CN110685841A - Multi-cylinder combined high-pressure oil pump of marine low-speed engine - Google Patents

Multi-cylinder combined high-pressure oil pump of marine low-speed engine Download PDF

Info

Publication number
CN110685841A
CN110685841A CN201911088467.5A CN201911088467A CN110685841A CN 110685841 A CN110685841 A CN 110685841A CN 201911088467 A CN201911088467 A CN 201911088467A CN 110685841 A CN110685841 A CN 110685841A
Authority
CN
China
Prior art keywords
oil
plunger
cavity
valve
communicated
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201911088467.5A
Other languages
Chinese (zh)
Inventor
涂天华
杜兵
侯旭洪
林小雪
郭海堂
陈超
许强
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Chongqing Hongjiang Machinery Co Ltd
Original Assignee
Chongqing Hongjiang Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Chongqing Hongjiang Machinery Co Ltd filed Critical Chongqing Hongjiang Machinery Co Ltd
Priority to CN201911088467.5A priority Critical patent/CN110685841A/en
Publication of CN110685841A publication Critical patent/CN110685841A/en
Priority to PCT/CN2020/086386 priority patent/WO2021088324A1/en
Priority to FI20215003A priority patent/FI129983B/en
Priority to DE112020000519.4T priority patent/DE112020000519T5/en
Priority to GB2019140.9A priority patent/GB2594544B/en
Pending legal-status Critical Current

Links

Images

Classifications

    • 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • 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
    • F02M59/10—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 characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
    • 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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • 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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • 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
    • F02M59/462—Delivery valves

Abstract

The invention relates to a multi-cylinder combined high-pressure oil pump of a marine low-speed engine, which has the advantages that the electronic control, the oil circuit layering and the optimized sealing structure improve the oil supply regulation sensitivity and the heavy oil reliability of the high-pressure oil pump, simultaneously expand the application range of the heavy oil of the low-speed engine and meet the use environment of the heavy oil of 750 Cst. It includes: a pump body assembly comprising: the pump body is provided with a first horizontal middle hole and a plurality of first vertical middle holes, and the first horizontal middle holes are communicated with the first vertical middle holes; the pump cover is arranged on the upper side of the pump body and is provided with a second horizontal middle hole and a plurality of second vertical middle holes which are communicated; the vertical middle hole formed by the first vertical middle hole and the second vertical middle hole is internally provided with: the plunger matching part, the plunger spring, the lower spring seat and the guide piston assembly are arranged on the upper end of the plunger matching part; the plunger and barrel assembly is screwed in the second vertical middle hole and is internally provided with an oil inlet and outlet valve assembly; the cam shaft is arranged in a first horizontal middle hole of the pump body; a cooling circulation oil way is arranged in the electric control proportional valve; a mixed oil path is arranged in the pump cover.

Description

Multi-cylinder combined high-pressure oil pump of marine low-speed engine
Technical Field
The invention relates to the field of fuel oil systems of marine low-speed engines, in particular to a multi-cylinder combined high-pressure oil pump of a marine low-speed engine.
Background
The electronic control common rail fuel system can realize accurate control of timing and circulating fuel injection quantity of fuel injection, and is one of effective means for realizing high fuel economy and low harmful substance emission of a high-power marine diesel engine. The existing mechanical single high-pressure oil pump, common rail pipe, ICU and mechanical oil injector system of the low-speed engine fuel system realizes the flexible control of the injection timing and the circulating injection quantity of the low-speed engine, but has certain limitation on the flexible regulation of the circulating oil supply quantity and the oil supply frequency of the high-pressure oil pump, and is not beneficial to the pressure fluctuation control of the common rail. The existing combined oil pump proportional valve is generally of a non-cooling structure and cannot meet the use environment of 750Cst high-temperature high-viscosity heavy oil; the bolt is used for connecting the column plug sleeve, and the sealing surface of the bolt is special-shaped, so that the reliability of high-temperature and high-pressure heavy oil sealing is not facilitated, and the processing difficulty is high.
Disclosure of Invention
The invention aims to provide a multi-cylinder combined high-pressure oil pump of a marine low-speed engine, which has the advantages that the electronic control, oil circuit layering and optimized sealing structure are adopted to improve the oil supply regulation sensitivity and the heavy oil reliability of the high-pressure oil pump, the application range of heavy oil of the low-speed engine is expanded, and the use environment of the heavy oil of 750Cst is met.
The invention provides a multi-cylinder combined high-pressure oil pump of a marine low-speed engine, which comprises: a pump body assembly, comprising: the pump body is provided with a first horizontal middle hole and a plurality of first vertical middle holes, and the first horizontal middle holes are communicated with the first vertical middle holes;
the pump cover is arranged on the upper side of the pump body and provided with a second horizontal middle hole and a plurality of second vertical middle holes, each second vertical middle hole is communicated with the second horizontal middle hole, and one first vertical middle hole is correspondingly communicated with one second vertical middle hole; an electric control proportional valve and a heavy oil outlet interface are mounted on the pump cover;
and the vertical middle hole formed by the first vertical middle hole and the second vertical middle hole is internally provided with the following components in sequence from top to bottom: the plunger matching part, the plunger spring, the lower spring seat and the guide piston assembly are arranged on the upper end of the plunger matching part;
the plunger and barrel assembly is in threaded connection with the second vertical middle hole, and an oil inlet and outlet valve assembly is installed in the plunger and barrel assembly; the low-pressure heavy oil output by the electric control proportional valve is transferred by the oil inlet and outlet valve assembly and then flows into the plunger volume cavity of the plunger matching part, and the high-pressure heavy oil pressurized in the plunger volume cavity sequentially passes through the oil inlet and outlet valve assembly, the second horizontal middle hole and the heavy oil outlet interface and flows out;
the lower spring seat is arranged in the guide piston assembly, and the plunger spring is arranged between the plunger matching part and the lower spring seat;
a camshaft mounted within a first horizontal central bore of the pump body; the bearing bush is used for radial positioning, and thrust bearings and end covers which are arranged at two ends of the pump body are used for axial positioning; the camshaft has a plurality of cams corresponding respectively to the guide piston assemblies provided in the respective first vertical central bores;
a cooling circulation oil way is arranged in the electric control proportional valve and is communicated with a second cooling oil way arranged in the pump cover; and a mixed oil way is arranged in the pump cover, the mixed oil way is communicated with a mixed oil outlet joint arranged on the pump cover, and the mixed oil way is arranged between the second cooling oil way and a plunger volume cavity in the plunger matching part.
Preferably, the plunger and barrel assembly comprises:
the plunger sleeve is provided with a first mounting hole at the upper part and a second mounting hole at the lower part; the oil inlet and outlet valve assembly is arranged in the first mounting hole;
a plunger slidably inserted into the second mounting hole;
the plunger volume cavity is formed between the first mounting hole and the second mounting hole;
a first mixed oil groove and a first cooling oil groove which are arranged around the plunger are formed in the inner wall of the plunger sleeve;
a second mixed oil groove and a second cooling oil groove are formed in the outer circumferential direction of the plunger sleeve;
the first mixed oil groove is communicated with the second mixed oil groove through an oil passage, and the second mixed oil groove is communicated with a mixed oil way on the pump cover;
the first cooling oil groove is communicated with the second cooling oil groove through an oil passage, and the second cooling oil groove is communicated with a second cooling oil way on the pump cover;
the plunger sleeve is further provided with an oil inlet duct, and the oil inlet duct is communicated with the outer surface of the plunger sleeve and the first mounting hole.
Preferably, a stress transition annular cavity is arranged on the hole wall of the first mounting hole in the plunger sleeve, the stress transition annular cavity is an annular cavity with a gradually reduced hole diameter from top to bottom, and the stress transition annular cavity is arranged at a position opposite to the front three-thread of the upper end of the plunger sleeve.
Preferably, the pilot piston assembly comprises:
the upper end surface of the guide piston is provided with a first mounting cavity for mounting a lower spring seat, and the lower side of the guide piston is provided with a second mounting cavity for mounting the roller assembly;
the roller assembly includes: the roller comprises a roller, a roller bushing, a roller pin and thrust bearings, wherein the roller bushing is assembled in the roller in an interference fit mode, the roller pin is assembled in the roller bushing in a clearance fit mode, and the thrust bearings are assembled at two axial ends of the roller in an interference fit mode;
a lubricating oil groove is formed in the outer circumference of the guide piston, a first lubricating oil channel which is obliquely arranged is formed in the roller pin, and a second lubricating oil channel which is circumferentially arranged is formed in the roller bushing; one end of the first lubricating oil channel is communicated with the second lubricating oil channel, and the other end of the first lubricating oil channel is arranged at a position opposite to the guide piston; the first lubricating oil channel is communicated with the lubricating oil groove;
and two ends of the roller pin are respectively sleeved with a check ring, and the check rings are attached to the guide piston.
Preferably, the first mounting cavity is convex in the middle and concave in the outer side, a collar mounting groove is formed in a convex part of the guide piston in the first mounting cavity, a collar is mounted in the collar mounting groove, and the lower spring seat and the guide piston are fixedly connected through the collar;
the lower cylindrical head of the plunger is limited between the lower spring seat and the guide piston, and the lower end face of the lower cylindrical head of the plunger is attached to the upper end face of the guide piston.
Preferably, the oil inlet and outlet valve assembly comprises:
an oil inlet valve component: the method comprises the following steps: an oil inlet valve seat; the oil inlet valve is arranged in an oil inlet valve cavity arranged in the oil inlet valve seat, and the oil inlet valve cavity is respectively communicated with the oil inlet oil duct and the plunger piston volume cavity; the oil inlet valve spring is used for pushing the oil inlet valve and the oil inlet valve cavity to form conical surface sealing;
an oil outlet valve assembly comprising: the oil outlet valve seat is arranged on the upper side of the oil inlet valve seat, and a high-pressure oil outlet cavity communicated with the plunger volume cavity is arranged in the oil outlet valve seat; the oil outlet valve is arranged in an oil outlet valve cavity arranged in the oil outlet valve seat and communicated with the high-pressure oil outlet cavity; the oil outlet valve spring is used for pushing the oil outlet valve and the oil outlet valve cavity to form conical surface sealing; and the oil outlet valve spring seat is arranged on the upper side of the oil outlet valve seat, the oil outlet valve spring is limited between the oil outlet valve spring seat and the cavity wall of the oil outlet valve cavity, and a through hole for communicating the oil outlet valve cavity with the second horizontal middle hole is formed in the oil outlet valve spring seat.
Preferably, the electrically controlled proportional valve comprises:
a valve body; a proportional valve coupling disposed within the valve body; the spring is arranged in the valve body and is arranged on one side of the proportional valve matching part; the isolation sleeve is sleeved on the push rod, and the push rod and the isolation sleeve are arranged on the other side of the proportional valve matching part; the electromagnet is arranged on the outer side of the valve body and is connected with the push rod;
the valve body is provided with a cooling oil inlet channel, a cooling cavity and a cooling oil return channel which are sequentially communicated; the cooling cavity is arranged around the part of the push rod and is attached to the electromagnet;
the valve body is also provided with a waste oil cavity and a waste oil channel which are communicated with each other, and the waste oil cavity is arranged around the part of the isolation sleeve;
the valve body is further provided with a heavy oil inlet channel, a heavy oil cavity and a heavy oil outlet channel which are sequentially communicated, the heavy oil cavity surrounds the push rod, and the oil inlet cross-sectional area of the heavy oil inlet channel is larger than the oil outlet cross-sectional area of the heavy oil outlet channel.
The invention has the beneficial effects that:
(1) the oil supply regulation sensitivity and the heavy oil reliability of the high-pressure oil pump are improved through electronic control, oil circuit layering and an optimized sealing structure, the application range of the low-speed engine heavy oil is expanded, and the 750Cst heavy oil use environment is met; particularly, the high-temperature heavy oil is prevented from being in direct contact with the electromagnet of the electric control proportional valve by additionally arranging the electric control proportional valve and arranging the isolating sleeve for isolating the heavy oil in the electric control proportional valve, so that the high-temperature damage and corrosion of the electromagnet are avoided; the electric control proportional valve is provided with a forced cooling structure, cooling oil comes from an oil inlet oil path of lubricating oil in the combined heavy oil pump, and cooling return oil also flows back to the lubricating oil tank through an oil return oil path of the lubricating oil in the combined heavy oil pump; the outside of the isolation sleeve is provided with a low-temperature lubricating oil and high-temperature low-pressure heavy oil leakage mixed oil passage to prevent cooling from being polluted, and the mixed waste oil also flows back to the waste oil tank through a mixed oil return oil passage in the combined heavy oil pump.
(2) The guide piston assembly is provided with a symmetrical multi-point lubricating structure, and lubricating oil is introduced to the roller pin, the sliding bush, the roller and the thrust bearing through oil ducts on two sides of the guide piston and the roller pin, so that the moving parts are fully lubricated;
(3) the oil inlet and outlet valve assembly is arranged in the plunger sleeve, and a spring seat is arranged on the oil inlet and outlet valve assembly; the plunger sleeve is connected with the pump cover through external large threads to tightly press and seal the oil inlet and outlet valve assembly; the oil inlet and outlet valve components are arranged up and down, and the sealing surfaces of the oil inlet and outlet valve components are symmetrical annular seals, so that the sealing reliability is improved; the oil inlet valve and the oil outlet valve are the same, and the oil inlet valve spring and the oil outlet valve spring are the same, so that the low-pressure circulation function of heavy oil is met while the cost is reduced;
(4) the oil way in the oil pump is divided into 4 layers, wherein the lower layer is a cooling and lubricating oil way, lubricating oil enters from the middle part of the pump body, flows to the two sides to lubricate and cool the guide piston assembly, flows downwards to lubricate and cool the bearing bush and the thrust bearing, flows upwards to lubricate and change the cooling plunger and barrel assembly, flows upwards to cool the electric control proportional valve and flows back to the cooling oil way of the pump body from the oil way in the pump cover, and finally flows back to the lubricating oil tank from the oil hole of the front end cover of the high-pressure oil; the middle layer is a mixed oil way with slightly higher temperature, and the mixed oil way is mainly formed by mixing lubricating and cooling oil leakage at the lower part of the plunger and high-temperature heavy oil leakage at the upper part of the plunger and then reflowing to a waste oil tank through a mixed oil outlet joint at the tail end of the pump cover; the upper layer is a high-temperature heavy oil low-pressure oil way, and high-temperature low-pressure heavy oil from the electric control proportional valve enters the plunger volume cavity through the pump cover, the plunger sleeve and the oil inlet valve; the top layer is a high-temperature heavy oil high-pressure oil way, and low-pressure high-temperature heavy oil is pressurized by the plunger and then enters the high-temperature heavy oil high-pressure oil way at the top of the pump cover through the oil outlet valve; through the layered design of the oil circuit, low-temperature cooling lubricating oil, mixed waste oil and high-temperature heavy oil are isolated, the cooling efficiency of the lubricating oil can be effectively improved, the working reliability of moving parts such as a plunger matching part and a guide piston assembly is improved, and the using condition of the high-temperature heavy oil is met.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic structural diagram of the plunger and barrel assembly of the present invention;
FIG. 3 is a schematic view of the pilot piston of the present invention;
FIG. 4 is a schematic view of the construction of the roll pin of the present invention;
FIG. 5 is a schematic structural view of the oil inlet and outlet valve assembly of the present invention;
FIG. 6 is a schematic view of the pump cover, the fuel inlet and outlet valve assembly, and the plunger and barrel assembly of the present invention;
FIG. 7 is a schematic structural diagram of a prior art plunger and barrel assembly;
FIG. 8 is a schematic diagram of the electrically controlled proportional valve of the present invention;
FIG. 9 is a schematic diagram of the oil circuit arrangement in the configuration of the present invention;
description of reference numerals: 1-a pump body assembly; 101-a pump body; 102-bearing shells; 103-first cooling oil path; 2-pump cover; 201-a second horizontal mesopore; 202-a high pressure oil passage; 203-second cooling oil path; 301-a valve body; 302-proportional valve coupling; 303-a spring; 304-a push rod; 305-a spacer sleeve; 306-an electromagnet; 307-cooling oil inlet channel; 308-a cooling chamber; 309-cooling oil return channel; 310-a waste oil gallery; 311-waste oil chamber; 312-heavy oil inlet line; 313-heavy oil chamber; 314-heavy oil outlet; 4-plunger and barrel assembly; 401-plunger volume chamber; 402-a plunger sleeve; 403-a first mounting hole; 404-a plunger; 405-a first mixing oil sump; 406 — a first cooling oil sump; 407-a second oil mixture tank; 408-a second cooling oil sump; 409-an oil inlet duct; 410-stress transition ring cavity; 5-heavy oil outlet interface; 6-plunger spring; 7-lower spring seat; 8-a pilot piston assembly; 801-pilot piston; 802-a first mounting cavity; 803-rollers; 804-roller bushing; 805-roll pins; 806-a thrust bearing; 807-lubricating oil grooves; 808-a first lubricating oil channel; 809-second lubricating oil channel; 810-a retainer ring; 811-collar mounting groove; 812-oblique ring grooves; 9-oil inlet and outlet valve components; 901-an oil inlet valve seat; 902-an oil inlet valve; 903-oil inlet valve spring; 904-outlet valve seat; 905-high pressure oil cavity; 906-the delivery valve; 907-outlet valve spring; 908-outlet valve spring seat; 10-a camshaft; 11-a thrust bearing; 12 end caps; 13-mixed oil outlet joint.
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 to 9, the present invention provides a marine low-speed engine multi-cylinder combined high-pressure oil pump, including: pump body subassembly 1, it includes: the pump body 101 is provided with a first horizontal middle hole and a plurality of first vertical middle holes, and the first horizontal middle holes are communicated with the first vertical middle holes; specifically, a horizontal center hole is provided in a lower portion of the pump body 101, and penetrates both left and right sides of the pump body 101, and a first vertical center hole is opened from an upper end surface of the pump body 101. Two ends of a horizontal middle hole of the pump body 101 are respectively provided with one bearing bush 102 in an interference manner; the bearing shell 102 is assembled at two ends of the horizontal middle hole in an interference fit mode. The bearing bush is soft low-carbon steel, and a multi-element alloy layer is coated on the working surface of the bearing bush.
The pump cover 2 is installed on the upper side of the pump body 101, the pump cover 2 is provided with a second horizontal middle hole 201 and a plurality of second vertical middle holes, each second vertical middle hole is communicated to the second horizontal middle hole 201, and one first vertical middle hole is correspondingly communicated with one second vertical middle hole; and an electric control proportional valve and a heavy oil outlet interface 5 are arranged on the pump cover 2. The pump cover 2 is composed of a small rectangular parallelepiped located above and a large rectangular parallelepiped located below, the small rectangular parallelepiped and the large rectangular parallelepiped are integrally formed, the second horizontal middle hole 201 is provided in the small rectangular parallelepiped above, it is provided along the length direction of the small rectangular parallelepiped, and the two vertical middle holes are provided in the large rectangular parallelepiped below. The second vertical center hole and the first vertical center hole are not determined in terms of the diameter, size, etc. thereof, and are arranged according to the shape, size, etc. of the component mounted therein; the second vertical center hole is communicated to the second horizontal center hole 201 through a high-pressure oil passage 202. Aiming at the pump cover 2, two threaded holes are uniformly distributed on the horizontal middle line of the upper end surface of the pump cover 2 and used for installing a lifting ring, and the hole bottom of each threaded hole and the corresponding second horizontal middle hole 201 are arranged to keep a certain distance so as to ensure the strength of the pump cover 2.
The groove is formed in the groove bottom of one side, connected with the high-pressure oil duct 202, of the second vertical middle hole, the bottom of the second vertical middle hole is provided with a sealing ring band which is in contact with the oil inlet and outlet valve assembly 9 to form a high-pressure sealing cavity, the contact surface of the sealing ring band and the contact surface of the oil inlet and outlet valve assembly 9 require high flatness and roughness, the groove is formed to reduce the width of the sealing ring band, the machining difficulty of the sealing ring band is reduced, the machining precision of the sealing ring band is improved, the sealing ring band can better meet the requirement of high-pressure sealing, and the impact resistance of the pump cover 2 is improved.
And the vertical middle hole formed by the first vertical middle hole and the second vertical middle hole is internally provided with the following components in sequence from top to bottom: the plunger matching part 4, the plunger spring 6, the lower spring seat 7 and the guide piston assembly 8;
the plunger and barrel assembly 4 is in threaded connection with the second vertical middle hole, and an oil inlet and outlet valve assembly 9 is installed in the plunger and barrel assembly 4; the low-pressure heavy oil output by the electronic control proportional valve is transferred by the oil inlet and outlet valve assembly 9 and then flows into the plunger volume cavity 401 of the plunger matching part 4, and the high-pressure heavy oil pressurized in the plunger volume cavity 401 sequentially passes through the oil inlet and outlet valve assembly 9, the second horizontal middle hole 201 and the heavy oil outlet port 5 and flows out;
the lower spring seat 7 is installed in the guide piston assembly 8, and the plunger spring 6 is installed between the plunger matching part 4 and the lower spring seat 7; specifically, a lower spring seat mounting groove is opened in the side of the guide piston assembly 8 facing the plunger and barrel assembly 4, and the lower spring seat 7 is mounted in the lower spring seat mounting groove.
A camshaft 10 mounted in a first horizontal center hole of the pump body 101; the bearing bush 102 is used for radial positioning, and the thrust bearings 11 and the end covers 12 which are arranged at two ends of the pump body 101 are used for axial positioning; the camshaft 10 has a plurality of cams corresponding respectively to the pilot piston assemblies 8 arranged in the respective first vertical central bores. Specifically, the cam on the camshaft 10 is a disk-shaped member with varying diameter that rotates about a fixed axis, and the camshaft 10 rotates to move the corresponding guide piston assembly 8 upward. As shown in fig. 1 and 6, the end cap 12 is fixed to the pump body 101 by screwing, and a seal ring for improving sealing performance is provided on an end surface of the end cap 12 contacting the pump body 101. The thrust bearing 11 is sleeved on the camshaft 10 and limited between the end cover 11 and the camshaft 10.
A cooling circulation oil way is arranged in the electric control proportional valve and is communicated with a second cooling oil way 203 arranged in the pump cover 2; and a mixed oil path is arranged in the pump cover 2, the mixed oil path is communicated with a mixed oil outlet joint 13 arranged on the pump cover 2, and the mixed oil path is arranged between the second cooling oil path 203 and a plunger volume cavity 401 in the plunger and barrel assembly 4. The electric control proportional valve is used as a hydraulic control device and has the effect of oil inlet throttling, and is mainly used for oil inlet regulation and control of light oil heavy oil outlet interfaces such as gasoline and diesel oil heavy oil outlet interfaces. 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 is used for carrying out oil inlet adjustment on heavy oil, and the temperature of the existing mechanical adjusting mode can be solved. Specifically, a cooling circulation oil path is arranged in the electric control proportional valve, so that cooling oil flowing in the pump cover 2 enters the electric control proportional valve to perform targeted cooling on an electric control element in the electric control proportional valve, and the electric control element of the electric control proportional valve is kept within a normal temperature range. The cooling circulation oil circuit designed in the electric control proportional valve should meet the following requirements: 1. the electric control element is close to a coil, an armature and the like of the electric control proportional valve as much as possible; the heavy oil outlet interface 2 is connected with the heavy oil outlet interface and the cooling oil flow introduced into the cooling circulation oil circuit, so that the temperature of electric control elements such as a coil, an armature and the like can be reduced to be within the 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 circulating oil way is arranged in the electric control proportional valve, so that the temperature of the armature and the coil of the electric control proportional valve is reduced, the electric control element works in a normal temperature range, and the electric control proportional valve is allowed to be used for oil inlet throttling of 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 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.
Referring to fig. 2, the plunger and barrel assembly 4 includes:
a plunger barrel 402 having a first mounting hole 403 formed in an upper portion thereof and a second mounting hole formed in a lower portion thereof; the oil inlet and outlet valve assembly 9 is installed in the first installation hole 403;
a plunger 404 slidably inserted in the second mounting hole;
the plunger volume 401 is formed between the first mounting hole 403 and the second mounting hole;
a first mixing oil groove 405 and a first cooling oil groove 406 which are arranged around the plunger 404 are arranged on the inner wall of the plunger sleeve 402;
a second mixing oil groove 407 and a second cooling oil groove 408 are formed in the outer circumferential direction of plunger sleeve 402;
the first mixed oil groove 405 is communicated with the second mixed oil groove 407 through an oil passage, and the second mixed oil groove 408 is communicated with a mixed oil passage on the pump cover 2;
the first cooling oil groove 406 is communicated with the second cooling oil groove 408 through an oil passage, and the second cooling oil groove 408 is communicated with the second cooling oil passage 203 on the pump cover 2;
the plunger sleeve 402 is further provided with an oil inlet passage 409, and the oil inlet passage 409 is communicated with the outer surface of the plunger sleeve 402 and the first mounting hole 403. First oil mixture groove 405 is provided above first cooling oil groove 406, and second oil mixture groove 407 is provided above second cooling oil groove 408. Cooling oil in the first cooling oil passage 103 in the pump body 101 flows into the second cooling oil passage 203 on the pump cover 2, supplies oil to the second cooling oil groove 408, and flows into a space between the plunger 404 and the plunger sleeve 402 through an oil passage to provide cooling lubrication; when the high-pressure heavy oil in the plunger volume chamber 401 flows out through the gap between the plunger 404 and the plunger sleeve 402, the high-pressure heavy oil flows out to the second mixed oil groove 408 through the oil passage at the first mixed oil groove 405, and then flows out to the mixed oil outlet joint 4 through the mixed oil passage on the pump cover 2. The oil inlet duct 409 is communicated with the oil outlet end of the electric control proportional valve, and the low-pressure heavy oil output by the electric control proportional valve flows into the oil inlet and outlet valve assembly 9 in the first mounting hole 403 through the oil inlet duct 409, and then the subsequent actions are performed. Meanwhile, a plurality of sealing ring grooves are further formed in the outer circumferential direction of the plunger sleeve 402, and sealing performance between the plunger sleeve 402 and the pump body 101 is improved by installing sealing rings in the plurality of sealing ring grooves.
In this embodiment, the lower cuboid of pump cover 2 and the surface of pump body 101 complex are the plane, and the degree of difficulty of processing the vertical mesopore of second as plunger trepanning on the cuboid down is lower, simultaneously, because plunger bushing 402 and pump cover 2's mounting means is through carrying out threaded connection in the vertical mesopore of second, need not handle the lower surface of cuboid down, and lower cuboid and the surface of pump body 101 complex still are the plane, can ensure sealed effect of face. Meanwhile, the internal thread is arranged in the vertical middle hole of the second to connect the plunger sleeve 402, so that the connection strength between the plunger sleeve 402 and the pump cover 2 is enhanced, the space is fully utilized, and the structure of the oil injection pump is more compact. As shown in fig. 1, in the oil pumping process, the three plungers 404 pump oil to the second horizontal middle hole 201 at different phases, the second horizontal middle hole 201 has a large aperture, a long hole and a large volume, and effectively buffers pressure fluctuation of high-pressure fuel oil entering from each high-pressure oil cavity, and finally flows out through the heavy oil outlet interface 5, so that the pressure of the high-pressure fuel oil output by the oil injection pump to the common rail pipe is more gentle, the consistency of the oil injection quantity of the oil injector is further improved, and the performance of the oil injection system of the diesel engine is optimized.
Referring to fig. 2, a stress transition annular cavity 410 is arranged on the wall of a first mounting hole 403 in the plunger sleeve 402, the stress transition annular cavity 410 is an annular cavity with a gradually reduced pore diameter from top to bottom, and the stress transition annular cavity 410 is arranged at a position opposite to the first three threads on the upper end of the plunger sleeve 402. according to the stress characteristics of thread matching, the first three threads are stressed most when the threads are stressed, and the stress of the first thread reaches 30% ~ 40% of the total load, so that the first thread corresponds to the thread position when the threads work, the stress is too large, and fatigue cracks are easily caused.
Specifically, internal threads of M50-54 are arranged on the inner wall of the first vertical middle hole, and external threads are arranged on the outer wall of the plunger sleeve 402, so that the connection reliability of the plunger sleeve 402 and the pump cover 2 is realized.
As shown in fig. 3, the pilot piston assembly 8 includes:
the spring seat comprises a guide piston 801 and a roller assembly, wherein a first mounting cavity 802 for mounting a lower spring seat 7 is formed in the upper end face of the guide piston 801, and a second mounting cavity for mounting the roller assembly is formed in the lower side of the guide piston 801;
the roller assembly includes: a roller 803, a roller bushing 804 interference-fitted in the roller 803, a roller pin 805 interference-clearance-fitted in the roller bushing 804, and thrust bearings 806 interference-fitted at both axial ends of the roller 803;
a lubricating oil groove 807 is formed in the outer circumference of the guide piston 801, a first lubricating oil channel 808 which is obliquely arranged is formed in the roller pin 805, and a second lubricating oil channel 809 which is circumferentially arranged is formed in the roller bushing 804; one end of the first lubricating oil channel 808 is communicated with the second lubricating oil channel 809, and the other end of the first lubricating oil channel is arranged at a position opposite to the guide piston 801; the first lubricating oil passage 808 is communicated with the lubricating oil groove 807;
two ends of the roller pin 805 are respectively sleeved with a retaining ring 810, and the retaining rings 810 are attached to the guide piston 801. Wherein, as shown in fig. 3, the first lubricating oil passage 808 and the second lubricating oil passage 809 are provided in plural numbers, the first lubricating oil passage 808 being arranged obliquely so that one end thereof can be connected to the second lubricating oil passage 809 and the other end thereof can be connected to the opposite end faces of the roller pin 805 and the guide piston 801; the second lubricating oil passage 809 communicates the inner and outer surfaces of the roller bushing 804; thus, the cooling lubricant flowing from the lubricant groove 807 can lubricate between the roller pin 805 and the roller bushing 804, between the roller bushing 804 and the roller 803, and between the roller pin 805 and the guide piston 801. The roller bushing 804 is installed in the central hole of the roller 803, and can be in interference fit or clearance fit, so that the bearing capacity of the guide piston 801 is improved through the roller bushing 804, and the abrasion is reduced. Thrust bearings 806 are mounted at both ends of the roller 803 to balance the lateral force of the roller 803 and reduce lateral wear. The roller pin 805 is positioned by the retaining rings 810 on the left side and the right side, so that the roller pin 805 is prevented from axially moving, and meanwhile, the roller pin 805 can freely rotate around the axis, the relative rotating speed is reduced, and the friction is reduced.
The guide piston assembly 8 adopts symmetrical lubrication, and lubricating oil from the pump body assembly 1 firstly enters the lubricating oil groove 807 of the guide piston 801 and then enters the clearance among the roller pin 805, the roller bush 804 and the roller 803 from the lubricating oil passages symmetrically arranged at the left side and the right side of the guide piston 801 to realize the overall lubrication of the roller pin 805, the roller bush 804 and the roller 803.
As shown in fig. 3 and 4, a plurality of inclined ring grooves 812 corresponding to the number of the first inclined oil channels 808 are formed on the outer surface of the roller pin 805, two ends of one first lubricating oil channel 808 are respectively located in one inclined ring groove 812, and the inclined ring groove 812 is communicated with the second lubricating oil channel 809.
As shown in fig. 3, the first installation cavity 802 is convex in the middle and concave in the outside, the raised part of the guide piston 801 in the first installation cavity 802 is provided with a collar installation groove 811, a collar is installed in the collar installation groove 811, and the lower spring seat 7 and the guide piston 801 are fixedly connected through the collar;
the lower cylindrical head of the plunger 404 is limited between the lower spring seat 7 and the guide piston 801, and the lower end surface of the lower cylindrical head of the plunger 404 is attached to the upper end surface of the guide piston 801. This first installation cavity 802 is for being the concave middle convex shape in both sides, is provided with this rand mounting groove 811 at the bellied part that direction piston 801 is located this first installation cavity 802, through installing the rand in rand mounting groove 811, can restrict the axial and radial displacement of restriction plunger 404, easy dismounting, and the processing cost is low. The lower end surface of the lower cylindrical head of the plunger 404 and the upper end surface of the convex portion of the guide piston 801 located in the first mounting chamber 802 are fitted together.
As shown in fig. 5, the oil inlet/outlet valve assembly 9 includes:
an oil inlet valve component: the method comprises the following steps: an oil inlet valve seat 901; the oil inlet valve 902 is installed in an oil inlet valve cavity arranged in the oil inlet valve seat 901, and the oil inlet valve cavity is respectively communicated with the oil inlet oil duct 409 and the plunger volume cavity 401; an oil inlet valve spring 903 for pushing the oil inlet valve 902 and the oil inlet valve cavity to form conical surface sealing;
an oil outlet valve assembly comprising: an oil outlet valve seat 904 arranged on the upper side of the oil inlet valve seat 901, wherein a high-pressure oil outlet cavity 905 communicated with the plunger volume cavity 401 is arranged in the oil outlet valve seat 904; the oil outlet valve 906 is arranged in an oil outlet valve cavity arranged in the oil outlet valve seat 904, and the oil outlet valve cavity is communicated with the high-pressure oil outlet cavity 905; an oil outlet valve spring 907 for pushing the oil outlet valve 906 and the oil outlet valve cavity to form conical surface sealing; and the oil outlet valve spring seat 908 is arranged on the upper side of the oil outlet valve seat 904, the oil outlet valve spring 907 is limited between the oil outlet valve spring seat 908 and the cavity wall of the oil outlet valve cavity, and a through hole for communicating the oil outlet valve cavity and the second horizontal middle hole 201 is formed in the oil outlet valve spring seat 908. As shown in the figure, in the oil filling stage, low-pressure high-temperature heavy oil is output from a fuel oil outlet of the electric control proportional valve, is transmitted to an oil inlet oil passage 409 on the plunger sleeve 402 through an oil passage on the pump cover 2 and enters an oil inlet valve cavity of the oil inlet valve seat 901, the oil inlet valve 902 opens a heavy oil outlet interface under the action of oil inlet pressure of the electric control proportional valve, namely, a conical surface sealing heavy oil outlet interface between the oil inlet valve 902 and the oil inlet valve seat 901 is removed, the oil outlet valve 906 forms conical surface sealing with the oil outlet valve seat 904 under the action of back pressure, oil is filled into the plunger volume cavity 401, and the ECU controls the amount of the oil inlet by adjusting the opening degree of the electric control; in the oil pumping stage: the guide piston assembly 8 moves upwards, the plunger 404 compresses heavy oil in the plunger volume cavity 401, the pressure of the heavy oil is gradually increased, when the pressure of fuel oil in the plunger volume cavity 401 is larger than the pressure of the fuel oil, the fuel inlet valve 902 is closed, when the pressure of the fuel oil in the plunger volume cavity 401, which is connected with the plunger volume cavity 401 through the high-pressure oil outlet cavity 905, exceeds the back pressure and the spring force of the fuel outlet valve, the fuel outlet valve 906 is opened, and the high-pressure fuel oil flows out to the second horizontal middle hole through the through hole of the fuel outlet valve spring seat 908 and is discharged through the heavy oil outlet port 5 communicated with the second horizontal middle. As shown in fig. 7, the previous high-pressure common rail 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 plunger volume cavity 401 in the plunger sleeve 402 is quickly closed when the plunger volume cavity is changed from oil absorption to compression by additionally arranging the oil inlet valve assembly, so that the pressure stability of relevant positions in an oil inlet channel of the oil inlet valve seat 901 is ensured, and cavitation corrosion is effectively prevented.
The sealing surface of the oil inlet and outlet valve assembly 9 is a symmetrical annular seal, so that the sealing reliability is improved; the oil inlet and outlet valve assembly 9 adopts a universal design, the oil inlet valve 902 is the same as the oil outlet valve 906, and the oil inlet valve spring 903 and the oil outlet valve spring 907 are the same, so that the cost is reduced, and the low-pressure circulation function of heavy oil is met.
As shown in fig. 8, the electrically controlled proportional valve includes:
a valve body 301; a proportional valve couple 302 disposed in the valve body 301; a spring 303 disposed in the valve body 301, the spring 303 being disposed on one side of the proportional valve coupling 302; a push rod 304 and an isolation sleeve 305 arranged in the valve body 301, wherein the isolation sleeve 305 is sleeved on the push rod 304, and the push rod 304 and the isolation sleeve 305 are arranged on the other side of the proportional valve matching part 302; the electromagnet 306 is arranged on the outer side of the valve body 301, and the electromagnet 306 is connected with the push rod 304;
the valve body 301 is provided with a cooling oil inlet channel 307, a cooling cavity 308 and a cooling oil return channel 309 which are sequentially communicated, and the three channels form the cooling circulation oil path together; the cooling cavity 308 is arranged around a part of the push rod 304, and the cooling cavity 308 is attached to the electromagnet 306;
the valve body 301 is further provided with a waste oil cavity 311 and a waste oil channel 310 which are communicated with each other, and the waste oil cavity 311 is arranged around part of the isolation sleeve 305;
the valve body 301 is further provided with a heavy oil inlet channel 312, a heavy oil cavity 313 and a heavy oil outlet channel 314 which are sequentially communicated, the heavy oil cavity 313 is arranged around the push rod 304, and the oil inlet cross-sectional area of the heavy oil inlet channel 312 is larger than the oil outlet cross-sectional area of the heavy oil outlet channel 314. Specifically, the heavy oil cavity 313 is formed by means of a special structure of the push rod 302, the electromagnet 306 drives the push rod 304 to push the proportional valve matching part 302 to compress the spring 303 according to the input signal after receiving the input signal, so that the oil inlet quantity in the heavy oil inlet channel 312 is controlled, and by means of the principle, the ECU can dynamically adjust the oil inlet flow quantity input into the pump by the electric control proportional valve according to the running condition of the low-speed engine. The isolation sleeve 305 can prevent the high-temperature heavy oil from directly contacting the electromagnet 306 of the electric control proportional valve, and avoid the electromagnet 306 from being damaged and corroded due to high temperature. The spacer 305 for isolating heavy oil in the electric control proportional valve and the oil passage for cooling and lubricating can effectively improve the adaptability of high-temperature heavy oil of the electric control proportional valve, have higher reliability and can meet the use requirement of 750Cst high-viscosity heavy oil. The heavy oil isolating sleeve 305 is externally provided with a heavy oil outlet interface formed by a heavy oil outlet interface waste oil cavity 311 and a waste oil channel 310 of a mixed oil channel when low-temperature lubricating oil and high-temperature low-pressure heavy oil leak, so that cooling is prevented from being polluted, and the mixed waste oil also flows back to a waste oil tank through a mixed oil return oil channel in the combined heavy oil pump.
As shown in fig. 9, in this embodiment, the oil path in the oil pump is divided into 4 layers, wherein the lower layer is a cooling and lubricating oil path, the lubricating oil enters from the middle of the pump body 101, and flows to the two sides to lubricate and cool the guide piston assembly 8, flows downward to lubricate and cool the bearing bush 102 and the thrust bearing 11, flows upward to lubricate and change the cooling plunger and barrel assembly 4, flows upward to cool the electric control proportional valve and flows back to the cooling oil path of the pump body 101 from the oil path inside the pump cover 2, and finally flows back to the lubricating oil tank from the oil hole of the front end cover; the middle layer is a mixed oil path with slightly higher temperature, and the mixed oil path is mainly formed by mixing lubricating and cooling oil leakage at the lower part of the plunger 404 and high-temperature heavy oil leakage at the upper part and then reflowing to a waste oil tank through a mixed oil outlet joint 14 at the tail end of the pump cover 2; the upper layer is a high-temperature heavy oil low-pressure oil way, and high-temperature low-pressure heavy oil from the electric control proportional valve enters the plunger volume cavity 401 through the pump cover 2, the plunger sleeve 402 and the oil inlet valve 902; the top layer is a high-temperature heavy oil high-pressure oil path, and the plunger 404 pressurizes low-pressure high-temperature heavy oil and then enters the high-temperature heavy oil high-pressure oil path at the top of the pump cover 2 through the oil outlet valve 906; through the layered design of the oil circuit, low-temperature cooling lubricating oil, mixed waste oil and high-temperature heavy oil are isolated, the cooling efficiency of the lubricating oil can be effectively improved, the working reliability of moving parts such as the plunger matching part 4 and the guide piston assembly 8 is improved, and the using condition of the high-temperature heavy oil is 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 (7)

1. The utility model provides a marine low-speed machine multi-cylinder combination formula high-pressure oil pump which characterized in that includes: pump body assembly (1), comprising: the pump comprises a pump body (101) and bearing bushes (102), wherein the pump body (101) is provided with a first horizontal middle hole and a plurality of first vertical middle holes, and the first horizontal middle holes are communicated with the first vertical middle holes;
the pump cover (2) is installed on the upper side of the pump body (101), the pump cover (2) is provided with a second horizontal middle hole (201) and a plurality of second vertical middle holes, each second vertical middle hole is communicated to the second horizontal middle hole (201), and one first vertical middle hole is correspondingly communicated with one second vertical middle hole; an electric control proportional valve and a heavy oil outlet interface (5) are arranged on the pump cover (2);
and the vertical middle hole formed by the first vertical middle hole and the second vertical middle hole is internally provided with the following components in sequence from top to bottom: the plunger and barrel assembly comprises a plunger and barrel assembly (4), a plunger spring (6), a lower spring seat (7) and a guide piston assembly (8);
the plunger and barrel assembly (4) is in threaded connection with the second vertical middle hole, and an oil inlet and outlet valve assembly (9) is installed in the plunger and barrel assembly (4); the low-pressure heavy oil output by the electric control proportional valve is transferred by the oil inlet and outlet valve assembly (9) and then flows into a plunger volume cavity (401) of the plunger matching part (4), and the high-pressure heavy oil pressurized in the plunger volume cavity (401) sequentially passes through the oil inlet and outlet valve assembly (9), the second horizontal middle hole (201) and the heavy oil outlet interface (5) and flows out;
the lower spring seat (7) is arranged in the guide piston assembly (8), and the plunger spring (6) is arranged between the plunger and barrel assembly (4) and the lower spring seat (7);
a camshaft (10) mounted within a first horizontal central bore of the pump body (101); the bearing bush (102) is used for radial positioning, and the thrust bearings (11) and the end covers (12) which are arranged at the two ends of the pump body (101) are used for axial positioning; the camshaft (10) has a plurality of cams corresponding respectively to the pilot piston assemblies (8) arranged in the respective first vertical central holes;
a cooling circulation oil way is arranged in the electric control proportional valve and is communicated with a second cooling oil way (203) arranged in the pump cover (2); and a mixed oil way is arranged in the pump cover (2), the mixed oil way is communicated with a mixed oil outlet joint (13) arranged on the pump cover (2), and the mixed oil way is arranged between the second cooling oil way (203) and a plunger volume cavity (401) in the plunger matching part (4).
2. The oil pump, as set forth in claim 1, characterized in that the plunger and barrel assembly (4) comprises:
a plunger sleeve (402) provided with a first mounting hole (403) at the upper part thereof and a second mounting hole at the lower part thereof; the oil inlet and outlet valve assembly (9) is installed in the first installation hole (403);
a plunger (404) slidably inserted in the second mounting hole;
the plunger volume (401) is formed between the first mounting hole (403) and the second mounting hole;
a first mixing oil groove (405) and a first cooling oil groove (406) which are arranged around the plunger (404) are formed in the inner wall of the plunger sleeve (402);
a second mixed oil groove (407) and a second cooling oil groove (408) are formed in the outer circumferential direction of the plunger sleeve (402);
the first mixed oil groove (405) is communicated with the second mixed oil groove (407) through an oil passage, and the second mixed oil groove (407) is communicated with a mixed oil passage on the pump cover (2);
the first cooling oil groove (406) is communicated with the second cooling oil groove (408) through an oil passage, and the second cooling oil groove (408) is communicated with a second cooling oil passage (203) on the pump cover (2);
the plunger sleeve (402) is further provided with an oil inlet oil duct (409), and the oil inlet oil duct (409) is communicated with the outer surface of the plunger sleeve (402) and the first mounting hole (403).
3. The oil pump according to claim 2, characterized in that a stress transition annular cavity (410) is arranged on the wall of the first mounting hole (403) in the plunger sleeve (402), the stress transition annular cavity (410) is an annular cavity with a gradually decreasing pore diameter from top to bottom, and the stress transition annular cavity (410) is arranged at a position opposite to the first three threads of the upper end part of the plunger sleeve (402).
4. The oil pump, as set forth in claim 2, characterized in that the pilot piston assembly (8) comprises:
the spring seat comprises a guide piston (801) and a roller assembly, wherein a first mounting cavity (802) for mounting a lower spring seat (7) is formed in the upper end face of the guide piston (801), and a second mounting cavity for mounting the roller assembly is formed in the lower side of the guide piston (801);
the roller assembly includes: a roller (803), a roller bushing (804) interference-fitted in the roller (803), a roller pin (805) clearance-fitted in the roller bushing (804), and thrust bearings (806) interference-fitted at both axial ends of the roller (803);
a lubricating oil groove (807) is formed in the outer circumference of the guide piston (801), a first lubricating oil channel (808) which is obliquely arranged is formed in the roller pin (805), and a second lubricating oil channel (809) which is circumferentially arranged is formed in the roller bushing (804); one end of the first lubricating oil channel (808) is communicated with the second lubricating oil channel (809), and the other end of the first lubricating oil channel is arranged at a position opposite to the guide piston (801); the first lubricating oil channel (808) is communicated with the lubricating oil groove (807);
two ends of the roller pin (805) are respectively sleeved with a check ring (810), and the check rings (810) are attached to the guide piston (801).
5. The oil pump according to claim 4, characterized in that the first mounting chamber (802) is of a shape convex in the middle and concave outside, the guide piston (801) is provided with a collar mounting groove (811) at a convex portion in the first mounting chamber (802), a collar is mounted in the collar mounting groove (811), and the lower spring seat (7) and the guide piston (801) are fixedly connected by the collar;
the lower cylindrical head of the plunger (404) is limited between the lower spring seat (7) and the guide piston (801), and the lower end face of the lower cylindrical head of the plunger (404) is attached to the upper end face of the guide piston (801).
6. The oil pump according to claim 2, characterized in that the oil inlet and outlet valve assembly (9) comprises:
an oil inlet valve component: the method comprises the following steps: an oil inlet valve seat (901); the oil inlet valve (902) is arranged in an oil inlet valve cavity arranged in the oil inlet valve seat (901), and the oil inlet valve cavity is respectively communicated with the oil inlet oil duct (409) and the plunger volume cavity (401); the oil inlet valve spring (903) is used for pushing a conical surface seal to be formed between the oil inlet valve (902) and the oil inlet valve cavity;
an oil outlet valve assembly comprising: an oil outlet valve seat (904) arranged on the upper side of the oil inlet valve seat (901), wherein a high-pressure oil outlet cavity (905) communicated with the plunger volume cavity (401) is arranged in the oil outlet valve seat (904); the oil outlet valve (906) is arranged in an oil outlet valve cavity arranged in the oil outlet valve seat (904), and the oil outlet valve cavity is communicated with the high-pressure oil outlet cavity (905); an oil outlet valve spring (907) for pushing a conical surface seal to be formed between the oil outlet valve (906) and the oil outlet valve cavity; and the oil outlet valve spring seat (908) is arranged on the upper side of the oil outlet valve seat (904), the oil outlet valve spring (907) is limited between the oil outlet valve spring seat (908) and the cavity wall of the oil outlet valve cavity, and a through hole for communicating the oil outlet valve cavity and the second horizontal middle hole (201) is formed in the oil outlet valve spring seat (908).
7. The oil pump of claim 1, wherein the electronically controlled proportional valve comprises:
a valve body (301); a proportional valve couple (302) disposed within the valve body (301); a spring (303) disposed within the valve body (301), the spring (303) disposed on one side of the proportional valve couple (302); the push rod (304) and the isolation sleeve (305) are arranged in the valve body (301), the isolation sleeve (305) is sleeved on the push rod (304), and the push rod (304) and the isolation sleeve (305) are arranged on the other side of the proportional valve matching part (302); the electromagnet (306) is arranged on the outer side of the valve body (301), and the electromagnet (306) is connected with the push rod (304);
the valve body (301) is provided with a cooling oil inlet channel (307), a cooling cavity (308) and a cooling oil return channel (309) which are communicated in sequence; the cooling cavity (308) is arranged around part of the push rod (304), and the cooling cavity (308) is attached to the electromagnet (306);
the valve body (301) is also provided with a waste oil cavity (311) and a waste oil channel (310) which are communicated with each other, and the waste oil cavity (311) is arranged around the part of the isolation sleeve (305);
the valve body (301) is further provided with a heavy oil inlet channel (312), a heavy oil cavity (313) and a heavy oil outlet channel (314) which are sequentially communicated, the heavy oil cavity (313) surrounds the push rod (304), and the oil inlet cross-sectional area of the heavy oil inlet channel (312) is larger than the oil outlet cross-sectional area of the heavy oil outlet channel (314).
CN201911088467.5A 2019-11-08 2019-11-08 Multi-cylinder combined high-pressure oil pump of marine low-speed engine Pending CN110685841A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201911088467.5A CN110685841A (en) 2019-11-08 2019-11-08 Multi-cylinder combined high-pressure oil pump of marine low-speed engine
PCT/CN2020/086386 WO2021088324A1 (en) 2019-11-08 2020-04-23 Multi-cylinder combined high-pressure oil pump of marine low-speed machine
FI20215003A FI129983B (en) 2019-11-08 2020-04-23 Multi-cylinder combined high pressure oil pump for marine low speed engine
DE112020000519.4T DE112020000519T5 (en) 2019-11-08 2020-04-23 COMBINED MULTI-CYLINDER HIGH PRESSURE OIL PUMP FOR A SLOW RUNNING MARINE ENGINE
GB2019140.9A GB2594544B (en) 2019-11-08 2020-04-23 Multi-cylinder combined high-pressure oil pump for marine low-speed engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201911088467.5A CN110685841A (en) 2019-11-08 2019-11-08 Multi-cylinder combined high-pressure oil pump of marine low-speed engine

Publications (1)

Publication Number Publication Date
CN110685841A true CN110685841A (en) 2020-01-14

Family

ID=69115938

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201911088467.5A Pending CN110685841A (en) 2019-11-08 2019-11-08 Multi-cylinder combined high-pressure oil pump of marine low-speed engine

Country Status (4)

Country Link
CN (1) CN110685841A (en)
DE (1) DE112020000519T5 (en)
FI (1) FI129983B (en)
WO (1) WO2021088324A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022223742A1 (en) * 2021-04-23 2022-10-27 Delphi Technologies Ip Limited Fuel pump roller tappet assembly

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114735408B (en) * 2022-03-21 2024-02-02 华能武汉发电有限责任公司 Novel safety barrier for belt conveyor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101131140A (en) * 2007-09-13 2008-02-27 成都市易控高科电喷有限责任公司 Electric-controlled direct combination type multi-cylinder fuel injection pump assembly
DE102014220670A1 (en) * 2014-10-13 2016-04-14 Robert Bosch Gmbh Electromagnetically actuated proportional valve and high-pressure fuel pump with such a proportional valve
CN107120219B (en) * 2017-07-07 2024-02-23 辽阳新风科技有限公司 High-pressure oil pump and engine
CN207004702U (en) * 2017-08-09 2018-02-13 重庆红江机械有限责任公司 Combined type electric-controlled co-rail high-pressure oil pump
CN109026479A (en) * 2018-10-25 2018-12-18 龙口龙泵柴油喷射高科有限公司 High-pressure oil feed pump assembly for common rail for diesel engine system
CN209179918U (en) * 2018-10-29 2019-07-30 中船动力研究院有限公司 New Marine low speed machine high pressure co-rail system
CN210919306U (en) * 2019-11-08 2020-07-03 重庆红江机械有限责任公司 Multi-cylinder combined high-pressure oil pump of marine low-speed engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022223742A1 (en) * 2021-04-23 2022-10-27 Delphi Technologies Ip Limited Fuel pump roller tappet assembly

Also Published As

Publication number Publication date
FI129983B (en) 2022-12-15
FI20215003A1 (en) 2021-05-09
WO2021088324A1 (en) 2021-05-14
DE112020000519T5 (en) 2021-10-07

Similar Documents

Publication Publication Date Title
EP3819493B1 (en) High-pressure common rail system for low-speed engine with multiple safety protection functions
US6694931B2 (en) Internal combustion engine
EP2959194B1 (en) Rocking journal bearings for two-stroke cycle engines
CN210919306U (en) Multi-cylinder combined high-pressure oil pump of marine low-speed engine
KR20030041822A (en) Fuel supply installation in the form of a common-rail system of an internal combustion engine having a plurality of cylinders
CN110685841A (en) Multi-cylinder combined high-pressure oil pump of marine low-speed engine
US6210127B1 (en) Fuel pump
EP3090151B1 (en) Lubricating configuration for maintaining wristpin oil pressure in a two-stroke cycle, opposed-piston engine
CN112780470A (en) Common rail type high-pressure fuel injection pump for marine high-speed diesel engine
JP2020159357A (en) High-pressure pump
CN105221208B (en) Engine lubrication system
CN113006993A (en) High pressure fuel pump driving structure
KR20170044754A (en) High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine
US6368071B1 (en) High pressure fuel pump
EP3819492B1 (en) Electrically-controlled monolithic high-pressure oil pump for marine low-speed engine
CN108915919B (en) Common rail pump driving device of high-pressure common rail diesel engine
JP2001003839A (en) High pressure fuel pump
US6622706B2 (en) Pump, pump components and method
US20180202346A1 (en) Piston bearing assembly for an opposed-piston engine
CN210919305U (en) Marine low-speed machine electric control single high-pressure oil pump
GB2594544A (en) Multi-cylinder combined high-pressure oil pump of marine low-speed machine
CN107850010B (en) Multi-plunger cryopump with intake manifold
CN210531033U (en) High-heat-dissipation diesel engine plunger
CN210919253U (en) Low-speed machine high pressure common rail system with multiple security functions
CN112081696A (en) Combined common rail fuel injection pump of high-speed diesel engine

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination