CN210919305U - Marine low-speed machine electric control single high-pressure oil pump - Google Patents

Abstract

This scheme provides an automatically controlled monomer formula high-pressure oil pump of marine low-speed machine to the oil feed throttle and the oil feed oil pressure stability of high-pressure oil pump are improved in the realization. It includes: the pump comprises a pump body, a pump cover, an oil inlet and outlet valve assembly, a plunger coupling assembly, a plunger spring, a lower spring assembly, a guide piston assembly and an electric control proportional valve; the oil inlet and outlet valve assembly comprises: an oil inlet valve assembly and an oil outlet valve assembly; the inlet valve subassembly includes: the oil inlet valve seat, the oil inlet valve and the oil inlet valve spring; the delivery valve assembly comprises: the oil outlet valve seat, the oil outlet valve spring and the oil outlet valve spring seat; a high-pressure oil outlet cavity is formed between the oil outlet valve seat and the oil inlet valve seat; a high-pressure oil cavity is formed in the plunger and barrel assembly and is communicated with a high-pressure oil outlet cavity through an oil hole in the oil inlet valve seat; the electric control proportional valve is communicated with an oil inlet hole of the oil inlet valve seat through an oil hole in the pump body, and the oil inlet hole is communicated with or disconnected from the high-pressure oil cavity; and the electric control proportional valve is provided with a cooling circulation oil duct which is communicated with the cooling oil duct of the pump body, and the cooling circulation oil can cool the armature and the coil of the proportional valve.

Description

Marine low-speed machine electric control single high-pressure oil pump

Technical Field

The invention relates to the field of high-pressure oil pumps of marine low-speed machines, in particular to an electric control single high-pressure oil pump of a marine low-speed machine.

Background

Along with the stricter emission regulations at home and abroad, the marine low-speed diesel engine puts higher requirements on a fuel injection system, and the electronic control common rail fuel system can realize the accurate control of the timing and the circulating injection quantity of the injected fuel, and is one of effective means for realizing high fuel economy and low harmful substance emission of the high-power marine diesel engine. An electrically controlled unitary high-pressure oil pump is widely used as a common type of an electrically controlled common rail system oil pump. Because the traditional proportional valve is generally in a non-cooling structure and cannot meet the use environment of 750Cst high-temperature and high-viscosity heavy oil, the existing low-speed engine high-pressure oil pump is not provided with the proportional valve to improve the working efficiency of the existing low-speed engine high-pressure oil pump; the sealing surface of the existing single high-pressure oil pump of the low-speed machine is mostly special-shaped, is not beneficial to high-temperature and high-pressure heavy oil sealing, and has poor reliability and larger processing difficulty. The plunger and barrel assembly of the existing heavy oil high-pressure oil pump leaks heavy oil and discharges the heavy oil into the spring cavity at the upper part of the guide piston for collection, the design is changed, the total height of the spring cavity is increased, and meanwhile, the spring is exposed in the heavy oil and is easy to corrode.

Disclosure of Invention

The invention aims to provide an electric control single high-pressure oil pump of a low-speed machine for a ship, which aims to realize the effects of improving the oil inlet throttling and the oil inlet pressure stability of the high-pressure oil pump.

The invention provides an electric control single high-pressure oil pump of a marine low-speed engine, which comprises:

the pump body is provided with a middle hole along the axis direction;

the pump cover is arranged on the upper end face of the pump body;

the oil inlet and outlet valve assembly, the plunger matching part, the plunger spring, the lower spring seat assembly and the guide piston assembly are all assembled in a middle hole of the pump body;

the electric control proportional valve is assembled on the side surface of the pump body;

the oil inlet and outlet valve assembly comprises: an oil inlet valve assembly and an oil outlet valve assembly;

the oil feed valve assembly comprises: the oil inlet valve seat, the oil inlet valve and the oil inlet valve spring;

the oil inlet valve is arranged in a middle hole of the oil inlet valve seat; the oil inlet valve spring is limited between the oil inlet valve and the hole wall of the oil inlet valve seat; under the compression of the oil inlet valve spring, the oil inlet valve and the oil inlet valve seat form conical surface sealing;

the delivery valve assembly comprises: the oil outlet valve seat, the oil outlet valve spring and the oil outlet valve spring seat;

the oil outlet valve spring seat is arranged at the upper end of the oil outlet valve seat; the oil outlet valve is arranged in a middle hole of the oil outlet valve seat; the oil outlet valve spring is limited between the oil outlet valve and the oil outlet valve spring seat; under the compression of the oil outlet valve spring, the oil outlet valve and the oil outlet valve seat form conical surface sealing;

a high-pressure oil outlet cavity is formed between the oil outlet valve seat and the oil inlet valve seat;

a high-pressure oil cavity is formed in the plunger and barrel assembly and is communicated with the high-pressure oil outlet cavity through an oil hole in the oil inlet valve seat;

the electric control proportional valve is communicated with an oil inlet hole of the oil inlet valve seat through an oil hole in the pump body, and the oil inlet hole is communicated with or disconnected from the high-pressure oil cavity;

and the electric control proportional valve is provided with a cooling circulation oil passage, and cooling oil from the cooling oil passage of the pump body flows back to the cooling oil passage of the pump body after being injected into the cooling circulation oil passage.

Preferably, the plunger and barrel assembly comprises:

the plunger sleeve is arranged at the lower end of the oil inlet valve seat;

the plunger is slidably inserted into the middle hole of the plunger sleeve, and the high-pressure oil cavity is formed among the plunger sleeve, the plunger and the oil inlet valve seat;

the inner wall of the plunger sleeve is provided with a first ring groove and a second ring groove;

the pump body is provided with a mixed oil outlet channel and a lubricating oil channel, the mixed oil outlet channel is communicated with the first annular groove through the mixed oil channel on the plunger sleeve, and the lubricating oil channel is communicated with the second annular groove through the lubricating oil channel on the plunger sleeve;

the first ring groove is located above the second ring groove.

Preferably, the lower spring seat assembly is disposed below the plunger and barrel assembly, and the lower spring seat assembly includes:

the outer spring seat is of a boss type structure with a thin outer side and a thick middle part, and a counter bore in a concave spherical surface is formed in the upper end surface of the outer spring seat;

the lower part of the upper ball body is installed in the counter bore, and the lower end surface of the upper ball body is provided with a convex spherical surface matched with the concave spherical surface;

the inner spring seat is sleeved on the upper part of the upper ball body and is provided with an axial through hole penetrating through the upper end surface and the lower end surface;

the lower cylindrical head of the plunger is limited in the axial through hole, and the lower end face of the lower cylindrical head of the plunger is abutted to the upper end face of the upper ball body.

Preferably, a spherical hole is formed in the center of the counter bore, a third ring groove is formed in the lower end face of the outer spring seat, and the spherical hole is communicated with the third ring groove through a lubricating oil inlet oil passage;

the outer surface of the outer spring seat forms a conical surface, the conical surface is provided with a lubricating oil outlet duct, and the lubricating oil outlet duct is communicated with the lower end surface of the outer spring seat; the lubricating oil outlet duct is obliquely arranged;

a circumferential ring groove is formed in the circumferential direction of the upper sphere;

the positioning pin penetrates through a positioning pin hole of the outer spring seat and then is installed in the circumferential ring groove;

the interval between the upper surface of circumference annular and the lower surface is greater than the dowel is located the cylinder diameter of the part in the circumference annular.

Preferably, the axial through hole provided inside the inner spring seat includes:

a first hole, a second hole and a third hole of which the diameters are gradually increased from top to bottom;

a first guide hole with gradually increasing diameter is arranged between the second hole and the third hole;

one side of the third hole facing the upper ball body is provided with a second guide hole with the diameter gradually increasing;

the hole walls of the first guide hole and the second guide hole are formed into guide conical surfaces;

an upper portion of the upper sphere is located in the third bore through the second pilot bore portion;

a gap larger than or equal to 1mm is arranged between the upper ball body and the third hole;

and a clearance which is larger than or equal to 1mm is formed between the counter bore and the upper ball body.

Preferably, the method further comprises the following steps:

the upper spring seat is sleeved on the plunger sleeve and is positioned at the upper end of the inner spring seat;

the plunger spring includes:

a first plunger spring that is press-fitted between the upper spring seat and the outer spring seat;

a second plunger spring press-fitted between the upper spring seat and the inner spring seat.

Preferably, the diameters of the concave spherical surface in the outer spring seat and the convex spherical surface of the upper sphere are 20 to 100 times the diameter of the plunger.

Preferably, the pilot piston assembly comprises:

the center position of the upper end surface of the guide piston is provided with a first mounting hole; a second mounting hole is formed in the lower end face of the lower spring seat assembly, the first mounting hole is communicated with the second mounting hole through a communication hole, and the lower spring seat assembly is mounted in the first mounting hole;

a roller assembly comprising: the roller is arranged in the second mounting hole, the roller bushing is in interference fit in the roller, and the thrust bearings are in interference fit at the two axial ends of the roller; the annular groove is formed in the axial direction of the roller, and arc transitional connection is formed between the groove bottom of the annular groove and the axial end face of the roller.

A roller pin which is clearance fitted in the roller bushing;

a boss is arranged on the hole wall of the second mounting hole in a protruding mode and is in contact with the thrust bearing;

the boss has a plurality of first radial oil grooves evenly arranged along radial direction, first radial oil groove for thrust bearing sets up.

Preferably, the outer surface of the roller pin is a cylindrical surface, two positions on the cylindrical surface are respectively provided with two-step kidney-shaped grooves, and the kidney-shaped grooves are arranged in the middle of the roller pin;

a small-angle wedge-shaped groove with an angle between 5 and 10 degrees is formed between the kidney-shaped groove positioned on the outer layer and the outer surface of the roller bushing, and an oil hole is formed in the kidney-shaped groove positioned on the inner layer;

two oilholes of two positions department are through the lubricating oil delivery way intercommunication, are 90 settings between two oilholes.

Preferably, the outer surface of the guide piston is a cylindrical surface, a plurality of circumferential oil grooves, a first axial oil groove and a vertical groove are arranged on the cylindrical surface, the vertical groove is formed in the circumferential oil grooves, and the vertical groove is communicated with the circumferential oil grooves through the first axial oil groove;

the cylindrical surface is also provided with an inclined hole, and two ends of the inclined hole are respectively communicated with the circumferential oil groove and the inner wall of the second mounting hole;

the cylindrical surface is also provided with a second axial oil groove communicated with the circumferential oil groove;

the cylindrical surface is also provided with a first straight hole and a second straight hole which are connected, the first straight hole is communicated with the first axial oil groove, and the second straight hole is communicated with the first mounting hole;

and a lubricating oil inlet channel is arranged on the outer circular surface of the roller pin and is arranged opposite to the inclined hole, and the lubricating oil inlet channel is communicated with the lubricating oil outlet channel.

Preferably, the outer circle surface of the roller pin is provided with a DLC coating;

the roller bushing is made of copper alloy;

the thrust bearing is made of copper alloy;

forced lubrication is adopted between the roller pin and the roller bushing;

preferably, forced lubrication is adopted between the thrust bearing and the boss, and first chamfers are arranged on the excircle of the upper end surface of the guide piston, the excircle of the lower end surface of the guide piston and the circumferential oil ring groove;

a second chamfer is arranged on the wall of the first mounting hole;

a fourth hole is formed in the hole wall of the second mounting hole;

a fifth hole is formed in the outer circle surface of the roller pin;

and a spring and a stop pin are sequentially placed in the fifth hole, and the stop pin partially extends into the fourth hole.

Preferably, the lubricant oil inlet passage includes: the third radial oil passage is arranged along the radial direction of the roller pin, and the axial oil passage is arranged along the axial direction of the roller pin, and the third radial oil passage is connected with the axial oil passage; the axial oil passage is connected with the oil hole in the kidney-shaped groove.

The invention has the beneficial effects that:

(1) and the temperature of the existing mechanical adjusting mode can be solved by applying the electric control proportional valve to carry out oil inlet adjustment on the heavy oil. Specifically, a cooling circulation oil duct is arranged in the electric control proportional valve, so that cooling oil flowing in the pump body enters the electric control proportional valve, an electric control element in the electric control proportional valve is cooled specifically, the electric control element of the electric control proportional valve is kept within a normal temperature range, and the electric control proportional valve is allowed to perform oil-feeding throttling on the pump. The electric control proportional valve overcomes the defect of mechanical oil quantity regulation, improves the precision, flexibility and response speed of oil supply flow regulation, further realizes more accurate matching of the oil supply quantity of the pump and the operation working condition of the diesel engine, avoids performance reduction caused by insufficient oil supply, also reduces surplus flow during working, and further reduces the actual load of the pump;

(2) by additionally arranging the oil inlet valve assembly, the high-pressure oil cavity of the plunger sleeve is quickly closed when the high-pressure oil cavity is changed from oil absorption to compression, so that the pressure of the relevant position in the oil inlet channel of the oil inlet valve seat is ensured to be stable, and cavitation corrosion is effectively prevented;

(3) and the leakage of heavy oil can be completely prevented by using a small amount of lubricating oil in the second ring groove of the plunger matching part, and the leaked heavy oil is prevented from corroding important parts such as a plunger spring and the like below the plunger sleeve. In addition, this application seals heavy oil through a small amount of lubricating oil, can effectively reduce guide piston's vertical height (do not need the longer seal section that traditional low-speed machine set up on guide piston), and then reduces high-pressure oil pump's pump vertical height, alleviates high-pressure oil pump's total weight, learns according to the experiment, and the scheme of this application has reduced 1/3 with high-pressure oil pump's vertical height.

(4) The outer spring seat is of a boss type structure with a thin outer side and a thick middle part, the outer spring seat mainly bears the pressure transmitted to the upper ball body by the plunger during working, and a stress field caused by the pressure is distributed in the outer spring seat in a conical shape. The outer spring seat is arranged into a boss shape corresponding to the outer spring seat, so that the mass of the outer spring seat can be reduced under the condition of meeting the strength, the moving mass is further reduced, and a thicker part between bosses provides a design space for a middle spherical surface and an oil duct;

(4) the outer spring seat and the upper ball body form spherical surface matching, when the lower spring seat assembly with the spherical surface is arranged between the plunger and the guide piston, even if the upper end surface of the guide piston and the tail end surface of the plunger have larger parallelism errors, the spherical surface can be automatically adjusted in angle, so that the contact surface between the upper ball body and the outer spring seat is kept in full contact, local contact is eliminated, the whole stress is balanced, and the excessive trend of local stress is relieved. Meanwhile, the resultant force passes through the center of the spherical surface, so that the bending moment of the accessory is eliminated, the dynamic characteristic is optimized, and the bearing capacity of the system is improved.

(5) The spherical hole provides lubricating oil for the spherical surface to lubricate the spherical surface, and the lubricating oil is utilized to form an elastic flow lubricating effect on the spherical surface, so that the wear rate is reduced, the contact stress is reduced, the fretting damage is reduced, and the bearing capacity and the fatigue strength of the spherical surface are improved;

(5) the outer surface of the outer spring seat forms a conical surface, and the lubricating oil outlet oil duct is formed on the outer conical surface of the outer spring seat, so that the flow area of the lubricating oil outlet oil duct can be prevented from being covered by the plunger spring, and the flow area is not influenced by the position of the plunger spring;

(6) the inner spring seat is provided with the guide conical surface, so that the centering performance can be improved, the inner spring seat and the upper ball body can be automatically aligned even if the inner spring seat is impacted, and the trend of uneven stress is improved;

(7) the communicating hole is formed in the guide piston, so that lubricating oil above the guide piston is uniformly distributed in the middle right above the second mounting hole of the roller 7 when flowing down from the communicating hole, the lubricating oil is uniformly distributed on a roller bus, and the distribution of the lubricating oil on the surface of the roller is not influenced by positive and negative rotation (can be uniformly distributed); the vertical stress distribution of the guide piston is improved, namely the pressure of the plunger is distributed to a thicker position around the communicating hole, so that the integral stress is balanced, the maximum stress is reduced, and the reliability of the bearing capacity of the system is improved; when the guide piston is matched with the outer spring seat during pump assembly, the lubricating oil outlet channel of the outer spring seat is communicated with lubricating oil leaked above the plunger and barrel assembly, so that oil holes can be prevented from being blocked by springs, and the flow area of the lubricating oil is increased;

(8) the first radial oil groove formed in the boss is filled with lubricating oil, sufficient lubricating oil is provided for a moving surface (the end face of the roller assembly), a dynamic pressure oil film is formed on the end face of the roller by utilizing the moving speed of the end face of the roller, the boss of the guide piston is separated from the end face of the roller assembly, abrasion is reduced, and the friction coefficient is reduced. The first radial oil groove is formed on the boss of the guide piston, compared with the first radial oil groove formed on the roller assembly. The guide piston can not rotate relatively, the high-low pressure oil membrane area on the friction surface is distributed relatively still, and the axial direction of the roller component is relatively still;

(9) the included angle of two-step kidney-shaped grooves arranged in the roller pin is 70-120 degrees, and the two-step kidney-shaped grooves are positioned right above the pressure-bearing area, so that the influence of the kidney-shaped grooves formed on the surface on the area of the pressure-bearing area is reduced under the condition of ensuring that oil is sufficiently supplied to the friction surface, the angle of the pressure-bearing area is larger, and the average pressure of an oil film in the pressure-bearing area is smaller; a small-angle convergent wedge is formed by the kidney-shaped groove on the outer layer and the corresponding friction surface, so that the extrusion effect in dynamic pressure lubrication is enhanced; the kidney-shaped groove on the inner layer is mainly used for storing more lubricating oil, so that the sufficient oil supply to the friction surface is ensured, the lubrication on the surface of the roller pin is not influenced even if the oil supply is poor in a short time, and the probability of system seizure is reduced when a lubrication system has problems.

Drawings

FIG. 1 is a schematic structural view of the present invention;

FIG. 2 is a schematic structural view of an oil inlet and outlet valve assembly;

FIG. 3 is a schematic diagram of a prior art plunger and barrel assembly;

FIG. 4 is a schematic diagram of the cooperation between the plunger and barrel assembly and the pump body and between the oil inlet valve seat and the upper spring seat;

FIG. 5a is a schematic view of the structure of the plunger forming an included angle with the upper ball;

FIG. 5b is a schematic diagram of the engagement of the plunger and the upper sphere after adjustment of the spherical surface;

FIG. 6 is a schematic view of the lower spring seat assembly and the plunger assembly in mating configuration;

FIG. 7 is a cross-sectional view of the lower spring seat assembly;

FIG. 8 is a cross-sectional view of the lower spring seat assembly;

FIG. 9 is a schematic structural view of an inner spring seat;

FIG. 10 is a schematic structural view of an upper sphere;

FIG. 11 is a cross-sectional schematic view of an outer spring seat;

FIG. 12 is a cross-sectional schematic view of an outer spring seat;

FIG. 13 is a schematic cross-sectional view of a pilot piston assembly;

FIG. 14 is a schematic cross-sectional view of a pilot piston;

FIG. 15 is a schematic view of a pilot piston;

FIG. 16 is a schematic cross-sectional view of a pilot piston;

FIG. 17 is a schematic view of the roller pin;

FIG. 18 is an axial cross-sectional view of the roll pin;

FIG. 19 is a schematic radial cross-section of a roll pin;

FIG. 20a is a schematic view showing the distribution of the stress of the roller assembly without the ring groove;

FIG. 20b is a schematic view showing the distribution of the stress of the roller assembly having the ring grooves;

description of reference numerals: 1, a pump body; 12-a lube oil gallery; 2, pump cover; 3-oil inlet and outlet valve assembly; 31-an inlet valve assembly; 311-oil inlet valve seat; 312-oil inlet valve; 313-oil inlet valve spring; 32-an oil outlet valve component; 321-an oil outlet valve seat; 322-oil outlet valve; 323-outlet valve spring; 324-outlet valve spring seat; 33-high pressure oil outlet cavity; 4-plunger and barrel assembly; 41-high pressure oil chamber; 42-plunger sleeve; 421-a first ring groove; 422-second ring groove; 423-mixed oil duct; 424-lubricating oil duct; 43-a plunger; 431-lower cylindrical head; 5-plunger spring; 51 — a first plunger spring; 52-second plunger spring; 6-lower spring seat assembly; 61-outer spring seat; 611, counter bore; 612 — spherical pores; 613-third ring groove; 614-lubricating oil inlet duct; 615 — lubricant outlet channel; 616-positioning pin holes; 62, upper sphere; 621-circumferential ring groove; 63-inner spring seat; 631-axial through hole; 6311 — first hole; 6312 — second hole; 6313 — third hole; 6314 — first guide hole; 6315 — second guide hole; 6316 — guiding cone; 6317-escape slot; 6318 — lightening ring groove; 64-positioning pins; 7-a pilot piston assembly; 71-a pilot piston; 711 — first mounting hole; 7110-second chamfer; 712 — a second mounting hole; 7121-boss; 7122 — first radial oil groove; 7123-fourth well; 713-a communication hole; 714. 715-circumferential oil grooves; 716 — first axial oil groove; 717-vertical slots; 718-an inclined hole; 719 — second axial sump; 7100-first straight hole; 7101 — second straight hole; 7102-first chamfer; 72-a roller assembly; 721-rollers; 7211-ring groove; 722-roller bushings; 723-thrust bearing; 73-roller pin; 731. 732-kidney slot; 733. 734-oil hole; 735 — oil inlet channel; 7351 — a third radial gallery; 7352-axial oil gallery; 736 — fifth hole; 737-spring; 738-stop pin; 8-an electrically controlled proportional valve; 9-upper spring seat.

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.

Referring to fig. 1, the present invention provides a marine low-speed engine electric monoblock high-pressure oil pump, including:

the pump body 1, pump body 1 is equipped with the mesopore along the axis direction.

And the pump cover 2 is installed on the upper end surface of the pump body 1.

The oil inlet and outlet valve component 3, the plunger matching part 4, the plunger spring 5, the lower spring seat component 6 and the guide piston component 7 are all assembled in a middle hole of the pump body 1.

And an electrically controlled proportional valve 8 which is assembled on the side of the pump body 1.

The oil inlet and outlet valve assembly 3 comprises: an inlet valve assembly 31 and an outlet valve assembly 32.

The oil feed valve assembly 31 includes: an oil inlet valve seat 311, an oil inlet valve 312 and an oil inlet valve spring 313.

The oil inlet valve 312 is installed in the central hole of the oil inlet valve seat 311; the oil inlet valve spring 313 is limited between the oil inlet valve 312 and the hole wall of the oil inlet valve seat 311; under the compression of the oil inlet valve spring 313, the oil inlet valve 312 and the oil inlet valve seat 311 form a conical surface seal.

The delivery valve assembly 32 comprises: an oil outlet valve seat 321, an oil outlet valve 322, an oil outlet valve spring 323, and an oil outlet valve spring seat 324.

The oil outlet valve spring seat 324 is mounted on the upper end of the oil outlet valve seat 321; the oil outlet valve 322 is installed in the central hole of the oil outlet valve seat 321; the outlet valve spring 323 is restrained between the outlet valve 322 and the outlet valve spring seat 324; the oil outlet valve 322 forms a conical surface seal with the oil outlet valve seat 321 under the compression of the oil outlet valve spring 323.

A high pressure oil outlet chamber 33 is formed between the oil outlet valve seat 321 and the oil inlet valve seat 311.

A high-pressure oil chamber 41 is formed in the plunger and barrel assembly 4, and the high-pressure oil chamber 41 is communicated with the high-pressure oil outlet chamber 33 through an oil hole in the oil inlet valve seat 311.

The electric control proportional valve 8 is communicated with an oil inlet hole of the oil inlet valve seat 311 through an oil hole in the pump body 1, and the oil inlet hole is communicated with or disconnected from the high-pressure oil chamber 41.

The electric control proportional valve 8 is provided with a cooling circulation oil passage, and cooling oil from the cooling oil passage of the pump body 1 flows back to the cooling oil passage of the pump body 1 after being injected into the cooling circulation oil passage.

As shown in fig. 1, the central hole provided in the pump body 1 is a through hole penetrating both upper and lower end surfaces of the pump body 1. The pump cover 2 is fixed on the upper end face of the pump body 1, a mounting hole opposite to the middle hole of the pump body 1 is formed in the direction, facing the body 1, of the pump cover 2, and the oil outlet valve seat 321 is mounted in the middle hole of the pump body 1 and the mounting hole of the pump body 1.

As can be seen from fig. 1, the oil outlet valve assembly 32 is installed above the oil inlet valve assembly 31, and an oil passage communicating with the oil outlet valve assembly 32 is provided above the pump cover 2, and finally, the high-pressure heavy oil pumped out by the high-pressure oil pump of the present application is discharged through the oil passage on the pump cover 2.

The electric control proportional valve 8 is used as a hydraulic control device, which has an oil inlet throttling effect, the electric control proportional valve 8 is mainly used for oil inlet regulation and control of light oil (such as gasoline, diesel oil) and the like, and in the prior art, a scheme for applying the electric control proportional valve 8 to oil inlet regulation and control of heavy oil does not exist, because the temperature of the heavy oil can reach 160 ℃ when the heavy oil works, and the temperature exceeds the limit working temperature of electric control elements such as an armature, a coil and the like of the existing electric control proportional valve 8. In the prior art, the oil inlet throttling regulation of a high-pressure oil pump using heavy oil is in a mechanical transmission design, namely, the oil quantity is controlled through a speed regulator and a spiral groove above a plunger piston, and the oil inlet regulation mode has the defects of low oil quantity regulation precision, low correspondence speed, dependence of the oil quantity on the rotating speed of the speed regulator and the like.

In the embodiment of the application, the electric control proportional valve 8 is used for carrying out oil inlet adjustment on the heavy oil, and the temperature of the existing mechanical adjusting mode can be solved. Specifically, a cooling circulation oil passage is provided inside the electrically controlled proportional valve 8, so that the cooling oil flowing in the pump body 1 enters the electrically controlled proportional valve 8, and the electrically controlled element in the electrically controlled proportional valve 8 is cooled specifically, so that the electrically controlled element of the electrically controlled proportional valve 8 is kept within a normal temperature range. The cooling circulation oil passage designed in the electrically controlled proportional valve 8 should satisfy the following requirements: (1) the electric control elements such as a coil and an armature close to the electric control proportional valve as much as possible; (2) the flow of the cooling oil introduced into the cooling circulation oil passage can reduce the temperature of electric control elements such as a coil, an armature and the like to be within a working temperature range. In order to enable the cooling circulation oil passage to meet the requirements, simulation calculation and experiments are required to be performed in advance for armatures of different models, and specific parameter information such as spatial arrangement and size of the cooling circulation oil passage in each model is determined.

The design has the advantages that the cooling circulation oil passage is arranged in the electric control proportional valve 8, the temperature of the armature and the coil of the electric control proportional valve 8 is reduced, and the electric control element works in a normal temperature range, so that the electric control proportional valve 8 is allowed to be used for oil inlet throttling of the pump. The electric control proportional valve 8 overcomes the defect of mechanical oil quantity regulation, improves the precision, flexibility and response speed of oil supply flow regulation, further realizes more accurate matching of the oil supply quantity of the pump and the operation condition of the diesel engine, avoids performance reduction caused by insufficient oil supply, also reduces surplus flow during working, and further reduces the actual load of the pump.

As shown in fig. 2, in the oil filling stage, the oil inlet valve 312 is opened under the action of the oil inlet pressure of the electrically controlled proportional valve 8, the oil outlet valve 322 is sealed with the oil outlet valve seat 321 under the action of back pressure, the low-pressure heavy oil enters the high-pressure oil cavity 41 from the oil inlet, oil filling is started, and the oil inlet amount is controlled by adjusting the opening degree of the electrically controlled proportional valve 8 to meet different working condition requirements; in the oil pumping stage: the guide piston assembly 7 moves upward, the plunger 43 compresses the heavy oil in the high-pressure oil chamber 41, the pressure of the heavy oil gradually rises, when the pressure of the fuel oil in the high-pressure oil chamber 41 is greater than the pressure of the fuel oil, the fuel inlet valve 312 is closed, the high-pressure oil chamber 33 is connected with the high-pressure oil chamber 41, when the pressure of the fuel oil in the high-pressure oil chamber 41 exceeds the back pressure and the force of the fuel oil outlet valve spring 323, the fuel oil outlet valve 322 is opened, and the high-pressure fuel oil is discharged from the central hole of the pump. As shown in fig. 3, the previous high-pressure common rail heavy oil pump is of a mechanical design, and an oil inlet passage 505 is provided on plunger barrel 6, and plunger 5 is slidably inserted in plunger barrel 6, and no oil inlet valve assembly is provided. When the oil suction and compression are alternated, part of the pressurized fuel oil flows back to the low-pressure oil inlet channel from the oil inlet channel 505, so that the pressure change in the oil inlet channel 505 is large, and therefore, the cavitation of the relevant position of the oil inlet channel 505 is easy. This is also one of the main failure modes of the plunger and barrel assembly in the actual ship experiment. Compared with the prior art, the high-pressure oil cavity of the plunger sleeve 42 is quickly closed when the high-pressure oil cavity is changed from oil absorption to compression by additionally arranging the oil inlet valve assembly 31, so that the pressure stability of relevant positions in the oil inlet channel of the oil inlet valve seat 311 is ensured, and cavitation erosion is effectively prevented.

Referring to fig. 4, the plunger and barrel assembly 4 includes:

and a plunger sleeve 42 disposed at a lower end of the oil inlet valve seat 311.

And a plunger 43 slidably inserted into the central hole of the plunger sleeve 42, wherein the plunger sleeve 42, the plunger 43 and the oil inlet valve seat 311 together form the high-pressure oil chamber 41.

The inner wall of the plunger sleeve 42 is provided with a first ring groove 421 and a second ring groove 422.

Be provided with miscella oil outlet way and lubricating oil duct 12 on the pump body 1, the miscella oil outlet way passes through miscella oil duct 423 intercommunication on the plunger bushing 42 first annular 421, the miscella that forms in first annular 422 department flows out to the waste oil tank through this miscella oil outlet way and mixed oil duct 12, lubricating oil duct 12 passes through lubricating oil duct 424 on the plunger bushing 42 intercommunication second annular 422.

The first ring groove 421 is located above the second ring groove 422.

The lubricating oil entering the second annular groove 422 has 2 functions: 1. the fuel entering the gap between the plunger 43 and the plunger sleeve 42 from the high-pressure oil chamber 41 above the plunger 43 has a sealing effect, so that the fuel can be prevented from flowing into a transmission part below the plunger 43, and the fuel is prevented from invading into the transmission part below the plunger 43 to pollute a whole machine lubricating oil system; 2. the friction surfaces below the plunger 43 are all in a clean lubricating oil lubrication state, and the friction state of the plunger 43 is improved. Compared with the above heavy oil, the lubricating oil has high cleanliness, contains an additive for improving friction in the lubricating oil, and can form a better oil film compared with the lubricating oil lubricated by the heavy oil.

Since the conventional low-speed machine allows the heavy oil to leak below the plunger 43, the leaked heavy oil is separately collected. But the leaked heavy oil risks corroding the plunger spring 5 and other parts under the plunger 43. In the present application, the leakage of heavy oil can be completely prevented by using a small amount of lubricating oil in the second annular groove 422 of the plunger and barrel assembly 4, and the leaked heavy oil can be prevented from corroding important parts such as the plunger spring 5 below the plunger sleeve 42. In addition, because the complicated dynamic seal mechanism that is equipped with on the guide piston of traditional low-speed engine plunger below, lead to the whole vertical height of high-pressure oil pump great, characteristics such as cost height, this application is through the heavy oil of a small amount of lubricating oil seal, the vertical height of guide piston 71 that can effectively reduce (be equipped with longer heavy oil seal section on the traditional heavy oil guide piston), and then reduce the pump vertical height of high-pressure oil pump, alleviate the total weight of high-pressure oil pump, learn according to the experiment, the scheme of this application, 1/3 has been reduced with the vertical height of high-pressure oil pump.

Preferably, referring to fig. 6 to 12, the lower spring seat assembly 6 is disposed below the plunger and barrel assembly 4, and the lower spring seat assembly 6 includes:

the outer spring seat 61 is of a boss type structure with a thin outer side and a thick middle part, and during operation, the outer spring seat 61 mainly bears the pressure transmitted by the plunger 43 to the upper ball body, and a stress field caused by the pressure is distributed in the outer spring seat 61 in a conical shape. The outer spring seat 61 is set to be in a boss shape corresponding to the outer spring seat, the mass of the outer spring seat 61 can be reduced under the condition of meeting the strength, the moving mass is further reduced, and a thicker part between bosses provides a design space for the middle spherical surface and the oil duct.

A counter bore 611 in a concave spherical surface is formed in the upper end surface of the outer spring seat 61; and an upper ball 62, the lower part of which is installed in the counter bore 611, and the lower end surface of the upper ball 62 is provided with a convex spherical surface matched with the concave spherical surface.

And the inner spring seat 63 is sleeved on the upper part of the upper ball 62, and the inner spring seat 63 is provided with an axial through hole 631 penetrating through the upper end surface and the lower end surface.

The lower cylindrical head 431 of the plunger 43 is limited in the axial through hole 631, and the lower end surface of the lower cylindrical head 431 of the plunger 43 abuts against the upper end surface of the upper ball 62.

It is known from experiments that when the plunger operates, the parallelism error exists between the tail plane and the corresponding pressing surface (the guide piston or the spring seat surface), so that the local excessive stress on the tail plane of the plunger 43 may be caused when the plunger operates (as shown in fig. 5a, an included angle of β is formed between the upper ball 62 and the plunger 43), and the uneven stress distribution may generate an additional moment about the central plane of the plunger 43, thereby causing additional load and energy loss to the system, and affecting the dynamic characteristics of the system.

Preferably, referring to fig. 7 to 12, a spherical hole 612 is formed in the center of the counter bore 611, a third annular groove 613 is formed in the lower end surface of the outer spring seat 61, the spherical hole 612 and the third annular groove 613 are communicated through a lubricating oil inlet oil passage 614, the lubricating oil inlet oil passage 614 is communicated with an oil passage on the guide piston 7, and lubricating oil forms an oil film on the convex spherical surface of the outer spring seat 61 through the lubricating oil inlet oil passage 614, so that fretting wear damage between the convex spherical surface of the upper ball 62 and the concave spherical surface of the outer spring seat 61 can be effectively prevented; spherical hole 612 provides lubricating oil for the sphere, lubricates the sphere, utilizes the lubricating oil to form the elastohydrodynamic lubrication effect on the sphere, reduces wear rate, reduces contact stress, reduces fretting damage, improves the bearing capacity and fatigue strength of the sphere.

The outer surface of the outer spring seat 61 forms a conical surface, the conical surface is provided with a lubricating oil outlet channel 615, and the lubricating oil outlet channel 615 is communicated with the lower end surface of the outer spring seat 61; the lubricating oil outlet channel 615 is obliquely arranged; the main purpose of the lubricant outlet duct is to communicate the upper and lower regions of the outer spring seat 61, so that the lubricant above the outer spring seat 61 smoothly flows into the lower region, and the additional load caused by the compression of the lubricant by filling the lubricant chamber above the outer spring seat 61 is prevented. The lubricating oil outlet passage 615 is formed in the outer conical surface of the outer spring seat 61, so that the plunger spring 5 can be prevented from covering the flow area of the lubricating oil outlet passage 615, and the flow area is not affected by the position of the plunger spring 5.

Specifically, the number of the lubricating oil outlet passages 615 is specifically 8; the plurality of lubricating oil outlet passages 615 are respectively communicated to the bottom end surface of the outer spring seat 61. Lubricating oil in the upper space of the outer spring seat 61 can be ensured to flow out smoothly, and additional load caused by accumulation of the lubricating oil is avoided; meanwhile, the lubricating oil outlet channel 615 is obliquely arranged on the conical surface of the outer spring seat 61, so that accumulation caused by unsmooth circulation of lubricating oil due to the fact that the plunger spring 5 blocks the lubricating oil outlet channel 615 is also prevented.

The upper sphere 62 is provided with a circumferential ring groove 621 along the circumferential direction.

The positioning pin 64 is installed in the circumferential ring groove 621 after passing through the positioning pin hole 616 of the outer spring seat 61.

The distance between the upper surface and the lower surface of the circumferential ring groove 621 is larger than the cylindrical diameter of the portion of the positioning pin 64 located in the circumferential ring groove 621.

The upper ball 62 and the outer spring seat 61 are connected by a threaded locating pin 64, the locating pin 64 is fixed on the outer spring seat 61 by threads, the head of the locating pin 64 is a cylindrical surface, and a corresponding circumferential ring groove 621 is arranged on the upper ball 62 for installing the head of the pin is a locating part. The circumferential groove 621 of the upper ball 62 can also be a circular hole. The positioning pin 64 can substantially position the upper ball 62 and the outer spring seat 61, and prevent the upper ball 62 from falling out of the outer spring seat 61 during the reciprocating motion when the plunger 43 and the upper ball 62 are separated.

Preferably, as shown in fig. 9, the axial through hole 631 provided inside the inner spring seat 63 includes:

a first hole 6311, a second hole 6312, and a third hole 6313, which have diameters gradually increasing from top to bottom;

a first blind guide hole 6314 with a gradually increasing diameter is arranged between the second hole 632 and the third hole 6313;

a second guide hole 6315 having a gradually increasing diameter is formed in the third hole 6313 at a side facing the upper sphere 62;

the hole walls of the first guide hole 6314 and the second guide hole 6315 are formed as guide tapered surfaces 6316;

the upper portion of the upper sphere 62 is partially positioned in the third hole 6313 through the second guide hole 6315. Wherein the upper end surface of the lower cylindrical head 431 of the plunger 43 abuts against the upper end surface of the second hole 6312; the wall of the second bore 6312 annularly engages the lower cylindrical head 431 of the plunger 43. Since the hole walls of the first guide hole 6314 and the second guide hole 6315 are formed as the guide tapered surfaces 6316, if the plunger 43 and the upper ball 62 are separated or the inner spring seat 63 and the plunger 43 are separated, the guide tapered surfaces 6316 will automatically align the plunger 43 and the upper ball 62, the plunger 43 and the inner spring seat 63, and the inner spring seat 63 and the upper ball 62 when the plunger 43 hits the upper ball 62 again, so as to prevent large angular deviation and radial displacement between the plunger 43 and the inner spring seat 63, and between the inner spring seat 63 and the upper ball 62, thereby ensuring that the system is in a proper position even if the system hits, and balancing the overall stress. Specifically, when the plunger 43 snaps, the inner spring seat 63 is relatively stationary (i.e., snaps at an upper dead center), and the outer spring seat 61 and the upper ball 62 may reciprocally impact. The inner spring seat 63 and the plunger 43 may not be aligned with the upper ball 62 at the time of impact, resulting in a partial force at the time of impact. The inner spring seat 63 is provided with the guide conical surface 6316, so that the centering performance can be improved, the inner spring seat 63 and the upper ball 62 can be automatically aligned even if the inner spring seat is impacted, and the uneven stress tendency is improved.

The gap of 1mm or more is formed between the upper ball 62 and the third hole 6313, specifically, the gap of 1mm is formed between the outer cylindrical surface of the upper ball 62 and the hole wall of the third hole 6313, and because the outer spring seat 61 and the upper ball 62 are matched in a spherical manner and have a large (millimeter-sized) gap, the outer spring seat and the upper ball 62 can slide freely relatively, so that in the working process of the plunger, if an angle error exists between the lower end surface of the lower cylindrical head 431 of the plunger 43 and the upper end surface of the upper ball 62, when the plunger 43 moves downwards and impacts the upper ball 62, the upper ball 62 can slide relatively with the outer spring seat 61 to automatically compensate the angle error, and further, the lower end surface of the lower cylindrical head 431 of the plunger and the upper end surface of the guide piston 71 are stressed uniformly in an additional load, and local stress can be effectively prevented from being.

A clearance larger than or equal to 1mm is formed between the counter bore 611 and the upper ball 62, specifically, a clearance of 1mm is formed between the outer cylindrical surface of the upper ball 62 and the cylindrical surface of the counter bore 611, that is, a larger clearance (1 mm) is formed between the upper ball 62 and the inner spring seat 63, and a larger clearance (1 mm) is formed between the positioning pin 64 and the upper ball 62, between the positioning pin 62 and the outer spring seat 61, and between the upper ball 62 and the inner spring seat 63, so that the effective rotational freedom of the upper ball 62 during radial movement is not limited by the positioning pin 64, the effective rotational freedom of the plungers 43 and the upper ball 62 during radial movement is not limited by the inner spring seat 63, and the radial additional load of the plungers 43 is prevented.

Millimeter-scale gaps are reserved between the upper ball body 62 and the third hole 6313 and between the counter bore 611 and the upper ball body 62, macroscopic angle errors of the upper ball body 62 relative to the outer spring seat 61 are allowed, the spherical surface is prevented from being locked, the effect of eliminating local contact is achieved, the overall stress is balanced, and the effect of relieving the overlarge trend of the local stress is achieved.

In addition, as shown in fig. 9, relief grooves 6317 are formed on the outer circumferential surface of the inner spring seat 63 and the hole wall of the 4 th hole 6312; the upper end surface of the inner spring seat 63 is provided with a weight-reduction ring groove 6318 around the center axis.

Preferably, referring to fig. 1, further comprising:

an upper spring seat 9 which is provided on the plunger sleeve 42 and is located at the upper end of the inner spring seat 63;

the plunger spring 5 includes:

a first plunger spring 51 press-fitted between the upper spring seat 9 and the outer spring seat 61;

a second plunger spring 52 that is press-fitted between the upper spring seat 9 and the inner spring seat 63.

Preferably, the diameters of the concave spherical surface in the outer spring seat 61 and the convex spherical surface of the upper ball 62 are 20 to 100 times the diameter of the plunger 43. The parallelism error magnitude of the tail part of the plunger 43 and the upper end surface of the guide piston 71 is lower and is generally 0.01 magnitude, the requirement on the spherical angle adjusting capability is low, and therefore the small-angle spherical adjustment can also meet the angle adjusting requirement. When the spherical surface is large, only a small part of the acting force of the two surfaces is converted into tensile stress when the spherical surface is pressed, and for metal materials, the general compressive strength is higher than the tensile strength, and the compressive stress is not easy to cause fatigue, so that the tensile stress proportion can be reduced by selecting the large spherical surface, and the bearing capacity and the fatigue strength of the material are improved.

Preferably, with reference to fig. 13 to 19, the pilot piston assembly 7 comprises:

a first mounting hole 711 is formed in the center of the upper end surface of the guide piston 71; a second mounting hole 712 is formed in a lower end surface thereof, the first mounting hole 711 and the second mounting hole 712 communicate with each other through a communication hole 713, and the lower spring seat assembly 6 is mounted in the first mounting hole 711.

A roller assembly 72, comprising: a roller 721 installed in the second installation hole 712, a roller bushing 722 interference-fitted in the roller 721, and thrust bearings 723 interference-fitted at both axial ends of the roller 721; an annular groove 7211 is formed in the axial direction of the roller 721, and circular arc transitional connection is formed between the groove bottom of the annular groove 7211 and the axial end face of the roller 721.

Roller pin 73, which fits with clearance in the roller bushing 722.

The hole wall of the second mounting hole 712 is provided with a protruding boss 7121 in a protruding manner, and the boss 7121 is in contact with the thrust bearing 723.

The boss 7121 is uniformly arranged with a plurality of first radial oil grooves 7122 in a radial direction, and the first radial oil grooves 7122 are disposed opposite to the thrust bearing 723.

The roller bushing 722, the thrust bearing 723 and the roller 721 are in interference fit, so that the motion surface is reduced, and the motion speed of the friction surface is increased. In the dynamic pressure lubrication theory, the friction coefficient decreases as the relative movement speed of the friction surface increases within a certain range. Therefore, the relative movement speed is increased, the dynamic pressure lubrication effect is enhanced, a thicker dynamic pressure oil film is formed on the corresponding friction surface, solid contact is avoided, and the friction coefficient and abrasion are reduced.

Due to the communication hole, the following effects are achieved: (1) when the lubricating oil above the guide piston 71 flows down from the communicating hole 713, the lubricating oil is uniformly distributed right above the second mounting hole of the roller 721, the lubricating oil is uniformly distributed on the bus of the roller 721, and the lubricating oil is distributed on the surface of the roller 721 and is not influenced by positive and negative rotation (can be uniformly distributed); (2) the vertical stress distribution of the guide piston 71 is improved, namely the pressure of the plunger 43 is distributed to the thick position around the communication hole 713, so that the overall stress is balanced, the maximum stress is reduced, and the bearing capacity reliability of the system is improved. (in the traditional guide piston, a communication hole is arranged around the center, and the position of the communication hole is solid, so that the position is thin and the stress is large); (3) in the pump assembly, when the guide piston 71 is matched with the outer spring seat 61, the lubricating oil outlet channel 615 of the outer spring seat 61 is communicated with the lubricating oil leaked above the plunger and barrel assembly 4, so that oil holes can be prevented from being blocked by springs, and the actual flow area of the lubricating oil is increased.

The ring groove 7211 is formed by machining the inner hole and the outer circle of the roller 721 after finish machining, as shown in fig. 20a and 20b, the rigidity of the two ends of the roller 721 is reduced due to the arrangement of the ring groove 7211, when the surface of the roller 721 is subjected to radial pressure, the roller 721 near the ring groove 7211 can be automatically deformed at present, meanwhile, after the ring groove 7211 is machined, the outer circle and the inner hole of the roller 721 automatically collapse, micro arc surfaces are formed at the two ends of the inner hole and the outer circle of the roller 721, the concentration of geometric stress at the two ends of the roller 721 is reduced, and further the stress on the surface. (geometric stress concentration: when the surface of the roller 721 is stressed, the contact stress of the two ends of the generatrix of the roller 721 is obviously larger than that of the middle). The groove wall of the ring groove 7211 is formed into an arc shape, which can effectively weaken the collective stress concentration existing on the outer cylindrical surface of the roller 721 in the rotation process of the roller 721 and the side pressure effect of the inner hole of the roller 721, so that the stress distribution of the inner and outer working surfaces of the roller assembly 72 is balanced, and the probability of seizure between the roller assembly 72 and the roller pin 73 is reduced.

The bosses 7121 and corresponding friction surfaces (end faces of the roller assemblies) form a thrust bearing model. Namely, the first radial oil groove 7122 is filled with lubricating oil to provide sufficient lubricating oil for the moving surface (the end surface of the roller assembly), and a dynamic pressure oil film is formed on the end surface of the roller 721 by utilizing the moving speed of the end surface of the roller 721 to separate the boss 7121 of the guide piston 71 from the end surface of the roller assembly 72, so that the abrasion is reduced, and the friction coefficient is reduced. The first radial oil groove 7122 is formed on the boss 7121 of the guide piston 71, as compared with the roller assembly 72. The guide piston 71 does not rotate relatively, the high and low pressure oil film areas on the friction surfaces are distributed relatively still, and the roller assembly 72 is axially relatively still. If the first radial oil groove is formed in the moving component (the end face of the roller component 72), the relative movement of the first radial oil groove relative to the guide piston 71 causes the oil film to be distributed and move relatively, and further causes the roller 721 to vibrate in an axial direction unnecessarily and reduce the overall dynamic performance.

For roller 721, roller 721 is designed with end-grooving deformations to reduce boundary stresses; specifically, for the roller 721, when the roller 721 is machined, the outer circle of the roller 721 and the inner hole of the roller are firstly ground, then the grooving machining of the annular grooves 7211 on the two axial end faces is carried out, after the grooving machining is completed, the generatrix of the outer circle and the inner hole of the roller 721 is naturally deformed into an arc line, so that the geometric stress concentration existing on the outer cylindrical surface of the roller and the side pressure effect of the inner hole of the roller 721 in the rotation process of the roller 721 can be effectively weakened, the stress distribution of the inner working surface and the outer working surface of the roller assembly 72 is balanced, and the probability of seizure between the roller assembly 72 and the roller pin 73 is. The roller bushing 722 and the roller 721 are in interference fit, so that the relative speed between the moving surface of the roller bushing 722 and the roller pin 73 is increased, the end surface of the roller bushing 722 moves at a high speed to form an effective dynamic pressure oil film with the roller pin 73, the dynamic pressure lubrication effect is improved, and the probability of seizure between the roller bushing 722 and the roller pin 73 is reduced; the roller 721 and the thrust bearing 723 are in interference fit, so that the relative speed between the moving surface of the thrust bearing 723 and the boss 7121 is increased, the end surface of the thrust bearing 723 moves at a high speed to form an effective dynamic pressure oil film with the boss 7121, the boss 7121 and the thrust bearing 723 can be prevented from being tightly attached, excessive wear caused by insufficient oil supply to the end surface of the thrust bearing 723 can be avoided, the dynamic pressure lubricating effect can be improved due to the formation of the dynamic pressure oil film, and the possibility of seizure between the thrust bearing 723 and the boss 7121 can be reduced.

Preferably, as shown in fig. 17, the outer surface of the roller pin 73 is a cylindrical surface, two- step kidney slots 731 and 732 are respectively arranged at two positions on the cylindrical surface, and the kidney slots 731 and 732 are arranged at the middle position of the roller pin 73; the arrangement of the slender kidney-shaped grooves enables the lubricating oil in the kidney-shaped grooves 731 and 732 to have larger contact area with corresponding friction surfaces, and makes full use of the movement speed of the corresponding moving surfaces to bring more lubricating oil into the bearing surface to form a dynamic pressure oil film, thereby forming a thicker lubricating oil film. The two sides of the kidney-shaped groove 731 are kidney-shaped, so that the stress concentration caused by the grooving on the surface of the roller pin 73 is reduced. The two-step oil waist grooves 731 and 732 increase the surface lubrication flow rate.

A small-angle wedge-shaped groove with an angle of 5-10 degrees is formed between the kidney-shaped groove 731 on the outer layer and the outer surface of the roller bushing 722, and oil holes 733 and 734 are arranged in the kidney-shaped groove 732 on the inner layer; the included angle of the two kidney-shaped grooves is 70-120 degrees (the actual value can be determined according to a simulation calculation result, and can be selected as 90 degrees in an example), and the two kidney-shaped grooves are positioned right above the pressure-bearing area, so that the influence of the kidney-shaped grooves on the surface on the area of the pressure-bearing area is reduced under the condition of ensuring that oil is fully supplied to a friction surface, the angle of the pressure-bearing area is larger, and the average pressure of an oil film in the pressure-bearing area is smaller; a small-angle convergent wedge is formed by the outer-layer kidney-shaped groove 731 and the corresponding friction surface, so that the extrusion effect in dynamic pressure lubrication is enhanced; the inner layer kidney-shaped groove 732 is mainly used for storing more lubricating oil, so that sufficient oil supply is ensured for the friction surface, the lubrication on the surface of the roller pin is not influenced even if the oil supply is poor in a short time, and the probability of system seizure is reduced when a lubrication system has problems; the two oil holes 733 and 734 at the two positions are communicated through the lubricant oil outlet passage, and the two oil holes 733 and 734 are arranged at 90 degrees.

Preferably, as shown in fig. 15 and 16, the outer surface of the pilot piston 71 is a cylindrical surface, on which a plurality of circumferential oil grooves 714 and 715, a first axial oil groove 716 and a vertical groove 717 are arranged, the vertical groove 717 is opened in the circumferential oil groove 715, and the vertical groove 717 is communicated with the circumferential oil groove 714 through the first axial oil groove 716; and 1-10-degree chamfers are arranged between the two sides of the circumferential oil groove 715 and the upper end and the lower end of the guide piston, and the chamfers and the corresponding moving surfaces form a small-angle convergent wedge during movement, so that the extrusion effect in dynamic pressure lubrication is enhanced. The surface lubrication state of the guide piston 71 is improved, a thicker dynamic pressure oil film is built, friction is reduced, and the probability of seizure is reduced. According to relevant data and experiments, when the chamfer angle is too large (such as 45 degrees or 90 degrees), the chamfer angle cannot enhance lubrication, but has a scraping effect on a corresponding friction surface, so that surface lubricating oil is scraped off, and the lubricating effect is reduced.

An inclined hole 718 is further formed in the cylindrical surface, and two ends of the inclined hole 718 are respectively communicated with the circumferential oil groove 715 and the inner wall of the second mounting hole 712.

And a second axial oil groove 719 communicated with the circumferential oil groove 715 is further arranged on the cylindrical surface.

The cylindrical surface is also provided with a first straight hole 7100 and a second straight hole 7101 which are connected, the first straight hole 7100 is communicated with the first axial oil groove 716, and the second straight hole 7101 is communicated with the first mounting hole 711; the first and second straight bores 7100 and 7101 supply oil to the lower spring seat assembly 6 inside the pilot piston 71, reducing wear on the corresponding moving surfaces.

And a lubricating oil inlet channel 735 is arranged on the outer circular surface of the roller pin 73, the lubricating oil inlet channel 735 is arranged opposite to the inclined hole 718, and the lubricating oil inlet channel 735 is communicated with the lubricating oil outlet channel.

Preferably, the outer circle surface of the roller pin 73 is provided with a DLC coating; the DLC coating has high hardness, small friction coefficient, wear resistance and high temperature resistance, when the lubrication between the roller bushing 722 and the roller pin 73 is poor, the friction pair consisting of the DLC coating and the roller bushing 722 of the copper alloy bearing can still well run, and the probability of seizing between the roller pin 73 and the roller bushing 722 can be further reduced;

the roller bushing 722 is made of copper alloy.

The thrust bearing 723 is made of a copper alloy.

Forced lubrication is employed between the roller pin 723 and the roller bushing 722.

And forced lubrication is adopted between the thrust bearing 723 and the boss 7121.

The roller bushing 722 and the thrust bearing 723 are made of bronze alloy, and the friction characteristics of the bronze alloy such as low friction coefficient, good wear resistance, self-lubrication and impact resistance are utilized to improve the friction characteristics of the inner hole and the end face of the roller assembly 72 and the corresponding moving surface when solid friction exists, so that the friction coefficient is reduced, the impact resistance is improved, and the bearing capacity is improved.

Preferably, as shown in fig. 13, 14 and 18, the outer circle of the upper end face and the outer circle of the lower end face of the guide piston 71 and the circumferential ring groove 715 are provided with first chamfers 7102;

a second chamfer 7110 is arranged on the hole wall of the first mounting hole 711.

A fourth hole 7123 is formed in the wall of the second mounting hole 712;

a fifth hole 736 is provided on the outer circumferential surface of the roller pin 73;

a spring 737 and a stop pin 738 are sequentially disposed in the fifth hole 736, and the stop pin 738 partially extends into the fourth hole 7123. The fifth hole 736 is provided for receiving the stop pin 738, so that the roller pin 73 and the guide piston 71 are relatively stationary, the number of the relatively moving surfaces of the roller pin 71 and the roller 721 is reduced, the speed of the relatively moving surfaces is increased, and the dynamic pressure lubrication effect is enhanced (the principle is the same as that of the interference fit between the roller and the bushing). Specifically, when the roller assembly 72 and the roller pin 73 are assembled to the guide piston 71, the roller bushing 722 and the thrust bearing 723 are first mounted to the roller 721 in a cold-fitting manner; then, the spring 737 and the stop pin 738 are sequentially placed into the fifth hole 736 of the roller pin 73; then, the roller assembly 72 is placed at the lower part of the guide piston 71, and a roller pin 73 sequentially penetrates through one side of a fourth hole at the lower end of the guide piston 71, an inner hole (specifically, an inner hole of a roller bush) of the roller assembly and the other side of the fourth hole at the lower end of the guide piston; then, the stopper pin 738 is manually pressed to a height lower than the second mounting hole 712, while the roller pin 73 is pushed until the stopper pin 738 is sprung into the fourth hole 7123 of the guide piston 71 by the spring 737. That is, the lubricating oil flowing out of the fuel injection pump body 1 flows into the circumferential oil groove 715 through the second axial oil groove 719 and then flows into the circumferential oil groove 714 through the vertical groove 717 and the first axial oil groove 716, lubrication between the pilot piston 71 and the fuel injection pump body 1 is achieved, and since the clearance between the pilot piston 71 and the center hole of the pump body 1 fitted thereto is small, the lubricating oil entering into the second axial oil groove 719 of the pilot piston 71 and the circumferential oil groove 715 maintains a certain pressure, and a lubricating oil film can be formed between the outer circumference of the pilot piston 71 and the center hole of the pump body 1; meanwhile, the lubricating oil portion in the second axial oil groove 719 flows into the lubricating oil inlet oil passage 735 through the inclined hole 718 to penetrate deeply into the roller pin 73, and then flows out to the outer circumferential surface of the roller pin 73 through the oil holes 733 and 734 to deeply lubricate between the roller pin 73 and the rolling bush 722, forming a lubricating oil film between the roller pin 73 and the rolling bush 722.

The angle range of the first chamfer 7102 and the second chamfer 7110 is between 1 degree and 10 degrees, a small-angle convergent wedge can be formed when the guide piston 71 is matched with a middle hole in the pump body 1, the extrusion effect in dynamic pressure lubrication is enhanced, the thickness of an oil film on the surface of the guide piston 71 during operation is increased, and therefore the probability of seizure between the guide piston 71 and the pump body 1 is reduced.

Preferably, as shown in fig. 18 and 19, the lubricant oil inlet passage 735 includes: a third radial oil passage 7351 provided in the radial direction of the roller pin 73 and an axial oil passage 7352 provided in the axial direction of the roller pin 73, the third radial oil passage 7351 being connected to the axial oil passage 7352; the axial oil passage 7351 is connected to the oil holes 733, 734 in the kidney groove 732.

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 (10)

1. An electrically controlled monoblock high pressure oil pump for a marine low speed machine, comprising:

the pump body (1), the said pump body (1) has mesopores along the direction of axial line;

the pump cover (2), the pump cover (2) is installed on the upper end face of the pump body (1);

the oil inlet and outlet valve assembly (3), the plunger matching part (4), the plunger spring (5), the lower spring seat assembly (6) and the guide piston assembly (7) are all assembled in a middle hole of the pump body (1);

an electrically controlled proportional valve (8) fitted on the lateral surface of the pump body (1);

the oil inlet and outlet valve assembly (3) comprises: an oil inlet valve assembly (31) and an oil outlet valve assembly (32);

the oil feed valve assembly (31) includes: the oil inlet valve comprises an oil inlet valve seat (311), an oil inlet valve (312) and an oil inlet valve spring (313);

the oil inlet valve (312) is arranged in a middle hole of the oil inlet valve seat (311); the oil inlet valve spring (313) is limited between the oil inlet valve (312) and the hole wall of the oil inlet valve seat (311); under the compression of the oil inlet valve spring (313), the oil inlet valve (312) and the oil inlet valve seat (311) form conical surface sealing;

the oil outlet valve assembly (32) comprises: an oil outlet valve seat (321), an oil outlet valve (322), an oil outlet valve spring (323) and an oil outlet valve spring seat (324);

the oil outlet valve spring seat (324) is arranged at the upper end of the oil outlet valve seat (321); the oil outlet valve (322) is arranged in a middle hole of the oil outlet valve seat (321); the outlet valve spring (323) is limited between the outlet valve (322) and the outlet valve spring seat (324); under the compression of the oil outlet valve spring (323), the oil outlet valve (322) and the oil outlet valve seat (321) form conical surface sealing;

a high-pressure oil outlet cavity (33) is formed between the oil outlet valve seat (321) and the oil inlet valve seat (311);

a high-pressure oil cavity (41) is formed in the plunger and barrel assembly (4), and the high-pressure oil cavity (41) is communicated with the high-pressure oil outlet cavity (33) through an oil hole in the oil inlet valve seat (311);

the electric control proportional valve (8) is communicated with an oil inlet hole of the oil inlet valve seat (311) through an oil hole in the pump body (1), and the oil inlet hole is communicated with or disconnected from the high-pressure oil cavity (41);

and a cooling circulation oil passage is arranged on the electric control proportional valve (8), and cooling oil from the cooling oil passage of the pump body (1) flows back to the cooling oil passage of the pump body (1) after being injected into the cooling circulation oil passage.

2. The oil pump, as set forth in claim 1, characterized in that the plunger and barrel assembly (4) comprises:

a plunger sleeve (42) arranged at the lower end of the oil inlet valve seat (311);

a plunger (43) slidably inserted into a central bore of the plunger sleeve (42), the plunger (43) and the oil inlet valve seat (311) collectively forming the high-pressure oil chamber (41) therebetween;

the inner wall of the plunger sleeve (42) is provided with a first ring groove (421) and a second ring groove (422);

a mixed oil outlet channel and a lubricating oil channel (12) are arranged on the pump body (1), the mixed oil outlet channel is communicated with the first ring groove (421) through a mixed oil channel (423) on the plunger sleeve (42), and the lubricating oil channel (12) is communicated with the second ring groove (422) through a lubricating oil channel (424) on the plunger sleeve (42);

the first ring groove (421) is positioned above the second ring groove (422).

3. The oil pump according to claim 2, characterized in that the lower spring retainer assembly (6) is disposed below the plunger and barrel assembly (4), the lower spring retainer assembly (6) comprising:

the outer spring seat (61) is of a boss type structure with a thin outer side and a thick middle part, and a counter bore (611) which is a concave spherical surface is formed in the upper end surface of the outer spring seat (61);

an upper ball (62) with a lower portion mounted in the counter bore (611), wherein a lower end surface of the upper ball (62) is provided with a convex spherical surface matched with the concave spherical surface;

the inner spring seat (63) is sleeved on the upper part of the upper ball body (62), and the inner spring seat (63) is provided with an axial through hole (631) penetrating through the upper end surface and the lower end surface;

the lower cylindrical head (431) of the plunger (43) is limited in the axial through hole (631), and the lower end surface of the lower cylindrical head (431) of the plunger (43) is abutted to the upper end surface of the upper ball (62).

4. The oil pump of claim 3,

a spherical hole (612) is formed in the center of the counter bore (611), a third annular groove (613) is formed in the lower end face of the outer spring seat (61), and the spherical hole (612) is communicated with the third annular groove (613) through a lubricating oil inlet oil passage (614);

the outer surface of the outer spring seat (61) forms a conical surface, the conical surface is provided with a lubricating oil outlet duct (615), and the lubricating oil outlet duct (615) is communicated with the lower end surface of the outer spring seat (61); the lubricating oil outlet channel (615) is obliquely arranged;

a circumferential ring groove (621) is formed in the circumferential direction of the upper sphere (62);

the positioning pin (64) is installed in the circumferential ring groove (621) after penetrating through the positioning pin hole (616) of the outer spring seat (61);

the distance between the upper surface and the lower surface of the circumferential ring groove (621) is larger than the cylindrical diameter of the part of the positioning pin (64) located in the circumferential ring groove (621).

5. The oil pump of claim 3,

the inside axial through hole (631) that sets up of interior spring holder (63) includes:

a first hole (6311), a second hole (6312) and a third hole (6313) of gradually increasing diameters from top to bottom;

a first guide hole (6314) with the diameter gradually increasing is arranged between the second hole (6312) and the third hole (6313);

the third hole (6313) is provided with a second guide hole (6315) having a gradually increasing diameter toward the side of the upper sphere (62);

the hole walls of the first guide hole (6314) and the second guide hole (6315) are formed as guide tapered surfaces (6316);

the upper part of the upper sphere (62) is partially positioned in the third hole (6313) through the second guide hole (6315);

a gap of greater than or equal to 1mm is provided between the upper sphere (62) and the third bore (6313);

a clearance larger than or equal to 1mm is arranged between the counter bore (611) and the upper ball body (62).

6. The oil pump of claim 4, further comprising:

the upper spring seat (9) is sleeved on the plunger sleeve (42) and is positioned at the upper end of the inner spring seat (63);

the plunger spring (5) includes:

a first plunger spring (51) that is press-fitted between the upper spring seat (9) and the outer spring seat (61);

a second plunger spring (52) press-fitted between the upper spring seat (9) and the inner spring seat (63).

7. The oil pump, as set forth in claim 1, characterized in that the pilot piston assembly (7) comprises:

a first mounting hole (711) is formed in the center of the upper end face of the guide piston (71); a second mounting hole (712) is formed in the lower end face of the lower spring seat assembly, the first mounting hole (711) is communicated with the second mounting hole (712) through a communication hole (713), and the lower spring seat assembly (6) is mounted in the first mounting hole (711);

a roller assembly (72) comprising: a roller (721) installed in the second installation hole (712), a roller bushing (722) interference-fitted in the roller (721), and thrust bearings (723) interference-fitted at both axial ends of the roller (721); an annular groove (7211) is formed in the axial direction of the roller (721), and arc transition connection is formed between the groove bottom of the annular groove (7211) and the axial end face of the roller (721);

a roller pin (73) which fits with clearance in the roller bushing (722);

a boss (7121) is arranged on the hole wall of the second mounting hole (712) in a protruding mode, and the boss (7121) is in contact with the thrust bearing (723);

the boss (7121) is uniformly provided with a plurality of first radial oil grooves (7122) along the radial direction, and the first radial oil grooves (7122) are arranged relative to the thrust bearing (723).

8. The oil pump of claim 7,

the outer surface of the roller pin (73) is a cylindrical surface, two-step kidney-shaped grooves (731, 732) are respectively arranged at two positions on the cylindrical surface, and the kidney-shaped grooves (731, 732) are arranged at the middle position of the roller pin (73);

a small-angle wedge-shaped groove with an angle between 5 and 20 degrees is formed between the kidney-shaped groove (731) positioned on the outer layer and the outer surface of the roller bushing (722), and oil holes (733, 734) are arranged in the kidney-shaped groove (732) positioned on the inner layer;

the two oil holes (733, 734) at the two positions are communicated through a lubricating oil outlet channel, and the two oil holes (733, 734) are arranged at an angle of 70-120 degrees.

9. The oil pump of claim 8,

the outer surface of the guide piston (71) is a cylindrical surface, a plurality of circumferential oil grooves (714, 715), a first axial oil groove (716) and a vertical groove (717) are arranged on the cylindrical surface, the vertical groove (717) is arranged in the circumferential oil groove (715), and the vertical groove (717) is communicated with the circumferential oil groove (714) through the first axial oil groove (716);

an inclined hole (718) is further formed in the cylindrical surface, and two ends of the inclined hole (718) are respectively communicated with the circumferential oil groove (715) and the inner wall of the second mounting hole (712);

a second axial oil groove (719) communicated with the circumferential oil groove (715) is further formed in the cylindrical surface;

the cylindrical surface is also provided with a first straight hole (7100) and a second straight hole (7101) which are connected, the first straight hole (7100) is communicated with the first axial oil groove (716), and the second straight hole (7101) is communicated with the first mounting hole (711);

be provided with lubricating oil inlet way (735) on the excircle face of gyro wheel pin (73), lubricating oil inlet way (735) is relative inclined hole (718) set up, lubricating oil inlet way (735) intercommunication lubricating oil outlet way.

10. The oil pump of claim 9,

the excircle of the upper end face and the excircle of the lower end face of the guide piston (71) and the circumferential oil groove (715) are respectively provided with a first chamfer (7102); a second chamfer (7110) is arranged on the wall of the first mounting hole (711);

a fourth hole (7123) is arranged on the wall of the second mounting hole (712);

a fifth hole (736) is formed in the outer circle surface of the roller pin (73);

a spring (737) and a stop pin (738) are sequentially placed in the fifth hole (736), and the stop pin (738) partially extends into the fourth hole (7123).

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