EP4103831A1 - Diesel injector with an optimized valve assembly - Google Patents

Diesel injector with an optimized valve assembly

Info

Publication number
EP4103831A1
EP4103831A1 EP21705475.8A EP21705475A EP4103831A1 EP 4103831 A1 EP4103831 A1 EP 4103831A1 EP 21705475 A EP21705475 A EP 21705475A EP 4103831 A1 EP4103831 A1 EP 4103831A1
Authority
EP
European Patent Office
Prior art keywords
groove
valve assembly
bore
sleeve
diesel
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
EP21705475.8A
Other languages
German (de)
French (fr)
Inventor
Laurent M. VINCENT
David Bonneau
Laurent QUERON
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.)
Phinia Delphi Luxembourg SARL
Original Assignee
Delphi Technologies IP 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 Delphi Technologies IP Ltd filed Critical Delphi Technologies IP Ltd
Publication of EP4103831A1 publication Critical patent/EP4103831A1/en
Pending legal-status Critical Current

Links

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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/05—Fuel-injection apparatus having means for preventing corrosion
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit

Definitions

  • the present invention relates to a diesel injector for an internal combustion engine of an automotive vehicle that drastically reduces the risks of corrosion of a valve assembly.
  • a diesel injector comprises a body provided with a bore, in which a needle is configured to reciprocate from a closed position of the injector to an open position of the injector.
  • An electromagnetic coil is arranged to urge the reciprocating of the needle in the bore of the body by varying diesel pressure in a control chamber via a valve actuator.
  • the valve comprises a body provided with a bore, in which a rod is configured to reciprocate depending on whether the coil is supplied with electrical current or not.
  • a sleeve is disposed in the valve bore to reduce the diesel leaks when the diesel pressure level is high.
  • the quantity of water in diesel is not higher than 200 ppm. But, when the quantity of water in diesel accidentally increases, for instance, because of peculiar meteorological conditions, water can stagnate between the sleeve and the valve body and can provoke oxidation of the valve that can generate cracks of the valve in the oxidized areas.
  • control valve assembly for a diesel fuel injector
  • the control valve assembly comprising a valve body, a tubular sleeve and a valve spool
  • the valve body being provided with a channel opening into a bore, said bore extending along a longitudinal axis, the tubular sleeve being press-fitted in the bore, the sleeve having a wall defining an inner bore, said wall being provided with a radial hole to enable fuel to flow from the channel to said sleeve inner bore
  • the spool comprising a rod configured to reciprocate into said sleeve inner bore between a closed position of a valve seat preventing fuel to flow and an open position of the valve seat enabling fuel to flow from the channel toward an outlet fuel
  • the valve body being further provided with a first annular groove surrounding the body bore and wherein the channel opens and, wherein an interface between the sleeve and the valve body comprises a second annular groove con
  • Said acute angle may be comprised between 40° and 75°.
  • Said angle may be of 50°.
  • Said second groove may be machined in the valve body.
  • Said second groove may be machined in the sleeve.
  • Said second groove may be machined in the valve body and in the sleeve.
  • the valve assembly may comprise a third groove under the first groove, said third groove having a substantially triangular section comprising a chamfer with an acute angle.
  • Said acute angle of the third groove chamfer may be comprised between 20° and 40°.
  • the angle of the sleeve groove chamfer may be of 30°.
  • Figure 1 is a longitudinal view of an injector with a valve assembly according to the prior art.
  • Figure 2 is a perspective view of a valve assembly as per the invention configured to equip the injector of figure 1.
  • Figure 3 is a perspective view of a valve body of the valve assembly of figure 2.
  • Figure 4 is a longitudinal view of a detail of the valve body of figure 3.
  • Figure 5 is a perspective view of a sleeve of the valve assembly of figure
  • Figure 6 is a longitudinal view of a detail of the sleeve of figure 5.
  • a diesel injector 10 for an internal combustion engine comprises a body 12 and a needle 14.
  • the body 12 comprises an elongated bore 16 extending longitudinally along a longitudinal axis, the bore 16 being provided with a diesel inlet 18 and a diesel outlet 20.
  • the needle extends from a head 22 to a tip 24 and is arranged to reciprocate in the bore 16 along the longitudinal axis X from a closed position to an open position.
  • the tip 24 of the needle 14 closes the diesel outlet 20, and, in the open position, the tip 24 of the needle 14 is spaced apart from the diesel outlet 20.
  • the injector 10 also comprises a control chamber 26 arranged to control the reciprocating of the needle 14 in the bore 16 via a valve assembly 28 that controls the pressure of the diesel in the control chamber 26.
  • valve assembly 28 comprises a valve body 30 and a rod 32.
  • the valve body 30 is provided with an elongated bore 34 extending along a longitudinal axis L preferably parallel to the longitudinal axis X of the injector bore 16.
  • the valve body 30 also comprises a diesel entrance channel 36 and a diesel seat 38.
  • the channel 36 is arranged to lead diesel from the control chamber 26 to the valve assembly 34.
  • the channel 26 ends in the valve assembly 28 in a first annular groove 39 protruding from the valve body 30.
  • the rod 32 extends along the longitudinal axis L in the bore 34 to reciprocate between a closed position and an open position, such that the reciprocating of the rod 32 controls the diesel charge and discharge in the control chamber 26.
  • the valve assembly 28 also comprises a magnetic frame 40 fixed to the rod 32 and arranged to cooperate with a magnetic coil (not illustrated).
  • a magnetic coil (not illustrated)
  • the frame 40 lifts in the bore 34 and diesel flows from the diesel exit 38 to the diesel tank.
  • the diesel pressure in the control chamber quickly reduces and this discharge leads to the lifting of the needle 14 in the bore 16, opening the diesel outlet 20.
  • a spring (not illustrated) reinstate the sealing in the actuator, which closes the diesel outlet 20.
  • valve actuator 28 comprises a tubular sleeve 42 disposed in the bore 34 around the rod 32 to limit leaks that could happen when the pressure in the injector is high (2000 bars for instance).
  • the sleeve 42 is press-fitted in the valve body 30.
  • the sleeve 42 comprises a wall 440 defining an inner bore 460, the wall 440 being provided with a radial hole 480 to enable fuel to flow from the channel 36 to said sleeve inner bore 460.
  • valve assembly 28 of the prior art can be damaged because of oxidation of the valve.
  • valve assembly 44 as per the present invention is now detailed in reference to figures 2 to 6. Indeed, the actuator 44 can be installed in the injector 10 of figure 1 instead of the known valve assembly 28, the functioning of the injector, and, in particular, the charge and discharge if the diesel in the injector 10 being left unchanged.
  • the valve body 30 of the valve assembly 44 is configured to reduce any risk of corrosion of the valve, as is now described.
  • valve body 30 presents a general cylindrical shape extending along the longitudinal axis L.
  • the interface between the valve body 30 and the sleeve 42 comprises an annular grove 46.
  • the annular groove 46 is made in the valve body 30.
  • the groove 46 of the valve body 30 is disposed in a first contact zone Z between the sleeve 42 and the valve body 30, also called top ring.
  • the annular groove 46 is disposed just below a plain bearing P between the sleeve 42 and the valve body 30.
  • the annular groove 46 is contiguous to the first annular groove 39.
  • the annular grooves 39 and 46 are disposed in contact, next to each other such that the annular groove 46 opens in the first annular groove 39.
  • the groove 46 is provided with a chamfer 48 forming an angle A with the longitudinal axis L in the direction of the needle 14 of the injector 10, as best seen in figure 4.
  • the angle A is formed by the initiation between the plain bearing P and the beginning of the groove 46.
  • the angle A is preferably comprised between 40° and 75°.
  • the angle A ensures a reduction of the tensile stresses between the sleeve and the valve body 30 and a decrease of uncertain contact length that can generate fretting corrosion. Also, the angle A improves the circulation of the water in the valve since it prevents dead area from existing in the valve, said dead area implying stagnant water in the valve, and hence risk of oxidation of the valve.
  • the angle A further guarantees a gradual reduction of pressure of the diesel in the first contact zone Z.
  • the angle A is comprised between 42° and 65°, specifically of 50°, which value particularly reducing risk of corrosion and damage, as tests led by the Proprietor have shown.
  • a depth D of the annular groove 46 is preferably chosen between 0.1 mm and 0.2 mm, advantageously 0.15 mm.
  • An associated angle B between a down end 49 of the annular groove 46 and the longitudinal axis L in a direction opposed to the needle is consequently between 10° to 20°, preferably 15°.
  • the angle B and the depth D allow the control the volume of the annular groove 46.
  • the sleeve 42 of the valve assembly 46 is configured to reduce any risk of corrosion of the valve, as is now described.
  • the sleeve 42 is of a general cylindrical shape longitudinally extending along the longitudinal axis L.
  • the sleeve 42 comprises an annular groove 50.
  • the groove 50 of the sleeve 42 is disposed in a second contact zone ZZ between the sleeve 42 and the valve body 30, also called bottom ring.
  • the annular groove 50 is disposed just above a plain bearing PP between the sleeve 42 and the valve body 30.
  • the groove 50 is provided with a chamfer 52 forming an angle AA with the longitudinal axis L in the direction opposite to that of the needle 14 of the injector 10, as best seen in figure 6.
  • the angle A is formed by the initiation between the plain bearing PP and the beginning of the groove 50.
  • the angle AA is comprised between 20° and 40°, preferably 30°.
  • the angle AA ensures an increase circulation of backwater by reducing dead area without modifying stresses.
  • annular grooves 46 and 50 present each a substantially triangular cross-section.
  • the present invention in particular the chamfered grooves 46 and 50, two criteria are optimized: the stagnant water and the uncertain contact length are reduced.
  • the injector 10 can be used in countries and conditions where gas oil contains more than 0.15% of water (1500 ppm to 5000 ppm), as tests led by the Proprietor have shown.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

A control valve assembly for a diesel fuel injector (10), the control valve assembly comprising an interface between a sleeve (42) and a valve body (30) of the valve assembly provided with an annular groove having a substantially triangular cross-section comprising a chamfer forming an acute angle with a longitudinal axis of the valve (L) within said first annular groove.

Description

DIESEL INJECTOR WITH AN OPTIMIZED VALVE ASSEMBLY
TECHNICAL FIELD
The present invention relates to a diesel injector for an internal combustion engine of an automotive vehicle that drastically reduces the risks of corrosion of a valve assembly.
BACKGROUND OF THE INVENTION
Usually, a diesel injector comprises a body provided with a bore, in which a needle is configured to reciprocate from a closed position of the injector to an open position of the injector. An electromagnetic coil is arranged to urge the reciprocating of the needle in the bore of the body by varying diesel pressure in a control chamber via a valve actuator. As is known, the valve comprises a body provided with a bore, in which a rod is configured to reciprocate depending on whether the coil is supplied with electrical current or not. Preferably, a sleeve is disposed in the valve bore to reduce the diesel leaks when the diesel pressure level is high.
In normal use, the quantity of water in diesel is not higher than 200 ppm. But, when the quantity of water in diesel accidentally increases, for instance, because of peculiar meteorological conditions, water can stagnate between the sleeve and the valve body and can provoke oxidation of the valve that can generate cracks of the valve in the oxidized areas.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the present invention to resolve the above mentioned problems in providing a control valve assembly for a diesel fuel injector, the control valve assembly comprising a valve body, a tubular sleeve and a valve spool, the valve body being provided with a channel opening into a bore, said bore extending along a longitudinal axis, the tubular sleeve being press-fitted in the bore, the sleeve having a wall defining an inner bore, said wall being provided with a radial hole to enable fuel to flow from the channel to said sleeve inner bore, the spool comprising a rod configured to reciprocate into said sleeve inner bore between a closed position of a valve seat preventing fuel to flow and an open position of the valve seat enabling fuel to flow from the channel toward an outlet fuel, the valve body being further provided with a first annular groove surrounding the body bore and wherein the channel opens and, wherein an interface between the sleeve and the valve body comprises a second annular groove contiguous to said first groove, the second groove having a substantially triangular cross-section comprising a chamfer forming an acute angle with said longitudinal axis within said first annular groove.
Thanks to the claimed arrangement, tensile stresses on the sleeve valve actuator decrease as well as uncertain contact lengths between the sleeve and the valve body. The circulation of water is improved, so that water does not stagnate between the sleeve and the valve body.
Said acute angle may be comprised between 40° and 75°.
Said angle may be of 50°.
Said second groove may be machined in the valve body.
Said second groove may be machined in the sleeve.
Said second groove may be machined in the valve body and in the sleeve.
The valve assembly may comprise a third groove under the first groove, said third groove having a substantially triangular section comprising a chamfer with an acute angle.
Said acute angle of the third groove chamfer may be comprised between 20° and 40°.
The angle of the sleeve groove chamfer may be of 30°.
It is another object of the invention to provide a diesel fuel injector for an internal combustion engine, said injector comprising: a body and a needle, the body being provided with a bore extending along a longitudinal axis, and comprising a diesel inlet and a diesel outlet, the needle extending from a head to a tip, and being configured to reciprocate in the bore along said longitudinal axis from a closed position to an open position, such that, in the closed position, the tip of the needle closes the diesel outlet, and, in the open position, the tip of the needle is spaced apart from the diesel outlet, a control chamber arranged to control said reciprocating of the needle in the bore, and control valve assembly as already described, the control valve assembly being arranged to control the pressure of the diesel in a control chamber. BRIEF DESCRIPTION OF THE DRAWINGS
The present invention is now described by way of example with reference to the accompanying drawings in which:
Figure 1 is a longitudinal view of an injector with a valve assembly according to the prior art.
Figure 2 is a perspective view of a valve assembly as per the invention configured to equip the injector of figure 1.
Figure 3 is a perspective view of a valve body of the valve assembly of figure 2.
Figure 4 is a longitudinal view of a detail of the valve body of figure 3. Figure 5 is a perspective view of a sleeve of the valve assembly of figure
2
Figure 6 is a longitudinal view of a detail of the sleeve of figure 5.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
As can be seen from figure 1, a diesel injector 10 for an internal combustion engine comprises a body 12 and a needle 14. The body 12 comprises an elongated bore 16 extending longitudinally along a longitudinal axis, the bore 16 being provided with a diesel inlet 18 and a diesel outlet 20.
As also shown in figure 1, the needle extends from a head 22 to a tip 24 and is arranged to reciprocate in the bore 16 along the longitudinal axis X from a closed position to an open position.
In the closed position, the tip 24 of the needle 14 closes the diesel outlet 20, and, in the open position, the tip 24 of the needle 14 is spaced apart from the diesel outlet 20.
The injector 10 also comprises a control chamber 26 arranged to control the reciprocating of the needle 14 in the bore 16 via a valve assembly 28 that controls the pressure of the diesel in the control chamber 26.
As illustrated in figure 1, the valve assembly 28 comprises a valve body 30 and a rod 32.
The valve body 30 is provided with an elongated bore 34 extending along a longitudinal axis L preferably parallel to the longitudinal axis X of the injector bore 16. The valve body 30 also comprises a diesel entrance channel 36 and a diesel seat 38.
As can be seen from figure 1, the channel 36 is arranged to lead diesel from the control chamber 26 to the valve assembly 34. As particularly seen from figures 1 and 3, the channel 26 ends in the valve assembly 28 in a first annular groove 39 protruding from the valve body 30.
The rod 32 extends along the longitudinal axis L in the bore 34 to reciprocate between a closed position and an open position, such that the reciprocating of the rod 32 controls the diesel charge and discharge in the control chamber 26.
The valve assembly 28 also comprises a magnetic frame 40 fixed to the rod 32 and arranged to cooperate with a magnetic coil (not illustrated). When the coil is supplied with electrical current, the frame 40 lifts in the bore 34 and diesel flows from the diesel exit 38 to the diesel tank. The diesel pressure in the control chamber quickly reduces and this discharge leads to the lifting of the needle 14 in the bore 16, opening the diesel outlet 20. When is the coil is not supplied with electrical current, a spring (not illustrated) reinstate the sealing in the actuator, which closes the diesel outlet 20.
As can be seen from figures 1, 2 and 5-6, the valve actuator 28 comprises a tubular sleeve 42 disposed in the bore 34 around the rod 32 to limit leaks that could happen when the pressure in the injector is high (2000 bars for instance).
The sleeve 42 is press-fitted in the valve body 30.
The sleeve 42 comprises a wall 440 defining an inner bore 460, the wall 440 being provided with a radial hole 480 to enable fuel to flow from the channel 36 to said sleeve inner bore 460.
As already explained, the valve assembly 28 of the prior art can be damaged because of oxidation of the valve.
The valve assembly 44 as per the present invention is now detailed in reference to figures 2 to 6. Indeed, the actuator 44 can be installed in the injector 10 of figure 1 instead of the known valve assembly 28, the functioning of the injector, and, in particular, the charge and discharge if the diesel in the injector 10 being left unchanged. The valve body 30 of the valve assembly 44 is configured to reduce any risk of corrosion of the valve, as is now described.
As particularly seen in figures 3 and 4, the valve body 30 presents a general cylindrical shape extending along the longitudinal axis L. The interface between the valve body 30 and the sleeve 42 comprises an annular grove 46. On the illustrated embodiment, the annular groove 46 is made in the valve body 30.
As can be seen from figure 3, the groove 46 of the valve body 30 is disposed in a first contact zone Z between the sleeve 42 and the valve body 30, also called top ring. In the contact zone Z, the annular groove 46 is disposed just below a plain bearing P between the sleeve 42 and the valve body 30.
As can also be seen from figure 3, the annular groove 46 is contiguous to the first annular groove 39. In other words, the annular grooves 39 and 46 are disposed in contact, next to each other such that the annular groove 46 opens in the first annular groove 39.
The groove 46 is provided with a chamfer 48 forming an angle A with the longitudinal axis L in the direction of the needle 14 of the injector 10, as best seen in figure 4.
Differently said, the angle A is formed by the initiation between the plain bearing P and the beginning of the groove 46.
The angle A is preferably comprised between 40° and 75°. The angle A ensures a reduction of the tensile stresses between the sleeve and the valve body 30 and a decrease of uncertain contact length that can generate fretting corrosion. Also, the angle A improves the circulation of the water in the valve since it prevents dead area from existing in the valve, said dead area implying stagnant water in the valve, and hence risk of oxidation of the valve.
The angle A further guarantees a gradual reduction of pressure of the diesel in the first contact zone Z.
Advantageously, the angle A is comprised between 42° and 65°, specifically of 50°, which value particularly reducing risk of corrosion and damage, as tests led by the Proprietor have shown.
A depth D of the annular groove 46 is preferably chosen between 0.1 mm and 0.2 mm, advantageously 0.15 mm. An associated angle B between a down end 49 of the annular groove 46 and the longitudinal axis L in a direction opposed to the needle is consequently between 10° to 20°, preferably 15°. The angle B and the depth D allow the control the volume of the annular groove 46.
The sleeve 42 of the valve assembly 46 is configured to reduce any risk of corrosion of the valve, as is now described.
As can be seen from figures 5 and 6, the sleeve 42 is of a general cylindrical shape longitudinally extending along the longitudinal axis L. The sleeve 42 comprises an annular groove 50.
As can be seen from figure 3, the groove 50 of the sleeve 42 is disposed in a second contact zone ZZ between the sleeve 42 and the valve body 30, also called bottom ring. In the contact zone ZZ, the annular groove 50 is disposed just above a plain bearing PP between the sleeve 42 and the valve body 30.
The groove 50 is provided with a chamfer 52 forming an angle AA with the longitudinal axis L in the direction opposite to that of the needle 14 of the injector 10, as best seen in figure 6.
Differently said, the angle A is formed by the initiation between the plain bearing PP and the beginning of the groove 50.
The angle AA is comprised between 20° and 40°, preferably 30°.
The angle AA ensures an increase circulation of backwater by reducing dead area without modifying stresses.
As can be seen from the figures, the annular grooves 46 and 50 present each a substantially triangular cross-section.
Thanks to the present invention, in particular the chamfered grooves 46 and 50, two criteria are optimized: the stagnant water and the uncertain contact length are reduced.
Thanks to the present invention, the injector 10 can be used in countries and conditions where gas oil contains more than 0.15% of water (1500 ppm to 5000 ppm), as tests led by the Proprietor have shown.
LIST OF REFERENCES
X longitudinal axis of the bore of the injector
L longitudinal axis of the bore of the valve
Z first contact zone
P first plain bearing D depth of the annular groove 46
ZZ second contact zone
PP second plain bearing
10 diesel injector
12 body
14 needle
16 bore of the body
18 diesel inlet
20 diesel outlet
22 needle head
24 needle tip
26 control chamber
28 valve assembly (prior art)
30 valve body
32 valve rod
34 valve bore
36 fuel channel
38 seat
39 first annular groove
40 magnetic armature
42 sleeve
440 sleeve wall
460 inner bore
480 radial hole
44 valve assembly (invention)
46 valve body groove
48 chamfer of valve body groove
49 end of groove
50 sleeve groove
52 chamfer of sleeve groove

Claims

CLAIMS:
1. A control valve assembly for a diesel fuel injector (10), the control valve assembly comprising
- a valve body (30), a tubular sleeve (42) and a valve spool ,
- the valve body (30) being provided with a channel (36) opening into a bore (34), said bore (34) extending along a longitudinal axis (L),
- the tubular sleeve (42) being press-fitted in the bore (34), the sleeve having a wall (440) defining an inner bore (460), said wall (440) being provided with a radial hole (480) to enable fuel to flow from the channel (36) to said sleeve inner bore (460),
- the spool comprising a rod (32) configured to reciprocate into said sleeve inner bore (460) between a closed position of a valve seat preventing fuel to flow and an open position of the valve seat enabling fuel to flow from the channel (36) toward an outlet fuel; the valve body (30) being further provided with a first annular groove (39) surrounding the body bore (34) and wherein the channel opens (36) and, wherein an interface between the sleeve (42) and the valve body (30) comprises a second annular groove contiguous to said first groove, the second groove having a substantially triangular cross-section comprising a chamfer forming an acute angle with said longitudinal axis (L) within said first annular groove.
2. A control valve assembly as per claim 1, wherein said acute angle is comprised between 40° and 75°.
3. A control valve assembly as per anyone of the preceding claims, wherein said second groove is machined in the valve body (30).
4. A control valve assembly as per claim 1 or 2, wherein said second groove is machined in the sleeve (42).
5. A control valve assembly as per claim 1 or not, wherein said second groove is machined in the valve body (30) and in the sleeve (42).
6. A control valve assembly as per anyone of the preceding claims, comprising a third groove under the first groove, said third groove having a substantially triangular section comprising a chamfer with an acute angle.
7. A control valve assembly as per claim 6, wherein said acute angle of the third groove chamfer being comprised between 20° and 40°.
8. A diesel fuel injector for an internal combustion engine, said injector (10) comprising: a body (12) and a needle (14), the body (12) being provided with a bore (16) extending along a longitudinal axis (X), and comprising a diesel inlet (18) and a diesel outlet (20), the needle (14) extending from a head (22) to a tip (24), and being configured to reciprocate in the bore (16) along said longitudinal axis (X) from a closed position to an open position, such that, in the closed position, the tip (24) of the needle (14) closes the diesel outlet (20), and, in the open position, the tip (24) of the needle (14) is spaced apart from the diesel outlet (20), a control chamber (26) arranged to control said reciprocating of the needle (14) in the bore (16), and control valve assembly (44) as per anyone of the preceding claims, the control valve assembly (44) being arranged to control the pressure of the diesel in a control chamber (26).
EP21705475.8A 2020-02-12 2021-02-11 Diesel injector with an optimized valve assembly Pending EP4103831A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB2001883.4A GB2592019B (en) 2020-02-12 2020-02-12 Diesel injector with an optimized valve assembly
PCT/EP2021/053386 WO2021160765A1 (en) 2020-02-12 2021-02-11 Diesel injector with an optimized valve assembly

Publications (1)

Publication Number Publication Date
EP4103831A1 true EP4103831A1 (en) 2022-12-21

Family

ID=69897196

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21705475.8A Pending EP4103831A1 (en) 2020-02-12 2021-02-11 Diesel injector with an optimized valve assembly

Country Status (3)

Country Link
EP (1) EP4103831A1 (en)
GB (1) GB2592019B (en)
WO (1) WO2021160765A1 (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2960485A1 (en) * 2014-06-24 2015-12-30 Delphi International Operations Luxembourg S.à r.l. Control valve

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GB2592019A (en) 2021-08-18
GB202001883D0 (en) 2020-03-25
WO2021160765A1 (en) 2021-08-19
GB2592019B (en) 2022-07-06

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