WO2023088755A1 - Procédé pour tester une soupape d'injecteur - Google Patents

Procédé pour tester une soupape d'injecteur Download PDF

Info

Publication number
WO2023088755A1
WO2023088755A1 PCT/EP2022/081327 EP2022081327W WO2023088755A1 WO 2023088755 A1 WO2023088755 A1 WO 2023088755A1 EP 2022081327 W EP2022081327 W EP 2022081327W WO 2023088755 A1 WO2023088755 A1 WO 2023088755A1
Authority
WO
WIPO (PCT)
Prior art keywords
plunger
valve
oil
piston
chamber
Prior art date
Application number
PCT/EP2022/081327
Other languages
English (en)
Inventor
Grzegorz SOWINSKI
Original Assignee
Iop Marine A/S
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 Iop Marine A/S filed Critical Iop Marine A/S
Priority to KR1020247017914A priority Critical patent/KR20240105406A/ko
Priority to CN202280075535.8A priority patent/CN118234938A/zh
Priority to EP22817877.8A priority patent/EP4433701A1/fr
Publication of WO2023088755A1 publication Critical patent/WO2023088755A1/fr

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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • 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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • F02M65/006—Measuring or detecting fuel leakage of fuel injection apparatus
    • 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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • F02M65/003—Measuring variation of fuel pressure in high pressure line
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M15/00—Testing of engines
    • G01M15/02—Details or accessories of testing apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures

Definitions

  • the disclosure relates to a method for testing an injector valve for liquid gas, such as liquefied petroleum gas, LGP.
  • WO 2016/155746 discloses a method for testing an injector valve for liquid gas such as methanol.
  • the injector valve may be used for a two-stroke combustion engine.
  • the injector valve is supplied with sealing oil and control oil for controlling the supply of liquid gas.
  • the disclosed injector valve holds a plunger piston chamber for forming a compression chamber, a suction valve with a suction piston and a nozzle valve with a nozzle piston, one or more nozzle openings, and a control oil channel, wherein the fuel fluid channels provide a fluid connection from the plunger piston chamber to the nozzle openings when the suction valve is open by a pressure on the suction piston provided by a fluid pressure in the plunger piston chamber and when the nozzle valve is open by a pressure on the nozzle piston provided by a control oil pressure supplied via the control oil channel.
  • the injector valve is placed in a holder and the top cover is removed and substituted with a connecting piece and the pressure of the control oil is increased until the opening pressure for the nozzle valve is reached and the injector valve sprays oil from the nozzle openings into a spray chamber.
  • the opening pressure of the nozzle valve can be checked.
  • DK 202070137 A1 and WO 2021/043380 disclose a method for testing a valve body of an injector valve for liquid gas, and a method for testing the assembled injector valve.
  • the injector valve may be used as a fuel booster injection valve for the liquefied petroleum gas, LGP, and may be designed for performing two functions: to pressurize or boost the LPG to the desired injection pressure, and to ensure the correct timing and duration of the LPG injection.
  • the injector valve is supplied with sealing oil, plunge oil, control oil, and liquid petroleum gas, LPG, as fuel. Sealing oil is to prevent internal leak of liquid gas from entering unintended areas of the injector valve. Plunge oil is to pressurize the fuel, LPG.
  • Control oil is to control the timing of opening the injector valve for delivering compressed fuel gas to the combustion chamber. Liquid fuel is supplied to the injector valve constantly.
  • the valve body of the valve disclosed in DK 202070137 A1 and WO 2021/043390 holds a plunger piston chamber for forming a compression chamber, a suction valve with a suction piston, one or more fuel fluid channels, a nozzle valve with a nozzle piston, one or more nozzle openings, and a control oil channel, wherein the fuel fluid channels provide a fluid connection from the plunger piston chamber to the nozzle openings when the suction valve is open by a pressure on the suction piston provided by a fluid pressure in the plunger piston chamber and when the nozzle valve is open by a pressure on the nozzle piston provided by a control oil pressure supplied via the control oil channel.
  • the test of the valve body includes a test for verifying that the suction valve is tight, and a test for testing that the nozzle valve is tight.
  • a new injector valve for LPG for a two-stroke combustion engine has been developed by MAN Energy Solutions. This injector valve is also supplied with sealing oil and control oil for controlling the supply of liquid gas. Leaks if any could be very dangerous.
  • injector valve (44) for a combustion engine, which injector valve (44) comprises: a plunger piston sealing chamber (136) with a plunger piston (58) for forming a plunger compression chamber (74), said plunger piston (58) being provided with a plunger piston fuel oil opening (57b) at the bottom and said plunger piston (58) being controlled by supply of plunger oil at a plunger oil pressure via a cover plunger oil supply channel (63); a suction one-way valve (70) for fuel oil inlet via a suction valve fuel inlet (72), a plunger chamber supply channel (73) for supply of fuel oil from the suction one-way valve (70) to the plunger compression chamber (74) or to the plunger piston fuel oil opening (57b); a non-return valve (77) in fluid connection with the plunger compression chamber (74) or the plunger piston fuel oil opening (57b) via a non-return valve supply channel (75) for supply of fuel oil
  • the injector valve (44) before being tested is in an assembled condition with an atomizer (43) provided at a bottom of the valve (44) with the nozzle valve piston cut-off shaft tip (61c) protruding into the atomizer (43) for output of fuel from the nozzle valve opening (61 b) through the atomizer (43), and the atomizer (43) is removed when testing the injector valve (44).
  • the injector valve under test (44) further comprises a hydraulic piston chamber (155) holding a hydraulic piston (64) connected to the nozzle valve piston cut-off shaft (62), said hydraulic piston (64) being controlled by supply of control oil at a control oil pressure via control oil supply channels (141 , 142) for opening and closing the nozzle valve (61a).
  • the injector valve under test (44) further comprises sealing oil channels (131 , 132, 133, 134) in fluid connection with the plunger piston sealing chamber (136) for sealing the plunger piston (58), and in fluid connection with the hydraulic piston chamber (155) for sealing the hydraulic piston (64); and the method before the supply of plunger oil at step (b) comprises a sealing step by supplying sealing oil at a first sealing oil pressure to the plunger piston sealing chamber (136) and the hydraulic piston chamber (155) via the sealing oil channels (131 , 132, 133, 135), said first sealing oil pressure being higher than or equal to a predetermined sealing oil pressure required for sealing of the plunger piston (58) within the plunger piston sealing chamber (23) and for sealing of the hydraulic piston (64) within the hydraulic piston chamber (155).
  • the predetermined sealing oil pressure is in the range of 60-100 bar, such as in the range of 70-90 bar, such as around 80 bar.
  • the valve (44) being tested is placed in a function test valve holder (45) holding a nozzle valve piston lifting unit (46b) with a lifting piston (67) and lifting oil channels (66), said nozzle valve piston lifting unit (46b) being positioned with the lifting piston (67) engaging the nozzle valve piston cut-off shaft tip (61 b), and lifting oil is supplied at a predetermined pressure to the lifting piston (67) via the lifting oil channels (68) to thereby provide said predetermined lifting pressure for maintaining the nozzle valve piston cut-off shaft (62) in the lifted position.
  • the nozzle valve piston lifting unit (46b) further has lifting unit fuel oil leakage channels (83, 84) and a lifting unit fuel oil outlet (85) in fluid connection with the nozzle valve opening (61 b), whereby any fuel oil reaching out from the nozzle valve opening (61 b) will reach out from the lifting unit fuel oil outlet (85).
  • the lifting unit fuel oil outlet (85) faces an oil injector chamber (59) for collection of oil leaking or reaching out from the lifting unit fuel oil outlet (85).
  • the first test plunger oil pressure is in the range of 280-320 bar, such as about 300 bar.
  • the step of supplying plunger oil to the plunger piston (58) at step (b) comprises a first step of slowly increasing the pressure of supplied plunger oil to a first lower initial oil pressure and then proceed by increasing the oil pressure to the first test plunger oil pressure.
  • the first lower initial oil pressure is in the range of 10 to 50 bar.
  • the first predetermined test fuel oil pressure of step (c) is about 30 bar.
  • the non-return valve (77) comprises a non-return valve housing (87a), a non-return valve spindle (86), a non-return valve connection seat (76) and a non-return valve spring (87b) for forcing the non-return valve spindle (86) against the non-return valve connection seat (76) to thereby close the nonreturn valve (77), and the predetermined fuel oil pressure required for opening the nonreturn valve (77) is determined by the spring force of the non-return valve spring (87b).
  • the method further comprises:
  • the non-return valve (77) opens when the pressure of the supplied fuel oil overcomes the spring force of the non-return valve spring (87b).
  • the method further comprises:
  • the method further comprises:
  • the method further comprises: (h) increasing the pressure of the supply of fuel oil to the suction valve fuel inlet (72) until it reaches a pressure being in the range of 3-5 bar below the determined opening pressure of the non-return valve (77); and
  • the fuel oil is supplied by a fuel oil pump (37) in fluid connection with the suction valve fuel inlet, and the fuel oil pressure is read from a fuel oil pressure gauge (36).
  • the method further comprises:
  • the method further comprises: releasing the predetermined lifting pressure from the nozzle valve piston cut-off shaft tip (61c) to thereby close the nozzle valve (61a) with the spring force of the nozzle valve spring (96) forcing the nozzle valve piston cut-off shaft (62) against the nozzle valve connection seat (88); supplying fuel oil at a second predetermined test fuel oil pressure to the suction valve fuel inlet (72), via the suction one-way valve (70) and the piston fuel oil opening (57b) to the non-return valve supply channel (75), said second predetermined test fuel oil pressure being higher than a predetermined fuel oil pressure required for opening the nonreturn valve (77); and checking whether any of the supplied fuel oil reaches out from the nozzle valve opening (61 b). If the nozzle valve 61a is tight, no oil should be observed reaching out from the nozzle valve opening 61 b.
  • the second predetermined test fuel oil pressure is about 5 bar higher than the predetermined fuel oil pressure required for opening the non-return valve (77).
  • a method of testing an injector valve (44) for a combustion engine which injector valve (44) comprises: a plunger piston sealing chamber (136) with a plunger piston (58) for forming a plunger compression chamber (74), said plunger piston (58) being provided with a plunger piston fuel oil opening (57b) at the bottom and said plunger piston (58) being controlled by supply of plunger oil at a plunger oil pressure via a cover plunger oil supply channel (63); a suction one-way valve (70) for fuel oil inlet via a suction valve fuel inlet (72), a plunger chamber supply channel (73) for supply of fuel oil from the suction one-way valve (70) to the plunger compression chamber (74) or to the plunger piston fuel oil opening (57b); a non-return valve (77) in fluid connection with the plunger compression chamber (74) or the plunger piston fuel oil opening (57b) via a non-return valve supply channel (75) for supply of fuel oil to the non-re
  • the second predetermined test fuel oil pressure is about 5 bar higher than the predetermined fuel oil pressure required for opening the non-return valve (77).
  • test plunger oil pressure is in the range of 280-320 bar, such as about 300 bar.
  • a method of testing an injector valve (44) for a combustion engine which injector valve (44) comprises: a plunger piston sealing chamber (136) with a plunger piston (58) for forming a plunger compression chamber (74), said plunger piston (58) being controlled by supply of plunger oil at a plunger oil pressure via a cover plunger oil supply channel (63), and said plunger piston (58) holding first and second plunger leakage channels (89,90) providing a fluid connection from the bottom of the plunger piston (58) to an upper sidewall part of the plunger piston (58); a suction one-way valve (70) for fuel oil inlet via a suction valve fuel inlet (72), a plunger chamber supply channel (73) for supply of fuel oil from the suction one-way valve (70) to the plunger compression chamber (74); a non-return valve (77) in fluid connection with the plunger compression chamber (74) via a non-return valve supply channel (75) for supply of fuel oil from the plunger
  • the predetermined leakage test fuel oil pressure of step is in the range of 20 to 40 bar, such as in the range of 25 to 35 bar, such as about 30 bar.
  • the injector valve under test (44) further comprises a hydraulic piston chamber (155) holding a hydraulic piston (64) connected to the nozzle valve piston cut-off shaft (62), said hydraulic piston (64) being controlled by supply of control oil at a control oil pressure via control oil supply channels (141 , 142) for opening and closing the nozzle valve (61a).
  • the injector valve under test (44) further comprises sealing oil channels (131 , 132, 133, 134) in fluid connection with the plunger piston sealing chamber (136) for sealing the plunger piston (58), and in fluid connection with the hydraulic piston chamber (155) for sealing the hydraulic piston (64); and the method before the supply of fuel oil comprises a sealing step by supplying sealing oil at a first sealing oil pressure to the plunger piston sealing chamber (136) and the hydraulic piston chamber (155) via the sealing oil channels (131 , 132, 133, 135), said first sealing oil pressure being higher than or equal to a predetermined sealing oil pressure required for sealing of the plunger piston (58) within the plunger piston sealing chamber (23) and for sealing of the hydraulic piston (64) within the hydraulic piston chamber (155).
  • the predetermined sealing oil pressure is in the range of 60-100 bar, such as in the range of 70-90 bar, such as around 80 bar.
  • a method of testing an injector valve (44) for a combustion engine which injector valve (44) comprises: a plunger piston sealing chamber (136) with a plunger piston (58) for forming a plunger compression chamber (74), said plunger piston (58) being controlled by supply of plunger oil at a plunger oil pressure via a cover plunger oil supply channel (63); a suction one-way valve (70) for fuel oil inlet via a suction valve fuel inlet (72), a plunger chamber supply channel (73) for supply of fuel oil from the suction one-way valve (70) to the plunger compression chamber (74); a non-return valve (77) in fluid connection with the plunger compression chamber (74) via a non-return valve supply channel (75) for supply of fuel oil from the plunger compression chamber (74) to the non-return valve (77); a nozzle valve (61a) with a nozzle valve chamber (81), a nozzle valve piston cutoff shaft (62), a nozzle valve spring
  • the suction one-way valve 70 for fuel oil inlet is a one-way valve, whereby fuel oil being compressed can only escape via the non-return valve 77 into the nozzle valve chamber 81. Since the nozzle valve 61a should not be open, no fuel oil should reach out from the nozzle valve opening 61 b.
  • the predetermined nozzle valve test fuel oil pressure is equal to or larger than a predetermined fuel oil pressure required for lifting the plunger piston (58) to its most upper position when no plunger oil pressure is applied to the plunger piston (58).
  • the predetermined nozzle valve test fuel oil pressure of step (aa) is in the range of 20 to 40 bar, such as in the range of 25 to 35 bar, such as about 30 bar.
  • the first nozzle valve test plunger oil pressure is in the range of 140-160 bar, such as about 150 bar.
  • the injector valve under test (44) further comprises a hydraulic piston chamber (155) holding a hydraulic piston (64) connected to the nozzle valve piston cut-off shaft (62), said hydraulic piston (64) being controlled by supply of control oil at a control oil pressure via control oil supply channels (141 , 142) for opening and closing the nozzle valve (61a).
  • the injector valve under test (44) further comprises sealing oil channels (131 , 132, 133, 134) in fluid connection with the plunger piston sealing chamber (136) for sealing the plunger piston (58), and in fluid connection with the hydraulic piston chamber (155) for sealing the hydraulic piston (64); and the method before the supply of plunger oil at step (bb) or before the supply of fuel oil at step (aa) comprises a sealing step by supplying sealing oil at a first sealing oil pressure to the plunger piston sealing chamber (136) and the hydraulic piston chamber (155) via the sealing oil channels (131 , 132, 133, 135), said first sealing oil pressure being higher than or equal to a predetermined sealing oil pressure required for sealing of the plunger piston (58) within the plunger piston sealing chamber (23) and for sealing of the hydraulic piston (64) within the hydraulic piston chamber (155).
  • the predetermined sealing oil pressure is in the range of 60-100 bar, such as in the range of 70-90 bar, such as around 80 bar.
  • the non-return valve (77) comprises a non-return valve housing (87a), a non-return valve spindle (86), a non-return valve connection seat (76) and a non-return valve spring (87b) for forcing the non-return valve spindle (86) against the non-return valve connection seat (76) to thereby close the nonreturn valve (77), and the fuel oil pressure required for opening the non-return valve (77) is determined by the spring force of the non-return valve spring (87b).
  • the method further comprises: (dd) increase the supply of plunger oil to the plunger piston (58) in steps from the first nozzle valve test plunger oil pressure to a final nozzle valve test plunger oil pressure, said final nozzle valve test plunger oil pressure being larger than the nozzle valve plunger oil pressure required for opening the nozzle valve (61a) by overcoming the force of the nozzle valve spring (96); and
  • the final nozzle valve test plunger oil pressure is in the range of 175 to 200 bar, such as about 185 bar.
  • the supply of plunger oil is increased in steps of 5 bar.
  • the method further comprises: (ff) observing the pressure of supplied fuel oil when fuel oil droplets or a stream of fuel oil flow reach out from the nozzle valve opening (61 b) to thereby determine an opening pressure for the nozzle valve (61a).
  • the method further comprises: (gg) changing the supply of plunger oil to the plunger piston (58) from the final nozzle valve test plunger oil pressure to a closed nozzle valve test plunger oil pressure, said closed nozzle valve test plunger oil pressure having a value in the range of 5 -10 bar below the determined opening pressure for the nozzle valve (61a); and
  • Fig. 1 is a diagram of a test system with lines for supply of control oil, sealing oil, constant oil, lifting oil, fuel oil and test gas for testing an injector valve being placed in a function test valve holder according to an example embodiment;
  • Fig. 2 is a perspective view of an assembled injector valve according to an example embodiment
  • Fig. 3 is a longitudinal sectional view of the assembled injector valve of Fig. 2 according to an example embodiment
  • Fig. 4 is a longitudinal sectional view of the assembled injector valve of Fig. 3 when turned a first angle according to an example embodiment
  • Fig. 5 is a longitudinal sectional view of the assembled injector valve of Fig. 3 when turned a second angle according to an example embodiment
  • Fig. 6 is an amplified longitudinal sectional view of the top cover of the assembled injector valve of Fig. 2 according to an example embodiment
  • Fig. 7 is a longitudinal sectional view of the assembled injector valve of Fig. 3 when turned a third angle according to an example embodiment
  • Fig. 8 is an amplified view of the top cover with inlet ports of the assembled injector valve of Fig. 2 according to an example embodiment
  • Fig. 9 is an amplified longitudinal sectional view of a part of the sectional view of Fig. 3, which part illustrates the arrangement of a suction one-way valve for fuel inlet, a plunger piston compression chamber for fuel compression, and a non-return valve for delivery of compressed fuel according to an example embodiment;
  • Fig. 10 is an amplified longitudinal sectional view of a part of the amplified sectional view of Fig. 9, which part shows the non-return valve of Fig. 9 at a first angle according to an example embodiment;
  • Fig. 11 is an amplified longitudinal sectional view showing the non-return valve of Fig. 9 at a second angle for illustrating the arrangement of supply channels for supply of compressed fuel to a nozzle valve according to an example embodiment
  • Fig. 12 is an amplified longitudinal sectional view showing the arrangement of further supply channels for supply of compressed fuel to the nozzle valve according to an example embodiment
  • Fig. 13 is an amplified longitudinal sectional view of a part of the sectional view of Fig. 5, which part illustrates the arrangement of control oil supply and drain channels for actuation of a hydraulic piston according to an example embodiment
  • Fig. 14 is an amplified longitudinal sectional view of a part of the sectional view of Fig. 7, which part illustrates the arrangement of oil leakage channels for control and sealing oil leakage form the hydraulic piston according to an example embodiment
  • Fig. 15 is an amplified longitudinal sectional view of a part of the assembled injector valve of Fig. 2, which part illustrates the arrangement of oil leakage channels for fuel oil leakage from the hydraulic piston according to an example embodiment
  • Fig. 16 is an amplified longitudinal sectional view of a part of the assembled injector valve of Fig. 2, which part illustrates the arrangement of oil leakage channels for collecting oil leakage from an intermediate valve part and from an atomizer part according to an example embodiment;
  • Fig. 17 is an amplified longitudinal sectional view of a part of the sectional view of Fig. 16, which part illustrates the arrangement of oil leakage chambers for collecting leakage oil at an upper and a lower surface of the intermediate valve part according to an example embodiment;
  • Fig. 18 is a cross-sectional view of an upper surface part of the intermediate valve part of Fig. 17, illustrating the arrangement of different oil channels with oil sealings according to an example embodiment
  • Fig. 19 is a cross-sectional view of an upper surface part of a spindle guide housing facing a lower surface of the intermediate valve part of Fig. 17, illustrating the arrangement of different oil channels with oil sealings according to an example embodiment
  • Fig. 20 is a perspective view of the injector valve of Fig. 2 with an atomizer unit nut and a corresponding atomizer being removed according to an example embodiment;
  • Fig. 21 illustrates the injector valve of Fig. 20 when placed in a function test valve holder with a spray chamber and a nozzle valve piston lifting unit according to an example embodiment
  • Fig. 22 shows the function test valve holder of Fig. 21 from another angle illustrating the arrangement of a fuel oil inlet connection piece and a lifting oil connection piece according to an example embodiment
  • Fig. 23 is an amplified longitudinal sectional view illustrating the arrangement of the injector valve of Fig. 20 relative to the nozzle valve piston lifting unit of the function test valve holder according to an example embodiment
  • Fig. 24 is an amplified longitudinal sectional view illustrating the arrangement of the injector valve of Fig. 20 relative to the fuel oil inlet connection piece of Fig. 22 according to an example embodiment
  • Fig. 25 is an amplified longitudinal sectional view illustrating the arrangement of the injector valve of Fig. 20 relative to a fuel oil leakage outlet provided in a test sleeve of the function test valve holder of Fig. 21 according to an example embodiment;
  • Fig. 26 is a longitudinal sectional view illustrating the arrangement of the injector valve of Fig. 20 relative to the function test valve holder of Fig. 21 with a fuel oil drain sleeve for drain of oil from the fuel oil leakage outlet to the spray chamber according to an example embodiment;
  • Fig. 27 illustrates the assembled injector valve of Fig. 2 when placed in a detection test valve holder according to an example embodiment
  • Fig. 28 is a longitudinal sectional view illustrating the arrangement of the injector valve of Fig. 2 relative to the detection test valve holder of Fig. 27, which detection test valve holder holds a test air inlet port and a number of test air outlet ports according to an example embodiment;
  • Fig. 29 is a schematic diagram illustrating a test setup holding the detection test valve holder and injector valve of Fig. 28 with the test air outlet ports connection to a detection test liquid chamber according to an example embodiment.
  • Control/Sealing oil pressure control valves 8 Control/sealing oil air pump safety valve 9 Plunger oil directional valve 10
  • Control oil drain channels 142, 143a Control oil drain channels 142, 143a
  • Nozzle valve piston leakage chamber 159 Nozzle valve bushing leakage chamber 161
  • DTS lower air outlet port 110 DTS bottom air outlet chamber 204
  • An injector valve is designed by MAN Energy Solutions for a two-stroke combustion engine.
  • the engine is a duel fuel engine, which can run on standard heavy fuel oil or on a liquefied petroleum gas, LGP, such as a mixture of propane and butane.
  • LGP liquefied petroleum gas
  • the injector valve may be used as a fuel booster injection valve for the liquefied petroleum gas, LGP, and may be designed for performing two functions: to pressurize or boost the LPG to the desired injection pressure, and to ensure the correct timing and duration of the LPG injection.
  • the injector valve is supplied with sealing oil, plunge oil, control oil, constant oil, and liquid petroleum gas, LPG, as fuel.
  • Sealing oil is to prevent internal leak of liquid gas from entering unintended areas of the injector valve.
  • Plunge oil is to pressurize the fuel, LPG.
  • Control oil is to control the timing of opening the injector valve for delivering compressed fuel gas to the combustion chamber. Liquid fuel is supplied to the injector valve constantly. As long as the control oil is supplied, the injector valve will be closed, and when the supply of control oil is stopped, the valve will open when the pressure provided by the plunge oil to the fuel overcomes the opening pressure of the valve.
  • the supplied constant oil runs opposite to the direction of supplied control oil, and when control oil is supplied, a pressure is built up in the valve for closing the valve, and when the supply of control oil stops, there is no counter pressure to the supplied constant oil and the valve opens.
  • the injector valve holds a top cover 120, a barrel body 122 with a barrel flange 121 , a spindle guide housing 124, an intermediate part 123 between the barrel body 122 and the spindle guide housing 124, a spindle guide union nut 127 for connecting the barrel body 122 with the intermediate part 123 and the spindle guide housing 124, and atomizer union nut 126 holding an atomizer 43 for output of the compressed fuel gas. See Figs. 2 and 3.
  • the top cover 120 holds a plunger oil inlet port 49b, a control oil inlet port 130, a sealing oil inlet port 128, a constant oil inlet port 129, which during normal operation functions as a control oil drainage port, but which during test can be used for supply of oil at a constant pressure, and an air bleeding outlet 55.
  • the top cover 120 further holds cover plunger oil channel 63 in direct fluid connection with the plunger oil inlet port 49b, and cover fluid channels 56a, 56b, 56c, in fluid connection with the air bleeding outlet 55. See Figs. 3, 4, 5, 6 and 8.
  • the barrel body 122 holds a plunger piston 58, see Figs. 3 and 4, inserted into a plunger piston sealing chamber 136 and a plunger piston head chamber 156.
  • the plunger piston 58 has an upper piston head moving within the plunger piston head chamber 156, while the bottom of plunger piston 58 faces a plunger compression chamber 74.
  • a plunger piston fuel oil opening 57b In the bottom of plunger piston 58 there is provided a plunger piston fuel oil opening 57b.
  • the length of the plunger piston head chamber 156 determines the maximum movement of the plunger piston 58 and thereby the minimum size of the compression chamber 74.
  • the pressure of any fuel within the compression chamber 74 will be determined by the pressure provided to the top of the plunger piston 58.
  • a plunger head seal 187 is provided in the head of the plunger piston 58 for sealing the connection between the head of the plunger piston 58 and the plunger head chamber 156, and a piston chamber seal 188 is provided in the barrel body 122 for sealing the connection between plunger piston 58 and the compression chamber 74.
  • a bottom part of the plunger piston 58 holds two plunger compression chamber leakage channels 89 and 90, which can be in fluid connection with a third plunger compression chamber leakage channels 91 and a fuel oil leakage outlet 92, both arranged in the barrel body 122. When the plunger piston 58 is in the upper position, leakage channels 89 and 90 are in fluid connection with leakage channel 91 and thereby the fuel oil leakage outlet 92.
  • plunger oil When plunger oil is supplied to the plunger oil channel 63 via the plunger oil inlet port 49b, the plunger piston 58 is pressed downwards and a plunger oil chamber 57a is formed between the head of the plunger piston 58 and the bottom of the top cover 120, see Fig. 6.
  • the barrel body 122 also holds plunger piston head chamber leakage channels 148, 149 for drainage of leaked plunger oil from the plunger piston head chamber 156 into corresponding oil leakage outlets 158, 158, see Fig. 7.
  • the sealing oil inlet port 128 is in fluid connection with sealing oil channels 131 , 132, 133 and 134, which are provided in the barrel body 122, the intermediate part 123, and the spindle guide housing 124.
  • the sealing oil channels are fluidly connected to a plunger piston sealing bore 135 for supply of sealing oil to the plunger piston sealing chamber 136.
  • a suction one-way valve 70 with a suction valve inlet port 72 is provided in the barrel body 122 for supply of fuel to the plunger compression chamber 74 via a plunger chamber supply channel 73. Compressed fuel is led from the plunger piston compression chamber 74 into a non-return valve 77 via a non-return valve supply channel 75. When the plunger piston 58 is at the bottom of the plunger piston compression chamber 74, the fuel is supplied from the plunger chamber supply channel 73 via the plunger piston fuel oil opening 57b into the non-return valve supply channel 75.
  • the non-return valve 77 is formed by a non-return valve housing 87a holding a non-return valve spindle 86, which is pressed through a non-return valve connection seat 76 by a non-return valve spring 87b.
  • the non-return valve 77 opens and fuel is supplied from nozzle-valve chamber supply channels 78a, 78b in the barrel body 122, via nozzle-valve chamber supply channels 79a, 79b in the intermediate part 123, through nozzle-valve chamber supply channels 80a, 80b in the spindle guide housing 124 into a nozzle valve chamber 81 formed in the spindle guide housing, see Figs. 11 and 15.
  • a non-return valve upper chamber 186 is formed around the upper part of the non-return valve housing 87a and a non-return valve seal 185 is provided as a seal between the nonreturn valve housing 87a and the barrel body 122.
  • a first non-return valve leakage chamber 145 is provided for collection of fuel leaking through the seal 185, which first leakage chamber 145 is in fluid connection with a first non-return valve leakage channel 144, which ends in the fuel oil leakage outlet 92.
  • a second non-return valve leakage chamber 147 inside the non-return valve housing 87a is via a second non-return valve leakage channel in fluid connection with the first non-return valve leakage chamber 145, see Fig. 3 and 10.
  • the spindle guide housing 124 holds a hydraulic piston 64 within a hydraulic piston bushing 125, see Fig. 15.
  • the hydraulic piston 64 connects to a nozzle valve piston guide 95 further connected to a nozzle valve piston cut-off shaft 62 forming part of a nozzle valve 61a.
  • the nozzle valve 61a holds a nozzle valve spring 96 within the nozzle valve chamber 81 for pressing the nozzle valve piston cut-off shaft 62 against a nozzle valve connection seat 88, with a nozzle valve lower chamber 82 being formed above the connection seat 88.
  • the nozzle valve piston cut-off shaft 62 holds a nozzle valve piston cut-off shaft tip 61c protruding through a nozzle valve opening 61b.
  • the nozzle valve 61a opens and fuel flows is sprayed out via the nozzle valve opening 61 b and the atomizer 43.
  • the pressure on the hydraulic piston 64 is determined by the pressure of supplied control oil.
  • the control oil is supplied from the control oil inlet port 130 via a first control oil supply channel 140 in the barrel body and a second control oil supply channel 141 in the intermediate part 123 to a hydraulic piston actuation chamber 65 formed on top of the hydraulic piston 64.
  • the control oil is drained from the piston actuation chamber 65 to the constant oil inlet port 129 via a control oil drain restriction 143b and a first control oil drain channel 143a in the intermediate part 123, and further via a second control oil drain channel in the barrel body 122, see Figs. 5 and 15.
  • Sealing oil is supplied to the hydraulic piston bushing 125 from the sealing oil inlet port 128 via the sealing oil channel 134 into a hydraulic piston sealing bore 137, which is fluidly connected to a hydraulic piston sealing channel 138 and a hydraulic piston sealing chamber 139 facing the hydraulic piston 64 for sealing the piston 64 within the bushing 125, see Figs. 4 and 14.
  • the upper part of the hydraulic piston 64 holds a hydraulic piston head moving within a hydraulic piston chamber 155, and the hydraulic piston head holds a hydraulic piston seal 189 for sealing the hydraulic piston head within the hydraulic piston chamber 155.
  • the lower surface part of the intermediate part 123 holds a hydraulic piston actuation chamber seal 184 for sealing the hydraulic piston actuation chamber 65, see Fig. 14.
  • a number of seals, sealing chambers and sealing channels are provided in connection with the hydraulic piston bushing 125 as illustrated in Figs. 14 and 15 and discussed in the following.
  • Control oil may leak through the hydraulic piston seal 189 into the hydraulic piston chamber 155 from where it may flow to a hydraulic piston bushing leakage chamber 153 via a hydraulic piston bushing leakage channel 154. From the leakage chamber 153 the leaked control oil may flow to the oil leakage outlet 158 via first, second and third control and sealing oil leakage channels 152, 151 and 150.
  • the hydraulic piston bushing 125 holds a first upper hydraulic piston bushing seal 190 for sealing of control oil, which may flow from the actuation chamber 65 via the seal 189 and into the hydraulic piston bushing leakage chamber 153.
  • the hydraulic piston bushing 125 also holds a second hydraulic piston bushing seal 191 for sealing of sealing oil, which may flow from the sealing bore 137 to the leakage chamber 153, and a third hydraulic piston bushing seal 192 for sealing of sealing oil, which may flow from the sealing bore 137 into a nozzle valve bushing leakage chamber 161 , which is fluidly connected to a first fuel oil leakage channel 162 in the spindle guide housing 124, a second fuel oil leakage channel 163 in the intermediate part 123, and a third fuel oil leakage channel 164 in the barrel body 122.
  • a nozzle valve leakage chamber 159 is provided, which is connected to the leakage chamber 161 via a fourth fuel oil leakage channel 160, whereby supplied fuel leaking from the nozzle valve chamber 81 along the nozzle valve piston guide 95 can flow from the leakage chamber 161 to the first fuel oil leakage channel 164.
  • Figs. 16 and 17 show the arrangement of further leakage chambers and channels. Fuel oil supplied from the nozzle valve chamber 81 , via the nozzle valve lower chamber 88 and passing the nozzle valve piston cut-off shaft 62 may leak into an atomizer fuel oil leakage chamber 194 between the atomizer 43 and atomizer union nut 126.
  • the leaked fuel oil may pass an atomizer fuel oil leakage channel 168 and a spindle guide upper leakage oil chamber 171 in the spindle guide housing 124, an intermediate upper leakage oil chamber 170 and an intermediate leakage oil collecting channel 169 in the intermediate part 123, an into an upper oil leakage channel 167 in the barrel body 122, and out via a upper oil leakage outlets 165 and 166, which are fluidly connected to the upper oil leakage channel 167.
  • An intermediate outer leakage chamber 198 is provided between the intermediate part 123 and the spindle guide union nut 127, and an intermediate leakage oil outlet channel 197 connects the channel 169 to the leakage chamber 198.
  • the intermediate part 123 has a number of supply and leakage channels passing through between the barrel body 122 and the spindle guide housing 124, which demands a corresponding number of seals. This is illustrated in Figs. 18 and 19, where Fig. 18 is a cross-sectional view of an upper surface part of the intermediate valve part 123, and Fig. 19 is a cross-sectional view of an upper surface part of the spindle guide housing 124 facing a lower surface of the intermediate valve part 123.
  • a first intermediate upper sealing ring 172 seals the second control oil supply channel 141
  • a second intermediate upper sealing ring 173 seals the first control oil drain channel 143a
  • a third intermediate upper sealing ring 174 seals the sealing oil channel 133
  • a fourth intermediate upper sealing ring 175 seals the second control and sealing oil leakage channel 151
  • a fifth intermediate upper sealing ring 176 seals the second fuel oil leakage channel 163
  • a sixth intermediate upper sealing ring 177 seals the nozzle valve supply channel 79a
  • a seventh intermediate upper sealing ring 178 seals the nozzle valve supply channel 79b.
  • the intermediate upper leakage oil chamber 170 is provided between the sealing rings 172, 173, 174, 175, 176, 177 and 178 for collection of leaked oil and, with the leakage oil chamber 170 being connected to the intermediate leakage oil collecting channel 169.
  • a first spindle guide upper sealing ring 179 seals the nozzle valve supply channel 79b
  • a second spindle guide upper sealing ring 180 seals the nozzle valve supply channel 79a
  • a third spindle guide upper sealing ring 181 seals the second fuel oil leakage channel 163
  • a fourth spindle guide upper sealing ring 182 seals the second control and sealing oil leakage channel 151
  • a fifth spindle guide upper sealing ring 183 seals the sealing oil channel 133.
  • the spindle guide upper leakage oil chamber 171 is provided between the sealing rings 179, 180, 181 , 182 and 183 for collection of leaked oil and, with the leakage oil chamber 171 being connected to the intermediate leakage oil collecting channel 168.
  • the upper surface part of the spindle guide housing 124 also has a centre opening for connection to the hydraulic piston bushing 125 holding the hydraulic piston 64.
  • a spindle guide union nut inner sealing ring 199 is provided as a seal between the spindle guide union nut 127 and the spindle guide housing 124, and a spindle guide housing seal 201 is provided as a seal between the atomizer union nut 126 and the spindle guide housing 124, see Fig. 16. Furthermore, a spindle guide union nut outer sealing ring 200 is provided at the outside of the spindle guide union nut 127, which is also illustrated in Fig. 16.
  • the atomizer union nut 126 and the atomizer 43 are removed from the injection valve as illustrated in Fig. 20. This leaves the spindle guide housing 124 uncovered with the tip of the nozzle valve piston cutoff shaft 62 protruding at the end of the spindle guide housing 124. The spindle guide union nut 127 is maintained.
  • the function test includes a test of the non-return valve 77, which requires that the nozzle valve piston cut-off shaft 62 is lifted from the nozzle valve connection seat 88 to keep the nozzle valve open.
  • the injection valve 44 of Fig. 20 is installed in a function test valve holder 45, see Figs. 21 to 26, and supplied with oil and gas for testing delivered by the test system 1 of Fig. 1.
  • the function test valve holder 45 holds a function test top plate 46a, a nozzle valve piston lifting unit 46b, valve holder nuts 46c for connecting the function test top plate 46a with the lifting unit 46b, a function test sleeve 46e, and an oil injection chamber 59 beneath the lifting unit 46b.
  • a drain hose hole 60 goes through the lifting unit 46b into the drain hose chamber 59.
  • Function test valve connecting nuts 46d holds the injection valve 44 of Fig. 20 in position during the function test.
  • the function test sleeve 46e is dimensioned to fit to the barrel body 122 of the injector valve 44 and holds a fuel inlet channel 71 facing the suction valve inlet port 72 of the barrel body 122, and a fuel oil connecting piece 47 is connected to the fuel inlet channel 71 for inlet of fuel oil.
  • a function test sleeve fuel oil leakage outlet 93 is provided in the function test sleeve 46a and faces the fuel oil leakage outlet 92 of the barrel body 122.
  • a fuel oil drain sleeve 94 can be connected to the fuel oil leakage outlet 93 and passed through the drain hose hole 60 into the drain hose chamber 59.
  • a plunger oil connecting piece 49a is connected to the plunger oil inlet port 49b
  • a control oil connecting piece 50 is connected to the control oil inlet port 130
  • a sealing oil connecting piece 51 is connected to the sealing oil inlet port 128, and
  • a constant oil connecting piece 52 is connected to the constant oil inlet port 129.
  • the air bleeding outlet 55 is provided with an air bleed stop valve 53, which connects to an air bleed drain hose 54. During a preliminary deaeration process, the air bleed stop valve 53 is open and the air bleed drain hose 54 is led through the drain hose hole 60 into the oil injector chamber 59.
  • the nozzle valve piston lifting unit 46b holds has a lifting oil channel 66 connected to a lifting oil connecting piece 48 for input of lifting oil from the test system 1 .
  • a centre part of the lifting unit 46b is dimensioned to fit closely to the protruding tip of the nozzle valve piston cut-off shaft 62 when inserted into the function test valve holder 45, and a lifting piston 67 is arranged in the lifting unit 46b for lifting the the nozzle valve piston cut-off shaft 62 when lifting oil is supplied to the lifting oil channel 66.
  • the length of the lifting of the nozzle valve piston cut-off shaft 62 is here denoted piston push up distance 68. Fuel oil may leak along the lifted nozzle valve piston cut-off shaft 62 into lifting unit fuel oil leakage channels 83, 84 and out into the oil injection chamber 59 via a lifting unit fuel oil outlet 85.
  • first, second, third, fourth and fifth barrel body outer sealing rings 205, 206, 207, 208 and 209 are provided at the outer part of the barrel body 122 as illustrated in fig. 28.
  • the detection valve holder 97a holds a detection test sleeve 97b, a detection test top plate 97c, and a detection test bottom plate 97d.
  • the detection test bottom plate 97d has a center opening dimensioned to fit the atomizer 43 of the assembled injector valve 44, whereby the atomizer protrudes the bottom plate 97d into a detection test sleeve, DTS, bottom air outlet chamber 204, having a detection test sleeve, DTS, bottom air outlet port 114 and a detection test liquid drain valve 108.
  • injector valve 44 When fully assembled injector valve 44 is positioned in the detection valve holder 97a, with the injector valve 44 holding the plunger oil connecting piece 49a, the control oil connecting piece 50, the sealing oil connecting piece 51 , and the constant oil connecting piece 52.
  • the air bleeding outlet 55 is provided with the air bleed stop valve 53, which is closed during the leakage detection test and a plunge oil plug 115 is inserted into the plunger oil connecting piece 49a.
  • the detection test sleeve 97b is dimensioned to fit to the barrel body outer sealing rings 205, 206, 207, 208, 209 thereby forming a number of air inlet and outlet chambers.
  • the detection test sleeve 97b further holds a number of corresponding air inlet and outlet ports, which is illustrated in Fig. 28.
  • the detection test sleeve 97b hence holds a detection test sleeve, DTS, air inlet port 107 and a detection test sleeve, DTS, air inlet channel 195 leading into a detection test sleeve, DTS, air inlet chamber 196 being sealed by sealing rings 200 and 209; a detection test sleeve, DTS, lower air outlet port 110 facing a detection test sleeve, DTS, lower air outlet chamber 203 being sealed by sealing ring 200; a detection test sleeve, DTS, barrel body air outlet port 1 111 facing a detection test sleeve, DTS, barrel body outlet chamber I 210 being sealed by sealing rings 209 and 208; a detection test sleeve, DTS, barrel body air outlet port II 113 facing a detection test sleeve, DTS, barrel body outlet chamber II 211 being sealed by sealing rings 206 and 205; a detection test sleeve, DTS, barrel body air outlet port III
  • a detection test liquid chamber 106 is provided holding a liquid and detection test hoses, which are connected to the air outlet ports and connecting pieces, are ending in the liquid chamber 106 to thereby detect any air leakage by bubbles in the liquid chamber 106.
  • the detection test hoses are connected as follows: detection test hose 98 is connected to the control oil connecting piece 50, detection test hose 99 is connected to the sealing oil connecting piece 51 , detection test hose 100 is connected to the constant oil connecting piece 52, detection test hose 101 is connected to DTS barrel body air outlet port II 113, detection test hose 102 is connected to DTS barrel body air outlet port III 112, detection test hose 103 is connected to DTS barrel body air outlet port 1 111 , detection test hose 104 is connected to DTS lower air outlet port 110, and detection test hose 105 is connected to DTS bottom air outlet port 114.
  • Each of the detection test hoses holds a nonreturn valve 109.
  • Fig. 1 is a diagram of showing the test system 1 used for performing the function test of the injection valve 44 of Fig. 20.
  • the test system 1 comprises a gas inlet 1a, an air inlet 1b, a gas outlet 1c, a control oil outlet 1 d, a sealing oil outlet 1e, a fuel oil outlet 1 f, a plunger oil outlet 1g, a lifting oil outlet 1 h and a constant oil outlet 1 i.
  • Air is provided via the air inlet 1 b at a pressure in the range of 7 - 10 bar in , which pressurized air is used as input to pressure control valves, a plunger oil pressure control valve 12, lifting oil pressure control valve 28, control/sealing oil pressure control valve 8, and fuel oil pressure control valve 33.
  • a gas inlet 1a is provided for inlet of a test gas in the form of Nitrogen at a pressure in the range of 80-300 bar.
  • the pressurized Nitrogen is supplied to a Nitrogen booster 20 via a Nitrogen inlet non-return valve 22, and from the Nitrogen booster 20 the Nitrogen is supplied to a gas stop valve 24, with a Nitrogen gas pressure control valve 23 provided for controlling the pressure of the gas being output from the gas stop valve 24 to gas outlet 1c.
  • an oil tank 16 is provided for holding the hydraulic oil.
  • the oil tank 16 is provided with an oil tank filler cap 17, an oil tank stop valve 18, and an oil filter 19.
  • An outlet of the oil tank 16 is via the stop valve 18 and oil filter 19 connected to four air driven pumps, a plunger oil air driven pump 15 being controlled by the plunger oil pressure control valve 12, a control/sealing oil air driven pump 7 being controlled by the control/sealing oil pressure control valve 8 and the control/sealing oil air pump safety valve 9, a lifting oil air driven pump 31 being controlled by the lifting oil pressure control valve 28 and the lifting oil air pump safety valve 29, and a fuel oil air driven pump 37 being controlled by the fuel oil pressure control valve 33 and the fuel oil air pump safety valve 34.
  • the oil pressure from the plunger oil air drive pump 15 can be read from plunger oil pressure gauge 13
  • the oil pressure from the control/sealing oil air driven pump 7 can be read from a control/sealing oil pressure gauge 6
  • the oil pressure from the fuel oil air driven pump 37 can be read from a fuel oil pressure gauge 36.
  • a hydraulic accumulator 5 is provided, which accumulator 5 may be charged by fuel oil up to a pressure of 250 bar. However, in the present test system 1 the maximum fuel oil pressure is 50 bar.
  • the hydraulic accumulator 5 is a membrane type of accumulator. It has a chamber which is divided by a rubber membrane. On one side of the membrane is Nitrogen at a pressure of 20-25 bar, on the other side of the membrane is hydraulic oil supplied from the fuel oil air driven pump 37. While the pressure of hydraulic oil is 0 bar, then the whole volume of accumulator is filled with Nitrogen. While applying hydraulic oil at a pressure above 2-25 bar, then the Nitrogen will start compress, as the hydraulic oil will start filling the volume of hydraulic accumulator.
  • the purpose of the accumulator 5 in the test system 1 is to accumulate hydraulic oil inside with a pressure of 20-25 bar and to reduce oil pressure fluctuation coming from the fuel oil air driven pump 37.
  • a plunger oil directional valve 10 is provided for opening and closing of plunger oil supply, which can be supplied from the plunger oil air driven pump 15 or from the Nitrogen booster 20 to the plunger oil outlet 1 g.
  • the oil pressure from the plunger oil air driven pump 15 can be read from a plunger oil pressure gauge 13, while the oil pressure from the plunger oil air driven pump 15 can be released by a plunger oil pressure relief valve 11 , in which case released hydraulic oil will flow back to the oil tank 16.
  • a plunger oil pressure safety valve 14 is provided. The plunger oil pressure safety valve 14 is adjusted to a maximum working pressure of 320 bar at the output side of the plunger oil air driven pump 15. If the plunger oil pressure exceeds the 320 bar, the plunger oil safety valve 14 will open and hydraulic oil will flow back to the oil tank 16.
  • the plunger oil directional valve 10 is also connected to the Nitrogen booster 20 via a booster oil pressure relief valve 21.
  • the Nitrogen booster 20 holds an inlet chamber with Nitrogen and an outlet chamber with hydraulic oil, which may be boosted in pressure by increasing the pressure of Nitrogen in the inlet chamber.
  • both the plunger oil pressure relief valve 11 and the plunger oil directional valve 10 are closed, the oil pressure of the outlet chamber in Nitrogen booster 20 can determined by the pressure of supplied Nitrogen and by the oil pressure produced the plunger oil air driven pump 15, and when opening the plunger oil directional valve 10, the oil pressure is supplied to the plunger oil outlet 1g.
  • Fuel oil is provided from the fuel oil air driven pump 37 to the fuel oil outlet 1f, and the oil pressure from the fuel oil air driven pump 37 can be read from the fuel oil pressure gauge 36, while the oil pressure from the fuel oil air driven pump 37 can be released by a fuel oil pressure relief valve 32, in which case released hydraulic oil will flow back to the oil tank 16.
  • a fuel oil pressure safety valve 35 is provided for protection of the fuel oil pressure gauge 36. The fuel oil pressure safety valve 35 is adjusted to a maximum working pressure of 60 bar at the output side of the fuel oil air driven pump 37. If the fuel oil pressure exceeds the 60 bar, the fuel oil safety valve 35 will open and hydraulic oil will flow back to the oil tank 16.
  • a control/sealing oil directional valve 2 is provided for opening and closing of oil supply from the control/sealing oil air driven pump 7 to the sealing oil outlet 1e or to a control oil directional valve 3, which controls opening an closing of oil supply to the control oil outlet 1d.
  • the oil pressure from the control/sealing oil air driven pump 7 can be read from the control/sealing oil pressure gauge 6, while the oil pressure from the control/sealing oil air driven pump 7 can be released by a control oil pressure relief valve 4, in which case released hydraulic oil will flow back to the oil tank 16.
  • Lifting oil is provided from the lifting oil air driven pump 31 to the lifting oil outlet 1 h, and the oil pressure from the lifting oil air driven pump 31 can be read from the lifting oil pressure gauge 30, while the oil pressure from the lifting oil air driven pump 30 can be released by a lifting oil pressure relief valve 27, in which case released hydraulic oil will flow back to the oil tank 16.
  • a constant oil valve 26 is provided for opening and closing of oil supply to the constant oil outlet 1 i, which is supplied with oil directly from the oil tank 16 via the oil tank stop valve 18 and oil filter 19. There is no air driven pump for generating an oil pressure in the oil supply line between the oil thank 16 and the constant oil outlet 1 i.
  • the function test includes a test of the non-return valve 77, which requires that the nozzle valve piston cut-off shaft 62 is constantly held in a lifted position from the nozzle valve connection seat 88 to keep the nozzle valve open.
  • the test of the non-return valve 77 is followed by several tests, for which the nozzle valve piston cut-off shaft 62 is in the normal operating mode. These tests include a test of the tightness of the nozzle valve piston cutoff shaft 62 against the nozzle valve connection seat 88, a test of a fuel injection sequence, and an indirectly test of the suction one-way valve 70.
  • the atomizer union nut 126 and the atomizer 43 are removed from the injection valve as illustrated in Fig. 20. This leaves the spindle guide housing 124 uncovered with the tip of the nozzle valve piston cutoff shaft 62 protruding at the end of the spindle guide housing 124. The spindle guide union nut 127 is maintained.
  • the injection valve 44 of Fig. 20 is installed in the function test valve holder 45, see Fig. 21.
  • the plunger oil connecting piece 49a is connected to the plunger oil inlet port 49b
  • the control oil connecting piece 50 is connected to the control oil inlet port 130
  • the sealing oil connecting piece 51 is connected to the sealing oil inlet port 128,
  • the constant oil connecting piece 52 is connected to the constant oil inlet port 129
  • the air bleed stop valve 53 is connected to the air bleeding outlet 55.
  • the top cover 120 of the valve 44 is secured to the function test valve holder 45 by two function test valve connecting nuts 46d.
  • test system 1 Before start of the test procedures, the test system 1 need to be configured to the initial settings as follows:
  • Air inlet 1b is connected to an external source of compressed air min 7 bar max 10bar, and gas inlet 1a is connected to an external source of nitrogen min 80bar.
  • the hydraulic accumulator 5 is filled with nitrogen up to 20-25 bar.
  • the fuel oil pressure safety valve 35 is adjusted to pressure 60bar (the purpose of safety valve 35 is to protect fuel oil pressure gauge 36 with range 0-60bar).
  • Safety valve 14 is adjusted to 320bar. All pressure relief valves 4, 11 , 27, 32 are set open.
  • the pressure control valves 33, 8, 28 and 12 are set in closed position to obtain an outlet pressure of the valves of 0 bar.
  • Fuel oil air pump safety valve 34 is adjusted to a pressure allowing the fuel oil air driven pump 37 to deliver an oil pressure of max 50 bar.
  • Control/sealing oil air pump safety valve 9 is adjusted to a pressure allowing the control/sealing oil air driven pump 7 to deliver an oil pressure of max 300 bar.
  • Lifting oil air pump safety valve 29 is adjusted to a pressure allowing the lifting oil air driven pump 31 to deliver an oil pressure of max 300 bar.
  • the oil tank stop valve 18 is set open.
  • the gas stop valve 24 is set closed
  • the oil tank 16 is filled with clean hydraulic oil with 7-10 cSt viscosity.
  • Flexible hoses are connected to the oil outlets 1 f, 1 d, 1 e,1 i, 1 h, 1 g., with the other ends of hoses being provided with quick couplings which are normally closed.
  • the quick couplings When the quick couplings are connected to corresponding connecting pieces on the injector valve and the test valve holder, the quick couplings opens.
  • the gas outlet port 1 c is equipped with a quick coupling which is normally closed
  • the oil outlets of the test system 1 are fluidly connected via the hoses and quick couplings to the oil connecting pieces by connecting the control oil outlet 1d to the control oil connecting piece 50, connecting the sealing oil outlet 1 e to the sealing oil connecting piece 51 , connecting the plunger oil outlet 1 g to the plunger oil connecting piece 49a, connecting the constant oil outlet 1 i to the constant oil connecting piece 52, connecting the fuel oil outlet 1f to the fuel oil inlet connecting piece 47, which is connected to the function test sleeve 46e, and connecting the lifting oil outlet 1h to the lifting oil connecting piece 48b, which is connected to the nozzle valve piston lifting unit 48a.
  • Plunger oil will now flow through the plunger oil connection piece 49a through the cover plunger oil channel 63 to the plunger oil chamber 57a until all air has been bled from the plunger oil chamber 57a through the cover fluid channels 56c, 56b, 56a, the air bleed stop valve 53 and through the air bleed drain hose 54 into oil the injection chamber 59.
  • the fuel oil will now flow through fuel inlet channel 71 and into the suction one-way valve 70 through the suction valve inlet port 72, and from the suction one-way valve 70 via the plunger chamber supply channel 73 via the plunger piston fuel oil opening 57b and via the non-return valve supply channel 75 into the non-return valve 77.
  • non-return valve 77 If the non-return valve 77 is not tight, there will be a leakage at the non-return valve connection seat 76 and the fuel oil will flow through the nozzle valve chamber supply channels 78a, 78b, 79a, 79b, 80a, 80b to the nozzle valve chamber 81. From nozzle valve chamber 81 the fuel oil will then pass to the nozzle valve lower chamber 82, passing the lifted nozzle valve piston cut-off shaft 62 and into lifting unit fuel oil leakage channels 83, 84 and out into the oil injection chamber 59 via lifting unit fuel oil outlet 85.
  • the non-return valve 77 holds the non-return valve spindle 86, which is pressed through the non-return valve connection seat 76 by the non-return valve spring 87b, and the nonreturn valve 77 opens when the fuel oil pressure operating on the non-return valve spindle 86 is larger than the pressure from the spring 87b.
  • the non-return valve 77 has passed the test, if the pressure has not decreased more than 2 bar.
  • the nozzle valve piston cut-off shaft 62 is in its normal operation mode without being constantly held in a lifted position from the nozzle valve connection seat 88.
  • the nozzle valve piston cut-off shaft 62 is released and will engage the nozzle valve connection seat 88 to hold a tight connection.
  • the fuel oil pressure through the suction on-way valve 70 will lift the plunger 58.
  • the plunger compression chamber leakage channel 90 meets the plunger compression chamber leakage channel 91 , and fuel oil starts to leak from plunger compression chamber 74 through the plunger compression chamber leakage channels 89, 90 and 91 to fuel oil leakage outlet chamber 92.
  • the fuel oil flows to the function test sleeve fuel oil leakage outlet 93 and continuous to flow through the fuel oil drain sleeve 94 to the oil injection chamber 59.
  • the pressure for the nozzle valve piston cut-off shaft 62 is determined by the pressure working in the area between the nozzle valve connection seat 88 and the diameter of the nozzle valve piston guide 95.
  • the opening pressure for the nozzle valve piston cut-off shaft 62 which is the pressure required to overcome the force from the nozzle valve spring 96, should be in the range of 388 - 447 bar.
  • the hydraulic gearing of the piston plunger 58 is 2.47. Therefore, the corresponding pressure to open the nozzle valve piston cut-off shaft 62 from the pressure supplied to the plunger oil chamber 57a on top of the plunger piston 58 is between 157 - 181 bar.
  • the control oil directional valve 3 is a 3-way valve with two positions. When in closed position there is no fluid connection from the control/sealing oil valve 2 to control oil outlet 1d, but there is a fluid connection from the control oil outlet 1d to the oil tank 16. So, when the valve 3 is closed the pressure of control oil at port 1d is released, and when the valve 2 is in open position the oil flows from via valve 2 through valve 3 and there is a control oil pressure at control oil outlet 1d.
  • the fuel oil pressure in the nozzle valve chamber 81 can now lift the nozzle valve piston cut-off shaft 62.
  • the suction one-way valve 70 is tested indirectly.
  • the lifting oil will now flow through the lifting oil channels 66 to the lifting piston 67, whereby the lifting piston 67 will be lifted to push up the nozzle valve piston cut-off shaft 62 a distance 68, which is about 2 mm, to keep the nozzle valve piston cut-off shaft 62 in the open position.
  • the nozzle valve piston cut-off shaft 62 is connected to the hydraulic piston 64, which is pushed up the same distance.
  • plunger oil pressure control valve 12 and plunger oil pressure gauge 13 with the plunger oil relief valve 11 and the booster oil relief valve 21 being closed and the plunger oil directional valve 10 being open.
  • the plunger oil pressure relief valve 11 shall be closed when increasing the plunger oil pressure.
  • the fully assembled injection valve 44 of Fig. 2 is exposed to a leakage detection test and placed in the detection valve holder 97a when performing the leakage detection test and supplied with air at 7 bar for detection of any leakages.
  • the valve 108 is a detection test liquid drain valve to drain liquid from the bottom of the detection test valve holder 97a when needed.
  • the compressed air will flow from air inlet port 107 through air inlet channel 195 to air inlet chamber 196, see Fig. 28.
  • the air will flow from air inlet chamber 196 through intermediate leakage oil outlet channel 197 and atomizer fuel oil leakage channel 168 to atomizer fuel oil leakage chamber 194 and then pass on to bottom air outlet chamber 204, see Figs 16 and 28. From chamber 204, the air passes through bottom air outlet port 114, valve 109h and hose 105 into the test liquid chamber 106. A leakage between union nut 126 and atomizer 43 will be visible as bubbles in liquid chamber 106.
  • the compressed air will flow from air inlet chamber 196 to upper oil leakage outlet 166, through upper oil leakage channel 167 into upper oil leakage outlet 165 and into barrel body air outlet chamber III 212, see Figs. 16 and 28. If any leakage through second barrel body outer sealing ring 206, the air will flow from chamber III 212 to chamber II 211 and into air outlet port II 113. From port 113 through valve 109d and hose 10 into the test liquid chamber 106. A leakage through sealing ring 206 will be visible as bubbles in liquid chamber 106.
  • the compressed air will flow from air inlet chamber 196 to upper oil leakage outlet 166, through upper oil leakage channel 167 into upper oil leakage outlet 165 and into barrel body air outlet chamber III 212, see Figs. 16 and 28. If any leakage through third barrel body outer sealing ring 207, the air will flow from chamber 212 to into fuel leakage outlet 92. From leakage outlet 92 the air can flow to barrel body outlet port III 112 and through valve 109e and hose 102 into the test liquid chamber 106. A leakage through third barrel body outer sealing ring 207 will be visible as bubbles in liquid chamber 106.

Landscapes

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

Abstract

Procédé pour tester une soupape anti-retour (77) d'une soupape d'injecteur (44) pour un moteur à combustion. La soupape (44) comprend une chambre d'étanchéité (136) avec un piston plongeur (58) pour former une chambre de compression (74), une soupape unidirectionnelle (70) pour une entrée d'huile combustible dans la chambre de compression (74), une soupape anti-retour (77) en connexion fluidique avec la chambre de compression (74) pour l'alimentation en huile combustible depuis la chambre de compression (74) dans la soupape anti-retour (77), et une soupape de buse (61a). La soupape de buse (61a) comprend une chambre (81), un siège de connexion (88), et un arbre de seuil de piston (62) ayant une pointe d'arbre de seuil (61c) faisant saillie à travers une ouverture (61b) de la soupape de buse (61a). Le procédé consiste à appliquer une pression de levage à la pointe d'arbre de seuil (61c) pour ainsi maintenir l'arbre de seuil (62) dans une position soulevée à partir du siège de connexion (88) dans laquelle la soupape de buse (61a) est ouverte, fournir de l'huile de plongeur au piston plongeur (58) à une première pression d'huile de plongeur de test pour fermer la chambre de compression (74), fournir de l'huile de combustible à une première pression d'huile de combustible de test à la soupape unidirectionnelle (70), ladite première pression d'huile de combustible de test étant inférieure à une pression d'huile de combustible prédéterminée requise pour ouvrir la soupape anti-retour (77), et vérifier si de l'huile de combustible fournie va au-delà ou non de l'ouverture de soupape de buse (61b). L'invention concerne également un procédé pour tester si la soupape de buse (61a) est étanche.
PCT/EP2022/081327 2021-11-16 2022-11-09 Procédé pour tester une soupape d'injecteur WO2023088755A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
KR1020247017914A KR20240105406A (ko) 2021-11-16 2022-11-09 인젝터 밸브의 테스트 방법
CN202280075535.8A CN118234938A (zh) 2021-11-16 2022-11-09 用于对喷射器阀进行测试的方法
EP22817877.8A EP4433701A1 (fr) 2021-11-16 2022-11-09 Procédé pour tester une soupape d'injecteur

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA202170565 2021-11-16
DKPA202170565A DK181283B1 (en) 2021-11-16 2021-11-16 Method for testing an injector valve

Publications (1)

Publication Number Publication Date
WO2023088755A1 true WO2023088755A1 (fr) 2023-05-25

Family

ID=84389244

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/081327 WO2023088755A1 (fr) 2021-11-16 2022-11-09 Procédé pour tester une soupape d'injecteur

Country Status (5)

Country Link
EP (1) EP4433701A1 (fr)
KR (1) KR20240105406A (fr)
CN (1) CN118234938A (fr)
DK (1) DK181283B1 (fr)
WO (1) WO2023088755A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016155746A1 (fr) 2015-03-27 2016-10-06 Iop Marine A/S Procédé pour tester une soupape d'injecteur pour un gaz liquide
WO2021043380A1 (fr) 2019-09-06 2021-03-11 Iop Marine A/S Procédé d'essai d'un corps de soupape d'une soupape d'injecteur et procédé d'essai d'une soupape d'injecteur
WO2021043390A1 (fr) 2019-09-03 2021-03-11 Nokia Technologies Oy Suppression de la mise en correspondance de signal
DK202070137A1 (en) 2020-03-03 2021-05-06 Iop Marine As Method for testing a valve body of an injector valve and method for testing an injector valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016155746A1 (fr) 2015-03-27 2016-10-06 Iop Marine A/S Procédé pour tester une soupape d'injecteur pour un gaz liquide
WO2021043390A1 (fr) 2019-09-03 2021-03-11 Nokia Technologies Oy Suppression de la mise en correspondance de signal
WO2021043380A1 (fr) 2019-09-06 2021-03-11 Iop Marine A/S Procédé d'essai d'un corps de soupape d'une soupape d'injecteur et procédé d'essai d'une soupape d'injecteur
DK202070137A1 (en) 2020-03-03 2021-05-06 Iop Marine As Method for testing a valve body of an injector valve and method for testing an injector valve

Also Published As

Publication number Publication date
DK202170565A1 (en) 2023-06-21
EP4433701A1 (fr) 2024-09-25
KR20240105406A (ko) 2024-07-05
DK181283B1 (en) 2023-06-21
CN118234938A (zh) 2024-06-21

Similar Documents

Publication Publication Date Title
US9599530B2 (en) Method of testing a gas shut-down valve and a system for exercising the method
KR20140079440A (ko) 가스 분사 밸브를 테스트하는 방법 및 상기 방법을 실행하기 위한 시스템
KR102468205B1 (ko) 액체 가스용 인젝터 밸브를 시험하는 방법
EP4028741B1 (fr) Unité de test et procédé de test d'une vanne entrée-sortie
DK181283B1 (en) Method for testing an injector valve
EP2110543B9 (fr) Valve de sécurité
JP7500710B2 (ja) インジェクションバルブのバルブボディをテストする方法及びインジェクションバルブをテストする方法
DK180461B1 (en) Method for testing a valve body of an injector valve and method for testing an injector valve
JPH0467021B2 (fr)
RU162302U1 (ru) Устройство подачи жидкого топлива к форсунке поршневого двигателя
JPH0420998Y2 (fr)

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22817877

Country of ref document: EP

Kind code of ref document: A1

DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)
WWE Wipo information: entry into national phase

Ref document number: 202280075535.8

Country of ref document: CN

ENP Entry into the national phase

Ref document number: 2024529118

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2022817877

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2022817877

Country of ref document: EP

Effective date: 20240617