KR20030065294A - Piston engine - Google Patents

Abstract

In a piston engine comprising at least one cylinder 1, the combustion chamber 3 of the cylinder can be closed via at least one valve 5. The valve is guided by a valve housing 9 comprising a duct 8 arranged on top of the cylinder head 2 and connected to the combustion chamber, and through a fluid control device located above the valve housing 9. Can be lifted from the attached valve seat in the opposite direction of the force of the valve, through which a sufficient sealing and lubricating effect can be achieved in a simple manner in the region of the valve guide 10, and the hydraulic oil is supplied to the valve guide 10. The hydraulic fluid may be lubricated in the form of a regulated leak, the hydraulic fluid may be diverted by the high pressure of the fluid control device in the form of a regulated leak, and through the metering device 28 It can be metered during the cycle of control and can be supplied to the guide device 10.

Description

Piston engine

The present invention relates to a piston engine, in particular a two cycle large diesel engine comprising at least one cylinder. The combustion chamber of the cylinder can be closed through at least one valve. The valve is guided by a valve housing comprising a duct located above the cylinder head and connected to the combustion chamber, and through the hydraulic control device disposed above the valve housing, the lid is removed from the valve seat attached against the force of the reducing device. I can peel it off.

In the two-cycle large diesel engine known as above, the above-mentioned scheme takes into account the gasket in the upper region of the guide device attached to the exhaust valve. The gasket seals the space above the exhaust valve housing opposite the gap between the valve shaft and the guide device. In order to prevent the exhaust gases from passing through the space located above the gasket mentioned above and being disturbed through the contaminant particles passing with the exhaust gases, the guide device attached to the exhaust valve is provided in the area underneath the gasket. It moves together with the return air. This certainly proves not enough. In addition, the return air does not lubricate the guide surface.

The object of the present invention is to start from this and to improve the piston engine of the above-mentioned manner in a simple and inexpensive way, to achieve a reliable sealing and lubricating effect in the area of the valve guide.

1 is a cross sectional view of an upper portion of a cylinder of a two cycle large diesel engine including a valve guide device of an attached lubricator;

2 is a cross-sectional view of the metering device attached to a preplanned lubricator.

3 is a longitudinal sectional view taken along the line III-III of FIG. 2;

4 is an explanatory diagram corresponding to an operation situation different from the operation situation according to FIG. 3 of the metering device shown in FIG. 3;

The object of the present invention is achieved by allowing the valve guide device to lubricate with the hydraulic oil, which can be obtained in the form of a controlled leak from the high pressure region of the hydraulic control device, the valve control cycle into the metering device. Can be metered and supplied by the valve guide device.

The hydraulic oil which can be supplied by the valve guide device not only has one suitable lubricating effect, but also preferably excellent sealing effect is obtained. The hydraulic fluid used for sealing and lubrication is supplied through the hydraulic control, which advantageously eliminates the need for an additional supply. In this case, the adjusted leak is such that the level of lubricant expected is due to a decrease in the adjusted hydraulic pressure. Embodiments according to the present invention allow a relatively low production cost and required space to be realized. This advantage is further accentuated by the relatively inexpensive oil compared to the lubricant supplied to the cylinder liner. The hydraulic oil supplied through the valve guide device is metered and economically consumed. This, on the other hand, leads to a slow repair of the oil storage tank. Embodiments according to the invention achieve correspondingly excellent stability and economy.

Further preferred configurations and preferred variants of the general embodiments are disclosed in the following dependent claims. Therefore, it may be desirable for the inlet of the metering device to be connected with the buffer chamber arranged above. The buffer chamber is connected to the high pressure region of the hydraulic control device through the first choke device and to the pressureless reduction stroke through the second choke device. The buffer chamber preferably contains sufficient oil with reduced pressure at the level expected with the help of the choke system.

The second choke device preferably has a larger cross section than the first choke device. In this way a relatively high pressure reduction can be achieved.

The metering device can be increased through oil pressure in the opposite direction to the force of the discharge device and has a metering chamber bounded by a single stopper, the metering chamber being placed in front of the metering device continuously in a cycle of valve operation. Can be connected to the outlet of the metering device connected to the buffer chamber and at least one lubrication point. This makes it possible to achieve a metering that is not highly constrained by the oil pressure and the machine speed.

In another preferred embodiment, it can be adjusted via a stop that can prevent the reciprocation of the discharge device. In this way, the capacity of the metering chamber and the amount of oil which can be introduced in the case of valve control of the valve guide device can be adjusted and can be adjusted according to the needs of each case.

In another variant of the embodiments, the metering device is provided with a servovalve spool which is movable through the pressure in the buffer chamber acting in the opposite direction to the force of the reducing device. The measurement chamber may be connected to the outlet of the buffer chamber and the measurement chamber through the servo valve spool. This embodiment achieves self-regulation of the metering device through the pressure of the oil in the buffer chamber which rises and falls in the case of each valve control.

It may be desirable to consider the limited limit stop in advance for the movement of the servovalve spool. In this case, the inlet limit stop has an axis formed through tapping around. The shaft protrudes above the inlet of the metering device. The shaft in this case functions as a breaker plate, and the hydraulic oil flowing from the breaker plate to the metering device can bounce back. This weakens the movement of the servovalve spool, which guarantees a cost-effective operation.

Further preferred configurations and preferred variants of the above-described embodiments are set forth in the remaining dependent claims, which will become apparent from the detailed description of the embodiments according to the following figures.

The construction and operation of a two cycle large diesel engine is already known and no further explanation is required in connection with the present application. Engines of this kind usually comprise a plurality of cylinders 1 of the kind illustrated in FIG. 1. The cylinder 1 has a cylinder block not shown in detail and a cylinder head 2 disposed thereon and comprises a combustion chamber 3 bounded by an unmarked piston, the combustion chamber having an upper shaft. A discharge orifice 4 is provided in the direction, which can be adjusted via an attached exhaust valve 5.

The exhaust valve 5 comprises a valve disc 6 which interacts with a predesigned valve seat in the region of the outlet orifice 4. The valve disc is installed at the lower end of the spindle shaft 7, the valve shaft being disposed above the cylinder head 2 and including a discharge orifice 4 and an exhaust duct 8 connected thereto. You are guided and located in (9). In addition, the valve housing 9 comprises a guide block 10 arranged in an upper region covering the exhaust duct 8. The guide block is penetrated by the valve shaft 7, which is accommodated in two housing parts 11a, 11b which rest on the valve housing 9 above the guide block 10. The housing includes a valve control device in the housing upper portion 11a and a reducing device in the housing lower portion 11b.

The valve control device consists of a fluid connecting machine, which has a piston 12 at the end of the valve shaft 7 inserted into the housing upper portion 11a at the top, and above the piston 12. It is provided with the operating chamber 13 which is arrange | positioned at the housing upper part 11a, and delimits from the said piston 12. Although not shown in the drawings, the operating chamber may be moved according to a cycle of a hydraulic oil passage formed of high pressure through a pressure source composed of a pump that can be operated by an engine according to the purpose. In addition, the operation chamber 13 is connected to a supply pipe 14 connected to the high pressure portion of the pressure source. Feedback of the leaking oil passing through the piston 12 occurs through the pressure reducing pipe 15. The reduction piping starts from the planned space 16 in the housings 11a and 11b below the piston 12.

When the operating chamber 13 is pressurized, the piston 12 is moved downwards, through which the valve disc 6 opens in its original position and the outlet orifice 4 is unblocked. In order to close the outlet orifice 4, a reduction guide device is considered. The reduction guide device pulls up the valve 5 when the pressure in the operating chamber 13 drops. In the above-described embodiment, the reduction guide device is composed of a gas connecting machine considered in the lower portion 11b of the housings 11a and 11b. The gas connecting machine protrudes from the guide block 10 and fixes an area of the valve shaft 7 penetrating the lower portion 11b of the housing, and partially borders the space 16 below. A piston 17 and an operating chamber 18 constrained upward by the piston are considered in the housing 11b. The operating chamber can be supplied with compressed air via an air pipe 52 starting from a pressure source and considered with the back conveying valve 51. In the case of the downward movement of the piston 17, the more condensed compressed air functions as an air spring. Additionally, or alternatively, reducing springs may be contemplated that interact with the bottom of the piston 12.

The operating chamber 18 is located at the bottom of the housing 11a, 11b of the valve control device at the bottom disposed on the lid of the valve housing 9 opposite the gap between the valve shaft 7 and the guide block 10. The lower part 11b is closed through a gasket 20 disposed in an area of a collar 19 which is penetrated by the valve shaft 7. In order for the gasket 20 to be sufficiently protected against the movement of contaminant particles, the gap between the valve shaft 7 and the guide block 10 through which the valve shaft penetrates is at least one lubrication point 53 with lubricant. Sufficient sealing and lubrication. In an embodiment the lubrication site 53 is configured through a radial bore under the collar 19 comprising the gasket 20. The radial bore is connected to the lubricant reservoir via a lubrication pipe 21.

As lubricant, hydraulic oil guided by the high pressure region of the valve control device composed of a fluid connecting machine is used. The hydraulic oil can be used at a relatively low price. The operating chamber 13 comprises an axial protrusion. The protrusion is located on the piston 12 and performs a function of the damper 54 to weaken the valve 5 by the blocking action, and the piston protrusion enters, and the radial drill starts from the piston protrusion, and is supplied to the radial drill. The pipe 14 is connected. The hydraulic fluid is branched into an artificial leak in order to be supplied to and used in the lubrication site 53 by the bore system 55 connected with the operation chamber 13. The leak creates a controlled pressure drop.

In addition, the choke system best seen in FIG. 2 includes two choke systems 22 and 23 arranged side by side. The choke system is arranged at the inlet and outlet of the buffer chamber 24 which is connected to the bore system 55 and the corresponding operating chamber 13. The choke system 22 at the inlet is smaller and thinner than the choke system 23 at the outlet. The thin cross section of the choke system 22 at the inlet is 0.7 mm for a two cycle large diesel engine. The thin cross section of the choke system 23 at the outlet is 1.2 mm. Along with this, the reduction in pressure required for the ventilation of the valve 5 reaches a pressure suitable for the lubricant from about 160-200 bar to about 11-15 bar in the buffer chamber.

The buffer chamber 24 is constituted by a step bore in the upper region of the housing 11 connected to the branch pipe starting from the bore system 55. The inlet choke system 22 protrudes into the buffer chamber 24 and enters a perforated socket 25 which, with its own perforation, departs from the above mentioned bore system 55. It is connected to the branch line. The outlet choke system 23 is guided to a reduction pipe 26 which is perforated and attached to a pin 27 inserted into a wall bordering the circumferential surface of the radial bore of the buffer chamber 24. to be. As shown in FIG. 1, the reducing pipe 26 may be considered in the lower part of the piston 12 and guided to the space 16 partially below by the piston 17 of the gas apparatus. The space can be balanced on the reduction pipe 15.

As shown in FIG. 2, the metering device 28 is placed on the housings 11a and 11b, the inlet of which is connected to the buffer chamber 24. The hydraulic oil supplied to the lubrication site 53 through the metering device 28 is metered in during the cycle of valve control. In this case, the amount of oil supplied to the lubrication site along the valve reciprocation is not limited to the oil pressure and the engine speed.

The metering device 28 rests on two housings 11a, 11b of the valve control device and also includes two housings 30a, 30b. The lower part of the housing is composed of a housing block. The housing block is provided with a through hole 31 located at an axis passing perpendicular to the axis of the buffer chamber 24. The servo valve spool 32 is arranged inside the through hole, and the servo valve spool can move between the limit stops 33 and 34 that block the through hole 31. The relative distance of the stop surfaces of the two limit stops 33, 34 is larger than the length of the servo valve spool 32 by the possible stroke s of the servo valve spool 32. The inlet 29 of the metering device 28 mentioned above consists of a radial bore which is fitted into the through hole 31 in the region of the limit stop, here the limit stop 33, which radial housing is a housing. It is connected to the buffer chamber 24 through the communication path 35 considered in the lower part of the (30). The limit stop 33 of the inlet part is configured with the socket 36 protruding through the through hole 31 by the side tapping. The socket is located above the inlet 29 and rotates on the servo valve spool 32 on the front side and forms a boundary of the annular space connecting with the inlet 29.

The servovalve spool 32 interacts with an end that is remote from the inlet that includes the elastic reducing device. In addition, a pin 37 is considered that penetrates the limit stop 34 away from the inlet and is placed on the servovalve spool 32. The pin is installed with an extended spring disc of the through hole attached to the limit stop 34, which spring disc is referred to as an extended side spring 38 on the side facing away from the servo valve spool 32. Adjacent to.

The housing 30 of the metering device 28 is arranged perpendicularly to the through hole 31 for receiving the servovalve spool 32, as can be guessed in FIGS. 3 and 4, starting from the through hole. Two through holes 39, 40 having a small cross section are provided together. The transverse through-hole 40 away from the inlet forms the outlet of the metering device 28, to which the lubrication pipe 21 is connected. The other, i.e., the through-hole 39 close to the inlet is provided with a discharge device bordering the metering chamber 41 best shown in FIG.

The discharge device consists of a piston system 42 which enters the attached through opening of the protruding piston. The piston system interacts with the rear face including the reducing device in the form of a compression spring 43 facing away from the metering chamber 41. The through hole 39 is composed of a piston system 42 having a step formed therein and a through hole forming a step. In this way, the stop device in front of and automatically forming the boundary of the discharge action of the piston system 42 is configured. In Fig. 3 a step-by-step piston system 42 constituting the discharge device is attached with a radial stop surface and adjacent to the opposite stop on the side of the housing. In Figure 4 the radial stop surface is raised. The stroke s of the discharge device is limited by the stopper 45 attached to the rear piston system 42. The stopper 45 and the stroke s can be preferably adjusted.

The distance of the through hole 39 of the inlet part attached to the metering chamber 41 from the stop surface of the limit stop 34 far from the inlet is at least equal to the length of the servo valve spool 32. Therefore, as can be seen in FIG. 4, in the case where the servo valve spool 32 is adjacent to the limit stop 34 far from the inlet, the metering chamber 41 of the through-hole 31 connected to the buffer chamber 24. It is open above the area of the inlet. The servo valve spool 32 is enclosed and forms a communication groove 44 bounded by a tension bar at the front of the servo valve spool 32. The relative distance of the two through holes 39, 40 corresponds to the length of the maximum communication groove 44. As a result, the through-hole 39 of the inlet portion is connected to the other through-hole 40 when the servo valve spool 32 is adjacent to the limit stop 33 of the inlet, as can be seen in FIG. The contents of the metering chamber 41 can be supplied to the lubrication pipe 21.

During operation, the pressure inside the buffer chamber 24 rises or falls depending on the cycle of valve control. In the case of low pressure, the servo valve spool 32 is located at the limit stop 33 close to the inlet by the return spring 38. This position is shown in FIG. 3. The region of the through hole 31 which is bordered with an end close to the inlet of the servovalve spool 32 and connected to the buffer chamber 24 is limited to the annular space surrounding the socket 36. A pressure of 160-200 bar is generated in the operating chamber 13 for the ventilation of the valve 5. The pressure, as already detailed above, causes a pressure rise of about 11-15 bar inside the buffer chamber 24. At this pressure the servovalve spool 32 moves in a direction opposite to the force of the return spring 38, here to the left, and is placed at the limit stop 34 remote to the inlet. This location is shown in FIG. 4.

Before the servo valve spool 32 reaches the position according to FIG. 4, the inlet edge of the servo valve spool is close to the inlet and passes through the inlet of the through hole 39 attached to the metering chamber 41. Through this, the metering chamber 41 is connected to the buffer chamber 24. Hydraulic oil exposed to a pressure of 11-15 bar can correspondingly be pushed into the metering chamber 41. In this case the piston system 42, which is bounded by the metering chamber 41, rises above the previous stop which is opposite to the force of the return spring 43 and stops at the stop 45 at the rear. The stroke s illustrated in FIGS. 3 and 4 is in this case not limited to oil pressure and is only limited by the adjustment of the stop 45. The capacity of the metering chamber 41 thus made corresponds to the product of the cross sectional area of the through hole 39 attached in the area of the metering chamber 41 multiplied by the stroke s.

By this arrangement, the servo valve spool 32 is raised back to the position based on FIG. 3 by the return spring 38, and the pressure in the buffer chamber 24 is immediately lowered somewhat. The return spring 43 of the discharge device is thus determined, so that the discharge device is not yet active. The discharge device is first moved in the case of a pressure below the pressure which can be overcome by the reducing spring 38. In the case of the return movement of the servo valve spool 32 already mentioned, the inlet of the metering chamber 41 is separated from the buffer chamber 24 by the passage of the inlet edge of the servo valve spool 32. When reaching the end according to FIG. 3, the inner boundary of the inlet edge of the servovalve spool 32 passes through the inlet of the metering chamber 41. This is connected to the communication groove 44 enclosed around it, and forms the outlet of the metering device 28 on the communication groove and is connected to the through hole 40 connected to the lubrication pipe 21. Immediately, the metering chamber 41 is separated from the buffer chamber 24, and the actual force due to the pressure of the oil that acted in the opposite direction to the return spring 43 of the discharge device is weakened. Accordingly, at the end of the servo valve spool 32 based on FIG. 3, the contents of the metering chamber 41 are discharged from the metering chamber 41 via a discharge device moving to the return spring 43, and the enclosed servovalve spool 32 is closed. The through hole 40 which forms the outlet of the metering device 28 connected to the lubrication pipe 21 through the communication groove 44 of the through and leads to the lubrication place 53 attached through the lubrication pipe 21. .

Since the servovalve spool 32 is exposed in the buffer chamber 24 and the hydraulic oil contemplated for supply to the lubrication site 18 is self-acting, no additional slide actuation device is required. The metering of the hydraulic oil supplied to the lubrication site 53 that occurs during the cycle of valve activity due to the slide movement is not constrained by the oil pressure and engine speed in this case. The amount of oil supplied to the lubrication site 18 for each round trip of the valve corresponds to the capacity of the metering chamber 41. The adjustment capability can be adjusted via the corresponding adjustment of the stop 45.

The present invention configured as described above can improve the conventional piston engine in a simple and inexpensive manner, and can obtain a reliable sealing and lubricating effect in the region of the valve guide.

Claims (10)

As a piston engine, in particular a two cycle large diesel engine comprising at least one cylinder 1, the combustion chamber 3 of the cylinder can be closed via at least one valve 5, the valve being the cylinder head 2. Located above and guided by a valve housing 9 comprising a duct 8 connected to the combustion chamber 3 and in the opposite direction of the force of the reducing device via a hydraulic control device mounted on the valve housing 9. A piston engine capable of removing a lid from an attached valve seat, The guide device 10 attached to the valve 5 on the side of the valve housing can lubricate with the hydraulic fluid, and the hydraulic fluid can be obtained from the high pressure region of the hydraulic control in the form of a regulated leak. And metered during the cycle of valve control via the metering device (28) and may be supplied by the guide device (10). 2. The inlet 29 of the metering device 28 is connected to the buffer chamber 24, which is connected to the high pressure of the fluid control device via the first choke system 22. , Piston engine, characterized in that connected to the reduction pipe 26 through the second choke system (23). 3. A piston engine according to claim 2, characterized in that the second choke system (23) in the reducing direction has a larger and thinner cross section than the first choke system (22) lying in the inflow direction. 4. The metering chamber (1) according to any one of the preceding claims, wherein the metering device (28) is provided with a metering chamber (41) which can be enlarged in a direction opposite to the force of the discharging device which can move between the stoppers. A piston engine, characterized in that it can be connected to the outlet of the metering chamber at least connected to the buffer chamber 24 and the lubrication site 53 attached to the guide device 10 arranged before the metering device 28 during the cycle of valve control. . 5. A piston engine according to claim 4, characterized in that the reduction device has a piston system (42) for interacting with a spring (43) and entering a through hole (39) comprising a metering chamber (41). The piston engine according to claim 4 or 5, characterized in that the stroke (s) of the discharge device can in particular be adjusted by a stop device (45) which is movable in interaction with the piston system (42). 7. The servovalve spool 32 according to any one of the preceding claims, wherein the metering device 28 is movable in the opposite direction of the force of the reducing device 38 via the pressure in the buffer chamber 24. Piston engine, characterized in that via the servo valve spool can be selectively connected to the inlet region and the outlet of the metering device (28) connected to the buffer chamber (24). 8. The metering device 28 according to claim 4, wherein the metering device 28 receives the servo valve spool 32, and the two limit stops 33, 34 attached to the servo valve spool 32. Servo valve spool (30a, 30b) including the slide through hole 31 connected to the buffer chamber 24 in the region of the limit stop 33 facing the reducing device and facing the reducing device through Two through holes 39 and 40 attached to or passing through 32, a through hole 39 close to the inlet, including a metering chamber 41 and a dispensing device, and another through hole 40. ) Forms the outlet of the metering device 28, in which case the distance between the through holes 39, 40 coincides with the length of the circumferential communication groove 44 of the servovalve spool 32, The distance of the inlet through-hole 39 from the limit stop 34 away from the servo valve spool 32 A piston engine, characterized in that at least match the length. 9. A piston engine according to claim 8, characterized in that the inlet limit stop (33) has a socket (36) configured by tapping on the side and located above the inlet (29) of the metering device (28). 10. The servo valve spool 32 according to claim 8 or 9, wherein the reducing device attached to the servo valve spool 32 has a pin 37 passing through a limit stop 34 remote from the inlet. A piston engine, characterized in that it is supported by a return spring (38) arranged inside a limit stop (34) with a support surface facing away from).