JP2018084234A - By-pass valve and 2 stroke compression ignition internal combustion engine with large-sized turbocharger using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a by-pass valve for a large sized 2 stroke compression ignition internal combustion engine of a cross head type.SOLUTION: A by-pass valve 50 for releasing gas of a combustion chamber of a large sized 2 stroke compression ignition engine upon a blow-off event includes housing 51, 70, 73, a first bore 64 in the housing, a first piston 56 which regulates a first air pressure chamber 60 in the first bore, a stem 53 as a valve member 52 stored in the first piston and a valve member 52 having a head part 54 which can be engaged with an annular seat 55. The housing 51 includes a by-pass channel between an inlet 57 and an outlet 58, an annular seat and a by-pass chamber 63. A first side of the first piston forms a first effective pressure surface 61 facing the first air pressure chamber 60 and a second side of the first piston forms a second effective pressure surface 62 facing the by-pass chamber. A first side of the head part forms a third effective pressure surface 59 facing the inlet.SELECTED DRAWING: Figure 8

Description

  The present disclosure relates to the control of blow-off events in a two-stroke compression ignition internal combustion engine with a large turbocharger that includes a crosshead.

  A compression-ignition internal combustion engine with a crosshead type large two-stroke turbocharger is used, for example, as a propulsion of a large vessel for ocean navigation or as a main engine of a power plant. Not just a matter of scale, these two-stroke diesel engines are manufactured differently than other internal combustion engines. The exhaust valve weighs up to 400 kg, the piston has a diameter up to 100 cm, and the maximum operating pressure of the combustion chamber is typically several hundred bar. The force and piston size associated with this high pressure level is enormous.

  Excessive pressure can rarely occur in one of the cylinders, for example by mistaking the timing or amount of fuel injection. In order to cope with such excessive pressure, the force that pushes the cylinder cover to the top of the cylinder liner depends on the tension applied to the stay bolts that connect the cylinder cover to the base plate and maintain the engine structure. Be carefully controlled. Thus, when overpressure occurs, the cylinder cover is lifted and the overpressure leaks from between the top of the cylinder liner and the bottom of the cylinder cover. This system, commonly used in the art, is not without problems.

  When the cylinder cover is lifted up, explosive gas leaks and uncontrollable gas is released with a loud noise up to 170db. Any bystander suffers serious damage when side blow-off occurs, often in the form of a flame injection, due to a hot gas explosion. In addition, extremely hot and high pressure gas erodes the precision-machined mating surfaces of the cylinder liner and cylinder cover, and seals placed between the top of the cylinder liner and the bottom of the cylinder cover Damage the ring.

  Therefore, when a blow-off event occurs, processing of these surfaces and repositioning of the seal ring is required to obtain the desired liquid tightness. Therefore, the repair cost after blow-off occurs is significant. In addition, the tension applied to the stay bolt varies with changes in the engine and ambient temperature and cannot be accurately controlled. If blow-off occurred instantaneously, the tension on the stay bolts was relatively high, and the forces generated on the piston and crankshaft have previously damaged the large end and other expensive engine elements. Such an event is expensive and it is better to control the blow-off.

  Ship insurers (class societies) require large marine engines to be protected in a safe manner against damage due to overpressure in the combustion chamber.

  Here, some prior art provides an engine with a rupture disc on the wall of the combustion chamber designed to collapse to protect the engine against damage that may be caused by overpressure in the combustion chamber. The disadvantage of these rupture discs is that they are subject to aging due to pressure fluctuations in the combustion chamber and eventually collapse due to a relatively small overpressure, for example due to a small misfire. Therefore, rupture discs tend to collapse early. In particular, it is a problem that the engine must be stopped in order to replace a crushed bursting plate with a new plate. Therefore, the most commonly used rupture disc strategy is not optimal.

  Other engines with security valves have been provided to meet the need to be opened to vent gases from the combustion chamber when overpressure occurs in the combustion chamber. These are spring-loaded poppet valves. However, with respect to the explosive nature of the blow-off phenomenon, these poppet valves are not very effective because their maximum opening is insufficient to release the pressure sufficiently quickly.

  Therefore, these security valves cannot effectively provide the desired open area in a sufficiently short time, they simply have the effect of becoming an indicator or horn before the cylinder cover is lifted. Known valves cannot prevent the cylinder cover from lifting.

  Such a valve is disclosed in GB817,018. This document discloses a large two-stroke diesel engine with a separation ring between the cylinder liner and the cylinder cover, the separation ring having a bore for receiving a safety valve. However, the use of this safety valve was discontinued because the known safety valve was not reliable.

  Accordingly, there is a need for an improved blow-off control system for a crosshead type large two-stroke compression ignition internal combustion engine.

  GB745714 discloses a relief valve for a large two-stroke compression ignition engine.

  An object of the present invention is to provide a relief valve for a crosshead type large two-stroke compression ignition internal combustion engine which can solve or at least reduce the above problems.

  These and other problems are solved by the features of the independent claims. Further implementations will become apparent from the dependent claims, the description and the drawings.

In a first aspect, a relief valve is provided for escaping gas in a combustion chamber of a large two-stroke compression ignition engine during a blow-off event, the relief valve comprising:
-A housing;
-A first bore in the housing;
A first piston slidably disposed in the first bore and defining a first pneumatic chamber in the first bore;
A valve member housed in a first piston, the valve member comprising a stem and a head portion engageable with the annular seat;
The housing comprises a relief channel between the inlet and the outlet, and an annular seat in the relief channel;
The relief flow path comprises a relief chamber between the annular seat and the outlet;
The first side of the first piston forms a first effective pressure surface facing the first pneumatic chamber and the second side of the first piston faces a second effective surface facing the relief chamber; Forming a pressure surface,
The first side of the head forms a third effective pressure surface facing the inlet;
The first effective pressure surface is larger than the third effective pressure surface;

  By providing a valve member on a piston having an effective pressure surface that is significantly greater than the effective pressure surface of the head on which the pressure of the combustion chamber acts, the relief valve is configured to reduce the air pressure in the pneumatic chamber significantly below the pressure in the combustion chamber. Can be kept at pressure designed to open.

  Further, by providing a second effective pressure surface facing the relief chamber, when the valve is lifted, the pressure of the relief chamber is applied to the larger second effective pressure surface in addition to the third effective pressure surface. Acting in the opening direction, this ensures that the valve is kept open for a time long enough to allow the combustion chamber pressure to escape sufficiently. Without this additional third effective pressure surface, the valve member may close after a small relief, i.e., as soon as the pressure in the combustion chamber drops slightly, which is undesirable.

  In a first possible implementation of the first aspect, the first pneumatic chamber is fluidly connected to the port for connection with a pneumatic source. Therefore, an appropriate air pressure can be maintained in the first air pressure chamber.

  In a second possible implementation of the first aspect, the first effective pressure surface is preferably at least twice as large as the third effective pressure surface, more preferably of the third effective pressure surface. Four times the size.

  In a third possible implementation of the first aspect, the valve member is elastically biased away from the annular seat. Thus, the valve member moves to the fully open position when the engine is stopped and the air pressure is removed. Thereby, the relief valve is operated periodically.

  In a fourth possible implementation of the first aspect, the housing is slidably disposed within the second bore and the second bore, and defines a second pneumatic chamber within the second bore. A second piston, wherein the second piston is operably connected to the stem. By providing the second piston on the stem and providing the second pneumatic chamber, the closing force applied to the valve member by the air pressure is significantly increased, and the closing force when the diameters of the first and second pistons are equal. Is essentially doubled.

  In a fifth possible implementation of the first aspect, the second pneumatic chamber is fluidly connected to the port for connection with a pneumatic source. Thus, an appropriate pressure level can be maintained in the second pneumatic chamber.

  In a sixth possible implementation of the first aspect, the head and a portion of the stem are disposed in the escape chamber.

  In a seventh possible implementation of the first aspect, the valve member is between a fully open position and a fully closed position between a closed position where the head is seated in the annular seat and a fully open position. It can be displaced axially over a range of intermediate positions.

  In an eighth possible implementation of the first aspect, the outlet is a radial outlet.

  In a ninth possible implementation of the first aspect, the inlet is an axial inlet.

  In a tenth possible implementation of the first aspect, the second piston has a fourth effective pressure surface facing the second pneumatic chamber, the fourth effective pressure surface being the first effective pressure surface. It faces the same direction as the pressure surface.

  In an eleven possible implementation of the first aspect, the fourth effective pressure surface has substantially the same size as the first effective pressure surface.

In a twelfth possible implementation of the first aspect, the second piston has a fifth effective pressure surface facing away from the fourth effective pressure surface, and the second piston has the second An air attenuation chamber is defined in the bore of the first and the fifth effective pressure surface faces the air attenuation chamber.
By providing the air damping chamber, the closing operation of the valve member can be attenuated, so that damage to the valve head can be prevented.

  In a thirteenth possible implementation of the first aspect, the air attenuation chamber comprises an orifice that allows air trapped in the attenuation chamber, thus acting in the direction that the air pressure in the air attenuation chamber opens after the valve is closed. You can be guaranteed not to.

  In a fourteenth possible implementation of the first aspect, the first bore is disposed in the first housing part, the second bore is disposed in the second housing part, and the first The housing part and the second housing part are connected by an elastic member that allows relative movement between the first housing part and the second housing part in order to compensate for a dimensional difference in the relief valve due to thermal expansion. The

  In a fifteenth possible implementation of the first aspect, the second effective pressure surface is affected by the pressure in the relief chamber, thereby causing the valve member to move when the valve member is lifted from the annular seat. Apply force in the opening direction.

  In a sixteenth possible implementation of the first aspect, the first housing part and the second housing part are telescopically connected using an elastic member between them, the elastic member preferably being a dish. It is a spring.

  In a seventeenth possible implementation of the first aspect, the annular seat is arranged floating on the housing so that the annular seat can self-align.

  In a second aspect, a two-stroke compression ignition internal combustion engine with a large turbocharger having a crosshead is provided, the engine comprising a plurality of cylinders functioning as a combustion chamber, the cylinder comprising: a cylinder cover; a cylinder cover; A centrally located exhaust valve and an exhaust duct connecting the exhaust valve to an exhaust gas receiver, the cylinder cover fluidly combusting with the relief valve of any possible implementation of the first aspect A relief valve inlet connected to the chamber and a relief valve outlet fluidly connected to the blow-off conduit.

  In a first possible implementation of the second aspect, the relief valve allows gas to flow from the inlet to the outlet when the valve member is lifted from the annular seat, and the valve member is seated on the annular seat. To prevent gas from flowing from the inlet to the outlet.

  In a second possible implementation of the second aspect, the first effective pressure surface is subjected to air pressure regardless of the position of the valve member, and the second effective pressure surface is When lifted, the pressure in the escape chamber 63 is received.

  In a third possible implementation of the second aspect, the annular seat is located in a blow-off bore that extends through the cylinder cover.

  In a fourth possible implementation of the second aspect, the main surface of the annular seat is arranged obliquely with respect to the main direction of the blow-off bore.

  In a fifth possible implementation of the second aspect, the blow-off bore is connected to an exhaust duct or exhaust gas receiver via a blow-off tube to bypass the exhaust valve.

  In a sixth possible implementation of the second aspect, the relief valve comprises a cooling means, preferably the cooling means is a flow for passing a cooling medium through or supplying the relief valve around the relief valve. Provide a road.

  In a seventh possible implementation of the second aspect, the engine comprises a pneumatic system that supplies air pressure to an air consumption location associated with the engine, the pressure of the pneumatic system preferably increasing with increasing engine load. However, it decreases as the engine load decreases.

  These and other aspects and possible implementations will be apparent from the detailed description and drawings.

  In the following detailed portion of the disclosure, the present invention will be described in more detail with reference to exemplary embodiments shown in the drawings.

1 is a front view of a large two-stroke diesel engine in an exemplary embodiment. FIG. 2 is a side view of the large two-stroke engine of FIG. 1. FIG. 2 is a block diagram of the large two-stroke engine of FIG. It is a top view of a cylinder cover provided with a relief valve and an exhaust valve in an embodiment. It is sectional drawing along the AA line of FIG. It is an elevation view of the relief valve in the embodiment. It is another elevation view of the relief valve in the embodiment. FIG. 8 is a cross-sectional view of the relief valve of FIGS. 6 and 7 with the valve member of the relief valve in a different position. FIG. 8 is a cross-sectional view of the relief valve of FIGS. 6 and 7 with the valve member of the relief valve in a different position. FIG. 8 is a detailed cross-sectional view of the upper portion of the relief valve of FIGS. 6 and 7.

  In the detailed description that follows, a compression ignition diesel internal combustion engine with a large two-stroke turbocharger that includes a relief valve and a crosshead is described by way of example embodiment. 1 to 3 show a two-stroke compression ignition engine with a large low-speed turbocharger that includes a crankshaft 42 and a crosshead 43. FIG. 3 is a schematic representation of an engine with an intake and exhaust system. In this exemplary embodiment, the engine comprises six cylinders 1 arranged in a row. A compression ignition internal combustion engine with a large two-stroke turbocharger typically includes between 5 and 16 cylinders housed in an engine frame 45 and arranged in a row. The engine can be used, for example, as a main engine in a ship or a stationary engine for operating a generator in a power plant. The total output of the engine can be in the range of 5,000 to 110,000 kW, for example.

  The engine is a two-stroke uniflow type compression ignition engine having a scavenging port 19 in a lower region of the cylinder 1 and an exhaust valve 4 disposed at the center of a cylinder cover 22 in the upper part of the cylinder 1. The main direction of gas flow through the cylinder is “uniflow” from the scavenging port 19 at the bottom of the cylinder 1 toward the exhaust valve 4 at the top of the cylinder 1. The supply air passes through the scavenging ports 19 of the individual cylinders 1 from the supply air receiver 2 in the shape of a large, generally hollow cylindrical body. The piston 41 in the cylinder 1 compresses the supply air, and fuel is injected into the cylinder cover 22 from a fuel injection valve (not shown), and exhaust gas is generated following combustion.

  When the exhaust valve 4 is opened, the exhaust gas flows through the exhaust duct 35 associated with the cylinder 1 to the exhaust gas receiver 3 in the shape of a large hollow cylinder and through the first exhaust conduit 18. To the turbine 6 of the turbocharger 5, from which the exhaust gas flows to the atmosphere through the second exhaust conduit 7. Via the shaft 8, the turbine 6 drives a compressor 9 supplied with air through an air inlet 10. The compressor 9 carries the compressed air supply to an air supply conduit 11 connected to the air supply receiver 2.

  The intake air in the conduit 11 passes through the intercooler 12 that cools the supply air while keeping the compressor at about 200 ° C., and reaches a temperature of 36 ° C. to 80 ° C.

  The cooled supply air is driven by an electric drive motor 17 and guided to the intake receiver 2 through an auxiliary blower 16 that pressurizes the supply air flow at a low or partial load state of the engine. At higher engine loads, the turbocharger compressor 9 carries a fully compressed scavenging and the auxiliary blower 16 is bypassed via the check valve 15.

  4 and 5 show in more detail the top and cross sections of the exhaust valve 4 and cylinder cover 22, respectively. The exhaust valve 4 is securely bolted to the cylinder cover 22 together with the exhaust valve spindle 44 and an integral valve element disposed in the central opening of the cylinder cover 22. The exhaust valve spindle 44 is shown in a closed position in which the valve body of the exhaust valve spindle 44 is placed on the valve seat. When the exhaust valve 4 is opened, the combustion chamber 27 is connected to the exhaust duct 35. The exhaust duct 35 is connected to the exhaust gas receiver 3.

  The cylinder cover 22 forms the upper part of the combustion chamber 27. The cylinder cover 22 includes a plurality of cooling channels that are not visible in the drawing. In addition, fuel injectors, typically three fuel valves for each cylinder single fuel engine and six fuel valves for each cylinder dual fuel engine (not shown) It is received in a bore 80 in the cover 22 and has a fuel valve nozzle that projects into the combustion chamber 27.

  The exhaust valve 4 comprises a hydraulic exhaust valve actuator 47 with a hydraulic chamber 38 at the top of the valve spindle 44. The air spring 37 biases the valve spindle 44 upward in FIG. 5, that is, the closing direction, and the hydraulic actuator 47 biases the valve spindle 44 in the opening direction when the hydraulic actuator 47 is pressurized. Therefore, the exhaust valve spindle 44 is lifted by applying hydraulic pressure to the hydraulic actuator 47, and the air spring 37 reliably returns the valve spindle 44 to its closed position.

  The engine includes a blow-off conduit 36 that extends from the combustion chamber 27 to the exhaust duct 35 as shown. Alternatively, the blow-off conduit 36 extends from the combustion chamber 27 to the exhaust gas receiver 3. The cross-sectional area of the blow-off conduit 36 is large enough to quickly relieve the pressure in the combustion chamber 27 in the event of non-ignition or other cases where overpressure occurs in the combustion chamber 27. The relief valve 50 controls the opening and closing of the blow-off conduit 36, and the relief valve 50 is large enough fast to relieve the pressure in the combustion chamber 27 in the event of excessive pressure to prevent damage to the engine. The opening can be opened.

  A part of the blow-off conduit 36 is formed by a blow-off bore 29 in the cylinder cover 22. A blow-off conduit 36 connects the blow-off bore 29 to the exhaust duct 35 or the exhaust gas receiver 3.

  6 to 10 show the relief valve 50 in more detail. The relief valve 50 can be used as a cartridge in which a blow-off valve is inserted into a suitable bore 28 (FIG. 5) in the cylinder cover 22 as shown, or a relief valve (not shown). Can be provided with its own housing 51, 70, 73 so that can be an integral part of the cylinder cover 22.

  The relief valve 50 is inserted into the bore 28 in the cylinder cover 22 together with a bracket (housing) 73 protruding from the cylinder cover 22. The bracket (housing) 73 may be bolted or welded to the housing or may be an integral part of the housing. The bracket (housing) 73 includes a bore for receiving a bolt (FIGS. 6 and 7) for fixing the relief valve 50 to the cylinder cover 22. The housings 51, 70, 73 include an axially oriented inlet 57 and a large radially oriented outlet 58 to allow exhaust gas exhaust when the relief valve 50 is opened.

  The relief valve 50 includes a valve member 52 that is displaceable between a closed position shown in FIG. 8 and a fully open position shown in FIG. 9, that is, the valve member 52 is shown in FIG. It can move back and forth over a range of positions between the fully open position shown. The valve member 52 can be located at any intermediate position between the fully open position and the fully closed position. The relief valve 50 includes a relief passage that allows gas to flow from the inlet 57 to the outlet 58 when the valve member 52 is lifted, ie, when the valve member 52 is not in its closed position. A relief chamber 63 in the housing 51 connects the axial inlet 57 to the radial outlet 58. The annular seat 55 is provided around the inlet 57.

  In one embodiment, the housing is composed of several parts. The first housing part 51 uses a disc spring 76 or other elastic means between the first housing part 51 and the second housing part 70 to adapt to the effects of thermal expansion, so that the second housing It is connected to the component 70 in a telescopic manner. The bracket (housing) 73 is fixed to the second housing part 70.

  The valve member 52 includes a stem 53, and the stem 53 is provided with a head 54 that can be engaged with the annular seat 55 at one of the longitudinal ends of the stem 53. The annular seat 55 is preferably arranged in a state of floating on the first housing part 51 so that the annular seat 55 can be automatically aligned with respect to the head portion 54.

  A portion of the head 54 and stem 53 are disposed within the escape chamber 63.

  The first piston 56 is fixed to the stem 53. In one embodiment, the second piston 65 is also fixed to the stem 53 so as to be spaced apart from the first piston 56 in the longitudinal direction. The first piston 56 is slidably disposed within a first bore 64 within the first housing part 51, and the first piston 56 is within the first bore 64 and a first pneumatic chamber 60. Is specified. The second piston 65 is slidably disposed within a second bore 72 within the second housing part 70, and the second piston 65 is within the second bore 72 and a second pneumatic chamber 68. Is specified.

  The stem 53 is slidably and sealably received in a bore in the horizontal wall 81 in the second housing part 70.

  The end of the stem 53 provided with the head 54 extends toward the escape chamber 63. The valve head 54 forms a third effective pressure surface 59 that is exposed to the inlet 57 and exposed to the pressure of the combustion chamber 27 when the valve member 52 is in the closed position, as shown in FIG. It sits on the annular seat 55 on the surface of the head 54.

  When the valve member 52 is lifted, the head 54 is located in the escape chamber 63 as shown in FIG. 9, creating a substantial flow region for the flow of gas from the inlet 57 to the outlet 58. In one embodiment, the major surface of the annular seat 55 is disposed at an angle with respect to the main direction to the blow-off bore 29 to minimize flow restrictions through the blow-off bore 29. When the blow-off bore 29 is straight, the main direction is the longitudinal direction of the blow-off bore 29. When the blow-off bore 29 is bent, the main direction is the local direction of the curve at the position where the annular seat 55 intersects the blow-off bore 29.

  The first side of the first piston 56 forms a first effective pressure surface 61 that faces the first pneumatic chamber 60. The second side of the first piston forms a second effective pressure surface 62 that faces the relief chamber 63. The first side of the head 54 forms a third effective pressure surface 59 that faces the inlet 57, ie is exposed to the pressure of the combustion chamber 27.

  The first effective pressure surface 61 is larger than the third effective pressure surface 59, and preferably has a surface area that is at least twice as large. In the illustrated embodiment, the first effective pressure surface 61 is four times as large as the third effective pressure surface 59. However, it should be understood that in principle any ratio between the first effective pressure region and the third effective pressure region can be used, depending on the maximum pressure in the combustion chamber and the available air pressure. It is.

  The second effective pressure surface 62 is affected by the pressure in the relief chamber 63, thereby applying a force in the direction of opening the valve member 52 when the valve member 52 is lifted from the annular seat 55. According to this, the opening operation of the valve member 52 is prevented by preventing the valve member 52 from closing immediately when the pressure of the combustion chamber 27 drops slightly due to the momentary opening when the valve member 52 is lifted. Can be stabilized. If the force to move the valve member 52 in the opening direction is not generated by the second effective pressure surface 62, it may vibrate between a closed position and a slightly open position.

  In one embodiment, the second housing part 70 comprises a second bore 72. The second piston 65 is slidably disposed within the second bore 72 and defines a second pneumatic chamber 68 within the second bore 72.

  The second piston 65 is operatively connected to the stem 53 by, for example, a taper fit connection between the tapered bore of the second piston 65 and the corresponding tapered portion of the stem 53. Not only the head 54 but also the second piston 65 is preferably formed as an integral part of the stem 53.

  Both the first pneumatic chamber 60 and the second pneumatic chamber 68 are connected to a pneumatic source via a connection bore 71, a bore feed 77, and an air port 79.

  The air pressure in the first pneumatic chamber 60 acts on the first effective pressure surface 61, thereby generating a force in the direction of closing the valve member 52.

  The second piston 65 has a fourth effective pressure surface 66 that faces the second pneumatic chamber 68. The fourth effective pressure surface 66 faces the same direction as the first effective pressure surface 61. Thus, the air pressure acting on the fourth effective pressure surface 66 generates a force in the direction of closing the valve member 52, thereby assisting the first piston 56 in attempting to hold the valve member 52 in the closed position. .

  In one embodiment, the fourth effective pressure surface 66 has substantially the same size as the first effective pressure surface 61.

  The second piston 65 has a fifth effective pressure surface 67 facing away from the fourth effective pressure surface 66. The second piston 65 defines an air damping chamber 69 within the second bore 72 and the fifth effective pressure surface 67 faces the air damping chamber 69. The air attenuation chamber 69 is preferably connected to the atmosphere via an orifice so that any pressure increase in the attenuation chamber 69 disappears over time. In one embodiment, the orifice is formed by a small opening in the housing 70 that connects the attenuation chamber 69 directly to the surrounding atmosphere. As a result, the air damping chamber 69 can act as a damper by the pressure in the air damping chamber 69 acting on the fifth effective pressure surface 67 before the valve member 52 is closed, that is, the valve member 52 is closed. It is possible to ensure that the head 54 smoothly seats on the annular seat 55 by generating a force opposite to that.

  The valve member 52 is elastically biased in a direction away from the annular seat 55 by a compression coil spring 75 surrounding a free end portion of the stem 53 protruding from the third housing part (bracket) 73. In this regard, the compression coil spring 75 is tensioned between the flange or disc at the free end of the stem 53 and the proximal end of the housing 51, 70, 73. The coil spring 75 opens the valve member 52 to a fully open position when the first pneumatic chamber 60 and the second pneumatic chamber 68 are not pneumatic, i.e., when the large two-stroke diesel engine is stopped. Move it securely. This ensures that the valve member 52 operates regularly.

  In one embodiment, the relief valve 50 includes cooling means. The cooling means preferably comprises a flow path (not shown) for allowing the cooling medium to flow through the relief valve 50 or to be supplied around the relief valve 50.

  The second effective pressure surface 62 is exposed to the pressure of the escape chamber 63, and when the pressure from the combustion chamber 27 enters the release chamber 63, the valve member 52 is biased to the fully open position.

  When overpressure occurs in the combustion chamber 27, the pressure in the combustion chamber 27 acting on the third effective pressure surface 59 is the pressure generated by the first pneumatic chamber 60 acting on the first piston 56, and , Exceeding the combination of air pressure in the second air pressure chamber 68 acting on the second piston 65. Accordingly, the valve member 52 starts to move toward the fully open position as shown in FIG.

  When the pressure in the combustion chamber 27 is released, the force generated by the pressure in the first pneumatic chamber 60 and the second pneumatic chamber 68 is applied to the second effective pressure surface 62 and the third effective pressure surface 59 of the escape chamber 63. Over the opposite force due to the pressure applied to the valve member 52, the valve member 52 begins to move toward the fully closed position. As a result, the air in the air damping chamber 69 is compressed and slowly pushed out to the atmosphere through the orifice, so that the movement of the head 54 returning to the seat 55 is attenuated.

  Outflow grooves 82 are provided in the walls of the damping chamber 69 to remove the barrier formed by the second piston 65 when the letter has moved a predetermined distance. This causes the pressure in the damping chamber 69 to correspond to the supply pressure (before compression). Several outflow grooves 82 can be distributed around the circumference of the damping chamber 69. Outflow groove 82 is designed so that both piston rings and PTFE sealing rings can be used.

  When the valve member 52 is fully moved toward the fully open position, the movement of the valve member 52 is damped by a stack of disc springs 74 provided in the third housing part (bracket) 73. The second piston 65 engages the stack of disc springs 74 immediately before reaching the fully open position.

  The pneumatic system of a large two-stroke diesel engine includes a compressor or compression station (not shown) that supplies compressed air to air supply piping. The pressure in the supply line can be anywhere between 10 bar and 50 bar and is supplied to various places of consumption of compressed air associated with the large two-stroke diesel engine 1. In one embodiment, the atmospheric pressure system is formed by a conventional startup air supply system, which typically comprises a large turbocharged two-stroke compression ignition internal combustion engine with a crosshead. The air port 79 of the relief valve 50 is connected to an air supply system to ensure that the pressure in the pneumatic chamber of the relief valve 50 remains constant or can be varied.

  The standard maximum pressure in the combustion chamber 27 increases as the engine load increases and decreases as the engine load decreases. Thus, in one embodiment, the pressure of the pneumatic system is adjusted according to the engine load.

  Accordingly, by sizing the area size of the first effective pressure surface 61 and the fourth effective pressure surface 66 in relation to the size of the area of the third effective pressure surface 59, the relief valve 50 is Depending on the actual engine load, it can be sized to open at a pressure higher than the standard pressure of the combustion chamber 27 by a margin. The margin may be a constant differential pressure, or may increase with increasing engine load, and vice versa.

  The relief valve 50 can also operate with a constant air pressure supplied to the air port 79. In this case, the pressure should allow the relief valve 50 to open when the maximum pressure in the combustion chamber 27 exceeds the margin during normal engine operation. For example, the relief valve 50 is set to open at a pressure of 230 Bar when the maximum expected pressure, ie 100% engine load, is 200 Bar. The relief valve 50 adjusts the ratio between the third effective pressure surface 59 and the total of the first effective pressure surface 61 and the fourth effective pressure surface 66 in consideration of the air pressure supplied to the air port 79. Can be set to open at the required pressure.

  In an embodiment (not shown), the relief valve 50 is coupled to the engine's (not shown) electrical control unit and issues an alarm in the event of a blow-off event. In this regard, the relief valve 50 includes a pressure sensor (not shown) that detects the pressure in the air damping chamber 69 in one embodiment. An alarm is issued when the pressure in the air attenuation chamber 69 exceeds a threshold. Alternatively, the valve member 52 can be monitored by a motion sensor and an alarm is issued when the valve member 52 moves away from the closed position.

  In one embodiment, the balance of forces that determines whether the valve member 52 is biased to the closed or fully open position is the pressure of the gas in the combustion chamber 27 acting on the valve member 52, and The pressure of the air supplied to the relief valve 50 acting on the first piston 56 and the second piston 65 is determined only by the balance. Therefore, if there are elastic means for operating the relief valve when the engine is stopped, these elastic means should have a weak force that does not significantly affect the operation of the valve member 52 during engine operation. become.

  The invention has been described with various embodiments. However, by examining the drawings, the present disclosure, and the appended claims, other variations to the disclosed embodiments can be understood and implemented by those skilled in the art practicing the claimed invention. In the claims, the term “comprising” does not exclude other elements or steps, the indefinite article “a”, and “an” does not exclude a plurality. The mere fact that certain measures are recited in mutually different dependent claims does not indicate that a combination of these measured cannot be used effectively.

  Any reference signs used in the claims should not be construed as limiting the scope.

Claims (25)

A housing (51, 70, 73);
A first bore (64) in the housing (51, 70, 73);
A first piston (56) slidably disposed within the first bore and defining a first pneumatic chamber (60) within the first bore (64);
A valve member (52) housed in the first piston (56), the valve member (52) being engageable with a stem (53) and an annular seat (55) ( 54) having a valve member (52);
With
The housing (51) comprises an escape channel between the inlet (57) and the outlet (58), and the annular seat (55) in the escape channel;
The escape passage comprises an escape chamber (63) between the annular seat (55) and the outlet (58);
The first side of the first piston (56) forms a first effective pressure surface (61) facing the first pneumatic chamber (60), the second side of the first piston; The side forms a second effective pressure surface (62) facing the relief chamber (63),
The first side of the head (54) forms a third effective pressure surface (59) facing the inlet (57);
The first effective pressure surface (61) is larger than the third effective pressure surface (59);
A relief valve (50) for releasing gas in the combustion chamber of a large two-stroke compression ignition engine during a blow-off event. The first pneumatic chamber (60) is fluidly connected to an air port (79) for connection to a pneumatic source;
Relief valve (50) according to claim 1. The first effective pressure surface (61) is at least twice as large as the third effective pressure surface (59),
Relief valve (50) according to claim 1 or 2. The valve member (52) is elastically biased in a direction away from the annular seat (55).
Relief valve (50) according to any one of the preceding claims. The housing (51, 70, 73) is slidably disposed in the second bore (72) and the second bore (72), and the second bore (72) is second. A second piston (65) defining a pneumatic chamber (68) of said second piston (65), said second piston (65) being operably connected to said stem (53),
Relief valve (50) according to any one of the preceding claims. The second pneumatic chamber (68) is fluidly connected to an air port (79) for connection to a pneumatic source.
Relief valve (50) according to claim 5. A portion of the head (54) and the stem (53) is disposed within the escape chamber (63);
Relief valve (50) according to any one of the preceding claims. The valve member (52) is intermediate between the fully open position and the fully closed position between the closed position where the head (54) is seated on the annular seat (55) and the fully open position. Is axially displaceable over a range of positions,
Relief valve (50) according to any one of the preceding claims. The outlet (58) is a radial outlet,
Relief valve (50) according to any one of the preceding claims. The inlet (57) is an axial inlet,
Relief valve (50) according to any one of the preceding claims. The second piston (65) has a fourth effective pressure surface (66) facing the second pneumatic chamber (68), and the fourth effective pressure surface (66) is the first effective pressure surface (66). Facing the same direction as the effective pressure surface (61) of
Relief valve (50) according to any one of the preceding claims. The fourth effective pressure surface (66) has substantially the same size as the first effective pressure surface (61),
Relief valve (50) according to claim 11. The second piston (65) has a fifth effective pressure surface (67) facing away from the fourth effective pressure surface (66), and the second piston (65) An air damping chamber (69) is defined in the second bore (72), and the fifth effective pressure surface (67) faces the air damping chamber (69);
Relief valve (50) according to any one of claims 5 to 12. The first bore (64) is disposed in a first housing part (51), and the second bore (72) is disposed in a second housing part (70), The first housing part (51) and the second housing part (70) are arranged such that the first housing part (51) and the second housing part (70) are arranged to compensate for a dimensional difference in the relief valve due to thermal expansion. 70) connected by an elastic member (76) allowing relative movement between
Relief valve (50) according to any one of claims 5 to 13. The second effective pressure surface (62) is affected by the pressure in the relief chamber (63) so that when the valve member (52) is lifted from the annular seat (55), Applying force in the direction of opening the valve member (52),
Relief valve (50) according to any one of the preceding claims. The first housing part (51) and the second housing part (70) are telescopically connected using the elastic member (76) between them, and the elastic member is preferably a disc spring. (76)
Relief valve (50) according to any one of claims 5 to 13. The annular seat (55) is disposed in a state of floating on the housing (51, 70, 73) so that the annular seat (55) can be self-aligned.
Relief valve (50) according to any one of the preceding claims. A two-stroke compression ignition internal combustion engine with a large turbocharger comprising a crosshead (43),
A plurality of cylinders (1) functioning as a combustion chamber (27), the cylinder (1) comprising a cylinder cover (22) and an exhaust valve (4) disposed at the center of the cylinder cover (22) And an exhaust duct (35) for connecting the exhaust valve (4) to an exhaust gas receiver (3),
18. The cylinder cover (22) includes the relief valve (50) according to any one of claims 1 to 17 and the relief valve (50) fluidly connected to the combustion chamber (27). An inlet (57) and an outlet (58) of the relief valve (50) fluidly connected to the blow-off conduit (36).
engine. The relief valve (50) allows gas to flow from the inlet (57) to the outlet (58) when the valve member (52) is lifted from the annular seat (55), and the relief valve (50) prevents gas from flowing from the inlet (57) to the outlet (58) when the valve member (52) is seated on the annular seat (55);
The engine according to claim 18. The first effective pressure surface (61) receives air pressure regardless of the position of the valve member (52), and the second effective pressure surface (62) Receiving pressure in the relief chamber (63) when lifted from the annular seat (55);
The engine according to claim 18 or 19. The annular seat (55) is disposed in a blow-off bore (29) extending through the cylinder cover (22).
The engine according to any one of claims 18 to 20. The main surface of the annular seat (55) is disposed obliquely with respect to the main direction of the blow-off bore (29).
The engine according to claim 21. The blow-off bore (29) is connected to the exhaust duct (35) or the exhaust gas receiver (3) via a blow-off conduit (36) to bypass the exhaust valve (4).
The engine according to claim 21 or 22. The relief valve (50) comprises cooling means, preferably the cooling means for allowing a cooling medium to flow through the relief valve (50) or to supply around the relief valve (50). Comprising
The engine according to any one of claims 18 to 23. The engine includes a pneumatic system that supplies air pressure to an air consumption location associated with the engine, the pressure of the pneumatic system preferably increasing as the engine load increases and decreasing as the engine load decreases. ,
The engine according to any one of claims 18 to 24.

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