first-stage stepped surface 22 of the booster plunger 2 and the oil inlet end surface 21 facing the oil inlet joint 5) forms a certain difference value. Under the effect of hydraulic pressure, pressure boost plunger 2 overcomes the effect of plunger spring 7 spring force and moves right, and then presses the high-pressure fuel of small cross-section 23 lower extreme, and the high-pressure fuel forms super high pressure fuel by the pressure boost, and cone valve core 32 receives the effect of right-hand super high pressure fuel to close, and the orifice 202 on pressure boost plunger 2 is sheltered from by the pressure boost pump body 1 because of the right side of self-going, and super high pressure fuel flows out through pressure boost pump body 1 fuel export 105.
A reset stage: the ultrahigh pressure fuel flows out through the fuel outlet 105, the hydraulic pressure is reduced along with the ultrahigh pressure fuel, the plunger spring 7 pushes the pressurizing plunger 2 to rebound, the cone valve spring 33 is compressed, a gap is formed between the cone valve core 32 and the cone valve seat 32 under the pressure of the cone valve spring 33, namely the cone valve core 32 is opened, and the oil path is communicated. Meanwhile, the gas-liquid double control valve component stops low-pressure control medium, the low-pressure control medium flow channel is communicated with atmosphere or an oil tank, the piston 43 drives the valve core 42 to reset, and the drainage oil channel 103 at the control cavity 101 is closed again. High-pressure fuel enters the control cavity 101 through the throttle hole 202 on the booster plunger 2, the internal pressure of the control cavity 101 is increased, and the booster plunger 2 is reset under the action of hydraulic pressure and the plunger spring 7.
The supercharging frequency of the gas-liquid double-control booster pump is determined by the on-off frequency of the gas-liquid double-control valve, can be matched with the oil injection rule of each working condition of the diesel engine, and can be suitable for various diesel engines.
The gas-liquid double-control booster pump adopts the design, and has the advantages of high booster ratio, compact structure, good reliability, flexible control, quick response and the like. The requirements of high-pressure fuel systems of the diesel engine with the rated rotating speed of 1000-2000 r/min, the injection pressure of 90-150 MPa and the flow of 0.5ml/cyl are met.
The embodiments described above describe only some of the one or more embodiments of the present invention, but those skilled in the art will recognize that the invention can be embodied in many other forms without departing from the spirit or scope thereof. Accordingly, the present examples and embodiments are to be considered as illustrative and not restrictive, and various modifications and substitutions may be made therein without departing from the spirit and scope of the present invention as defined by the appended claims.
Claims (8)
1. A gas-liquid double-control booster pump is characterized by comprising:
a booster pump body (1);
the booster pump comprises a booster plunger (2) movably arranged in an inner hole of a booster pump body (1), wherein a control cavity (101) and a booster cavity (102) are formed between the booster plunger (2) and the booster pump body (1);
a cone valve arranged in an inner hole of the pressurizing plunger (2);
an oil duct (201) for enabling the fuel oil passing through the cone valve to flow into the pressurization cavity (102) is arranged in the pressurization plunger (2), and the oil duct (201) can be communicated with the control cavity (101); the booster pump body (1) is provided with a fuel outlet (104) for enabling the boosted high-pressure fuel to flow out from the booster cavity (102) and a drainage oil channel (103) for enabling the fuel in the control cavity (101) to drain outwards;
the gas-liquid double control valve assembly is arranged on one side of the pressurization pump body (1), and can realize the connection or disconnection between the drainage oil channel (103) and the control cavity (101);
before pressurization, a low-pressure control medium is not introduced into the gas-liquid double-control valve assembly, the control cavity (101) and the drainage oil passage (103) are disconnected, and fuel oil sequentially enters the pressurization cavity (102) and the control cavity (101) through an oil inlet passage in the cone valve and an oil passage (201) of the pressurization plunger (2);
during pressurization, a low-pressure control medium is introduced into the gas-liquid double-control valve assembly to realize communication between the drainage oil duct (103) and the control cavity (101), and fuel oil entering the control cavity (101) flows out through the drainage oil duct (103); meanwhile, in the process of discharging the fuel in the control cavity (101), the booster plunger (2) moves towards one side of the booster cavity (102), the fuel is blocked from flowing into the control cavity (101) from an oil passage (201) in the booster plunger, and the fuel entering the booster cavity (102) is pressurized under the extrusion of the booster plunger (2);
after pressurization, high-pressure fuel in the pressurization cavity (102) flows out through a fuel outlet (104) of the pressurization pump body (1).
2. The gas-liquid double-control booster pump according to claim 1, further comprising:
install oil feed joint (5) of the booster pump body (1) one side, oil feed joint gland (6) will through the threaded connection mode oil feed joint (5) fasten be in on the booster pump body (1), be provided with on oil feed joint (5) with fuel oil inlet (501) of the inside oil inlet intercommunication of cone valve.
3. The gas-liquid double-control booster pump according to claim 1, wherein the inner hole of the booster pump body (1) is a three-stage stepped hole arranged along the direction of the central axis thereof, and the outer wall of the booster plunger (2) is formed in a stepped shape;
the control cavity (101) is formed between the first-stage step of the outer wall of the booster plunger (2) and the first-stage inner hole of the booster pump body (1), the booster cavity (102) is formed between the second-stage step of the outer wall of the booster plunger (2) and the second-stage inner hole of the booster pump body (1), and the fuel outlet (104) is formed in the third-stage inner hole of the booster pump body (1);
the double-control gas-liquid booster pump further comprises:
the plunger spring (7) is installed in the pressurization cavity (102), the plunger spring (7) is partially sleeved on the outer wall of the pressurization plunger (2) and forms an abutting relation with the second-stage step of the outer wall of the pressurization plunger (2), and the plunger spring (7) can be compressed or reset along with the movement of the pressurization plunger (2).
4. The gas-liquid double-control booster pump according to claim 3, wherein two-stage stepped holes are formed in the booster plunger (2) along the axial direction thereof, and the cone valve comprises:
the conical valve seat (31) is fixedly arranged in a first-stage stepped hole in the pressurizing plunger (2), and an oil inlet channel for fuel oil to enter is formed in the conical valve seat (31);
the conical valve core (32) can move in a first-stage stepped hole of the pressurizing plunger (2) and an oil inlet channel of the conical valve seat (31), and a conical surface seal or a conical flow channel for fuel oil to pass through can be formed between the conical valve core (32) and the oil inlet channel of the conical valve seat (31);
and the cone valve spring (33) is arranged between the first-stage stepped hole of the pressurizing plunger (2) and the cone valve core (32), and the cone valve spring (33) can be compressed or reset along with the movement of the cone valve core (32).
5. The gas-liquid double-control booster pump according to claim 3, wherein a hole (202) for communicating the control chamber (101) and the oil passage (201) is formed in a hole wall of the second-stage stepped hole of the booster plunger (2).
6. The gas-liquid double control booster pump according to claim 1, wherein the gas-liquid double control valve assembly comprises:
the valve cover (41) is fixed on one side of the booster pump body (1), and an accommodating cavity (401) is formed between the valve cover (41) and the booster pump body (1);
a valve core (42) movably installed in the supercharging pump body (1) and used for realizing communication or disconnection between the leakage oil channel (103) and the control cavity (101);
the piston (43) is partially arranged in the accommodating cavity (401) and is used for driving the valve core (42) to move;
a pressure regulating spring (44) installed in the housing chamber (401) and compressed or restored when the piston (43) moves;
a low-pressure control medium flow channel for introducing a low-pressure control medium is formed on the valve cover (41) and the pressurization pump body (1), the introduced low-pressure control medium is used for jacking the piston (43) to drive the valve core (42) to move, and the communication between the drainage oil passage (103) and the control cavity (101) is realized;
when a low-pressure control medium is introduced through the low-pressure control medium flow passage, the low-pressure control medium entering the lower portion of the piston (43) pushes the piston (43) to compress the pressure regulating spring (44), the piston (43) drives the valve core (42) to move in the forward direction, communication between the drainage oil passage (103) and the control cavity (101) is achieved, and fuel oil entering the control cavity (101) flows out through the drainage oil passage (103);
when the low-pressure control medium flow channel stops or a low-pressure control medium is not introduced, the pressure regulating spring (44) in a compressed state resets to push the piston (43) to move reversely, so that the valve core (42) is driven to move reversely, the leakage oil channel (103) is disconnected from the control cavity (101), and fuel oil in the control cavity (101) is blocked from flowing outwards.
7. The gas-liquid double-control booster pump according to claim 6, wherein the low-pressure control medium flow passage includes:
a first low-pressure control medium flow passage (402) formed in the valve cover (41) and a second low-pressure control medium flow passage (105) formed in the booster pump body (1), the first low-pressure control medium flow passage (402) and the second low-pressure control medium flow passage (105) being communicated;
the outlet of the second low-pressure control medium flow passage (105) is arranged at one end, far away from the pressure regulating spring (44), of the piston (43) in the accommodating cavity (401).
8. The gas-liquid double-control booster pump according to claim 6, wherein the valve cover (41) is further provided with a vent hole (403) for communicating with the accommodating cavity (401) to maintain a constant atmospheric pressure in the accommodating cavity (401).
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010471723.5A CN111608835B (en) | 2020-05-29 | 2020-05-29 | Gas-liquid double-control booster pump |
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| CN202010471723.5A CN111608835B (en) | 2020-05-29 | 2020-05-29 | Gas-liquid double-control booster pump |
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| CN111608835B true CN111608835B (en) | 2021-04-20 |
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| CN113833575B (en) * | 2021-09-07 | 2023-03-21 | 四川航天中天动力装备有限责任公司 | Fuel pressure difference self-compensating bypass regulating valve for aircraft engine |
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| DE10123911A1 (en) * | 2001-05-17 | 2002-11-28 | Bosch Gmbh Robert | Fuel injection device for internal combustion engine has transfer piston separating chamber connected to source from high pressure and return chambers |
| DE102004010760A1 (en) * | 2004-03-05 | 2005-09-22 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines with Nadelhubdämpfung |
| CN102022241A (en) * | 2009-09-21 | 2011-04-20 | 欧阳光耀 | Electrically-controlled secondary booster for diesel engine |
| CN103452726A (en) * | 2013-09-03 | 2013-12-18 | 成都威特电喷有限责任公司 | Pressure control valve of high-pressure fuel passage |
| CN204716438U (en) * | 2014-10-11 | 2015-10-21 | 陈海龙 | High-power high voltage common rail diesel engine rail pressure strengthens pump |
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