KR20070030707A - Muffler - Google Patents

Abstract

Mufflers has gas permeable openings (79), which are provided between the housing wall (44) and the adjusting body (77). The gas permeable openings connect the high pressure chamber (87) with the low pressure chamber (89) and the low pressure chamber can be connected with the interior area of the housing interior.

Description

Silencer {MUFFLER}

1 is a schematic cross-sectional view in longitudinal cut of a muffler having valve means and adjusting means in a blocking position;

Fig. 2 is an enlarged cross sectional view showing the valve means and the adjustment means in a cut position in the longitudinal direction.

FIG. 3 is a cross-sectional view similar to FIG. 1 but cut longitudinally with a silencer having valve means and adjustment means in an open position; FIG.

FIG. 4 is a sectional view similar to FIG. 2 but with longitudinal cuts in the valve means and the adjustment means in the open position as in FIG. 3.

5 is an oblique view of a variant of the valve means and the adjustment means.

FIG. 6 is an oblique view of the adjusting means for opening the box shown in FIG. 5. FIG.

* Explanation of symbols in the drawings

1: muffler 3: housing

3a: case 3b: end wall

3c: end wall 5: housing-interior

5a: interior region 5b: interior region

5c: interior region 7: partition wall

9: partition wall 11: inlet

13: inlet pipe 13a: outlet

15: axis 21: first exit

23: first outlet pipe

23a: scavenging port of the first outlet pipe

25: second outlet 27: second outlet tube

27a: extinguisher of the second outlet pipe 31: valve means

33: valve 35: adjusting means

41: box 43: box axis

44: box wall 45: box case

45a: gas passage hole

45b: gas passage hole

45c: opening (= control line connection)

47: end wall 49: end wall

49a: ring-shaped flat section

49b: collar 49c: valve seat

49d: gas passage hole 53: partition wall

53a: collar 53b: gas passage hole

55: partition wall 55a: color

57: box-interior 57a: interior area

57b: interior region 57c: interior region

59: control line 59a: end section

59b: prop 61: bush

61a: hole 65: blocking element

67: valve body = valve disk

67a: first surface 67b: second surface

69: rod 71: screw

73: damping element 75: damping member

77: adjusting body (= adjusting plate or adjusting disk)

77a: first surface 77b: second surface

79: annular gap 81: shell

83: spring 87: high pressure chamber

89: low pressure chamber

113: inlet tube 115: axis

127: second outlet pipe 127a: accessory of second outlet pipe

129: axis 131: valve means

133: valve 135: adjustment means

141: box 145: box wall

145a: front wall 145b: back wall

145c: side wall 145d: side wall

145e: opening = control line connection 145f: gas passage hole

149: projection 149c: valve seat

153: eye 155: bearing bolt

156: swivelling axis 157: inside the box

159: control line 159a: end section

159b: prop 165: blocking member

167: valve body = valve flap

167a: dog 169: hub

169a: case 169b: end wall of the hub

173: damping member

177: adjusting body = adjusting plate or adjusting flap

179: gap 183: spring

187: first chamber = high pressure chamber 189: second chamber = low pressure chamber

191: arrow 193: arrow

The present invention relates to a muffler for a flowing gas according to the preamble of claim 1, in particular a waste gas of an internal combustion engine, pulsating and flowing.

If an internal combustion engine coupled with an exhauster with a silencer has one or more cylinders each having a piston that can be pushed therein, the cylinder and the cylinder each time the piston is fully operated To each cylinder exhales exhaust gas. Thus, the pressure of the exhaust gas in the ejector fluctuates as a result of this intermittent exhaust gas supply. This fluctuation is also referred to as regular and periodic, and acoustic pressure fluctuation when the engine speed is constant. The frequency of this acoustic pressure fluctuation is proportional to the rotational speed of the engine and the number of cylinders associated with the ejector.

In addition, changes in the rotational speed and output power of the engine cause a change in the mean flow rate through one or several cycles of acoustic pressure fluctuations. This change in flow rate itself causes a change in the pressure of the exhaust gas or is associated with this pressure change. This pressure change is not periodic and is generally somewhat slower than the periodic acoustic pressure fluctuations.

The muffler is in particular provided for use as part of an exhaust for internal combustion engines of motor vehicles or, in some cases, other motor vehicles, and has a connecting passage which can be partially or completely blocked by valve means. The valve means have a valve seat and an adjustable blocking element arranged inside and / or on the side of the connecting passage. The damping characteristics of the muffler can sometimes be varied by at least partially blocking the connecting passage, so that adaptation to the flow rate of the exhaust gas is possible. By means of the valve means having or with adjusting means and at the same time being connected with the adjusting means, the blocking member is provided with a flow rate of the gas supplied to the muffler and / or a pressure difference between the pressure present at a specific position and associated with the flow rate to the pressure of the gas. Can be adjusted automatically. At this time, the pressure to pressure difference depends on the flow rate. Such a muffler with valve means operable automatically by the exhaust gas is also referred to as a semi-active muffler.

The silencer described in German utility model DE 89 08 244 U has one inlet pipe and two outlet pipes, one of which has a valve seat. The valve seat is formed by extending the outlet tube so as to extend conically from the scavenging port of the outlet tube along the direction of flow. The valve means has a corrugated pipe arranged inside the housing, and one end of the corrugated pipe is movably coupled with the blockable outlet pipe. The other end of the corrugated pipe is connected with a valve disk which functions as a blocking member for closing the valve seat by means of a pushable guided shank. The corrugated tube is closed at both ends and includes an interior. The interior is connected to the connecting passage of the inlet pipe by a control line. The corrugated tube has some elasticity and also forms a spring means. If the exhaust gas does not flow into the muffler at all, or extremely minimally, the valve disc is attracted to the corrugated pipe and the valve seat by the elasticity of the corrugated pipe and pressed onto the valve seat. As the flow rate of the exhaust gas increases, the pressure of the exhaust gas increases in the inlet pipe and the corrugated pipe. As a result, the corrugation tube is lengthened and the valve disc is separated from the conical valve seat, as well as the valve disc continues to be pushed into the extension of the outlet tube. If the exhaust gas pressure in the corrugated pipe exceeds a certain pressure limit, the connecting passage of the shutoff outlet pipe gradually opens up as the exhaust gas pressure increases and finally the valve disc reaches its end position. When the valve disc has been separated from the valve seat, the exhaust gas from the interior of the muffler flows through the outlet of the outlet pipe which is shut off to the valve disc, diverts through the valve disc and then the inner surface of the outlet pipe and the valve It flows past the ring gap between the disks. The exhaust gas then continues to flow through the outlet pipe in the longitudinal direction of the outlet pipe.

In the German utility model DE 89 08 244 U, the corrugated pipe is not described in detail. Well known corrugated tubes, however, are typically made of thin sheet steel and have a deformable case that is slightly elastic. In the case of the silencer described in German utility model DE 89 08 244 U, in particular, the corrugated pipe is severely loaded by hot corrosive exhaust gases having a temperature of up to 600 ° C and also has a disadvantage of rapid fatigue and shortened life. There is this. In addition, hard impurities, such as soot particles, may collect inside the corrugation tube and adversely affect the operation of the corrugation tube. In addition, condensation water may collect in the corrugated pipe during cold start, which may further increase corrosion. In addition, the corrugated tube allows only a relatively small hub of the valve disc.

The valve disc of the muffler described in German utility model DE 89 08 244 U is pushed away from the supporting surface of the valve seat when viewed in the general flow direction of the exhaust gas flowing through the outlet pipe. The exhaust gas thus has a large flow velocity when flowing into the outlet pipe, when diverting by the valve disc, and through the so-called ring gap. As a result, a disadvantage arises in that severe flow noise is produced when the exhaust gas flows around the valve disc. This results in worse silencing of the muffler when the flow rate is high after partially opening the disconnectable connection passage. This is especially the case when the exhaust gas pressure is only slightly above the so-called pressure limit in the corrugated pipe, and the valve disc remains in the intermediate position. In the intermediate position, the pressure created by the exhaust gas is balanced with the elasticity created by the corrugated pipe, with only a small ring gap existing between the inner surface of the outlet pipe and the valve disk. Even if the valve disc has been pushed out of the valve seat to its final position when the exhaust gas flow rate is very high, the exhaust gas must still flow around the valve disc. It should also be noted that the corrugated tube only permits a small stroke of the valve disc, as mentioned earlier, so that the valve disc cannot thus be pushed away from the valve seat. In addition, as described above, when the exhaust gas flows around the valve disk in the outlet pipe, the valve disk increases the flow resistance and increases the back pressure caused by the silencer and the discharger. .

In the case of the muffler described in German utility model DE 89 08 244 U, the force produced by the corrugated pipe changes with the periodic release of exhaust gases. Periodic changes in this force when the rotational speed is constant can cause periodic opening and closing of the valve and chattering noise. This is moreover the case because the mechanism of the control line leading into the corrugated pipe lies in the case of the inlet pipe leading the exhaust gas into the housing of the muffler. The pressure of the exhaust gas introduced into the corrugated tube by the control line is thus equal to the static pressure, so that it is less than the total pressure of the exhaust gas flowing through the inlet tube. Therefore, the pressure change caused by the change of the flow rate in particular is only relatively small. Here, too, the elasticity produced by the corrugated pipe has to be distributed smallly, and the disadvantage is that the change of the periodic force caused by the pulsation of the exhaust gas is relatively large compared to the elasticity.

Mufflers are also well known in which the inlet tube leading to the interior of the muffler or the connecting passage of the inner tube which is located completely inside the muffler and which connects the various chambers of the muffler can be partially blocked by an adjustable blocking member. In the case of the silencer described in German patent DE 195 03 322 A, a valve disc is present to block the outlet of the inlet pipe into the housing. The adjusting means of the muffler used to adjust the valve disc comprises a box, a flexible membrane arranged on the box and a spring. The flexible membrane divides the box-interior into a high pressure chamber and a low pressure chamber. The control line, which is connected to the high pressure chamber, is combined with the inlet tube or integrated into the rod from side to side above the outlet of the inlet tube and outside the muffler housing, the rod connecting the flexible membrane to the valve disc. Therefore, the high pressure chamber is dominant in the pulsating positive pressure or the pulsating total pressure. Since the low pressure chamber is combined with the ambient atmosphere, the low pressure chamber is dominated by a rather constant, especially non-pulsating atmospheric pressure for at least a short time.

The force produced by the flexible membrane and imparted on the valve disc changes severely with the cycle of exhaling the exhaust gas. The exhaust gas flowing through the inlet exerts a force on the valve disk that directly contacts the valve disk. The force at this time is also changed in accordance with the cycle of exhaling the exhaust gas, and has the same direction as the force applied by the exhaust gas to the flexible membrane. The valves of the silencer described in German patent DE 195 03 322 A therefore tend to have a greater chattering than the valves according to the German utility model DE 59 08 244 U in terms of the emission cycle of the exhaust gas.

The box of the muffler adjusting means described in German patent DE 195 03 322 A is arranged outside the original muffler housing and therefore requires additional space which is not used for the original noise. Since the flexible membrane arranged in the box cannot be made of almost metal because it must be very thin and very elastic, it is also almost impossible to arrange the box with the flexible membrane inside the housing due to the high temperature inside the housing. In addition, arranging the box outside the housing is very dangerous. Leakage may occur at the box or at the control line that connects the box to the rest of the silencer, resulting in the release of hot exhaust gases. In addition, the flexible membrane allows only a small stroke of the valve disc. In addition, gas tight arrangements of flexible membranes in boxes are complex and expensive. Furthermore, the box's high-pressure chamber can collect solid impurities such as soot particles and condensate at room temperature startup. In the case of the muffler described in German patent DE 195 03 322 A, as also mentioned earlier, since the element of the inlet pipe is blocked by the blocking member, the passage cross-section that can be used for the exhaust gas flowing out of the muffler housing will vary due to the valve. Can not. Also in the case of the silencer described in German patent DE 195 03 322 A, the blocking member used to at least partially block the connecting passage is pushed out when the exhaust gas is opened in the general flow direction flowing through the pluggable connecting passage. Therefore, in the case of the silencers according to German patent DE 195 03 322 A, when the valve is opened, the gas is vacated in the passage area since only a small passage area is emptied in numerous driving states, similar to the silencer described in German utility model DE 89 08 244 U described earlier. When flowing through them, they generate a lot of heavy noise.

German patent DE 125 837 C discloses a silencer having a housing, an inlet tube and an outlet tube. The outlet pipe has two side openings facing each other, which can be blocked by two valve discs fixed to one rod. The spring is in contact with the rod at one end of the rod. A funnel-shaped dog is fixed to the other end of the rod, which is located opposite the outlet of the inlet tube inside the housing. The force that the spring applies to the rod tends to separate the two valve discs from the side opening of the outlet tube at an angle to the outlet tube.

If the internal combustion engine is connected to the inlet tube of the muffler and intermittently supplies the exhaust gas to the inlet tube when driven, the outlet of the muffler is completely closed by the valve for a predetermined time and then reopened every time the exhaust gas is supplied. The valve thus produces chattering noise. When the valve is opened, the exhaust gas flows into the outlet tube at an angle to the outlet tube in opposite directions through both openings of the outlet tube and then severely changes in the outlet tube. This flow causes severe turbulence and noise. This turbulence and noise is exacerbated by being pushed into the interior of the outlet pipe from above the flow in relation to the general flow direction in the opening which can be closed by the valve disc when the second valve disc is opened and further disturbing the flow there.

In the case of modern engines, as usual, if the engine is provided with a plurality of cylinders, each cylinder must be provided with a separate silencer, which is very expensive.

The valve closes and reopens every time the engine emits exhaust gas, so when using modern engines, the two valve discs are more frequent and push back and forth as the speed increases. As a result, the valve is heavily loaded when driven. Due to the heavy load, the manufacture of the mufflers required for the engine or the valves provided in the respective mufflers is expensive. Likewise during operation, if the heavily loaded spring breaks, the outlet remains closed completely so that the exhaust gas can no longer flow. This can continue to cause significant damage to the engine and the exhaust.

US Pat. No. 6,427,645 B discloses a silencer whose interior is divided into a first chamber and a second chamber by a dividing wall. The first chamber is connected with a waste gas channel in the cylinder of the two-stroke engine. The second chamber has an outlet. The partition wall has three openings distributed along a circle. The three openings can be closed by one valve plate. The valve plate is guided with a deformable, corrugated guide element distributed along the circumference and connected via a rod with a flexible membrane arranged in a second chamber and contacted by a spring. The flexible membrane is fixed to the housing wall of the muffler and consists of rubber or rubber-like material.

If a large pressure in the second chamber at the time of driving is in contact with the flexible membrane, the valve plate is pressed against the valve seat formed by the surface of the dividing wall and closes the opening of the dividing wall so that no exhaust gas flows in the first chamber. You will not be able to go out. If the pressure in the second chamber drops below the threshold, the valve plate separates from the dividing wall above the flow through the force caused by the spring.

Since the valve is fully closed and reopened every two cycles of the two-stroke engine cylinders supplying exhaust gas to the muffler, the valve plate, as well as the deformable coronary guide member that guides the various parts of the valve and in particular the valve plate, The flexible membranes used to load are very heavily loaded.

This is furthermore the case because the muffler is arranged directly in the engine and the exhaust gases thus flow into the muffler at a very high temperature. Therefore, making such a silencer long enough in life is tricky and expensive. Since the openings remain closed in the dividing wall if the spring breaks during operation, similar damage can occur, especially engine damage, as in the silencer described in German patent DE 125 837 C.

In addition, the muffler disclosed in US Pat. No. 6,427,645 has a valve having a flap that can swing horizontally. The flap is adjusted by a plate cam arranged on the crankshaft of the engine and a rod sensing the plate cam.

Such a muffler has the disadvantage that in particular the previously mentioned rods must be guided through the passages from the outside into the muffler and the rods must be located outside the muffler, so that the possibility of positioning the muffler is severely limited.

In addition, the two silencers described above described in US Pat. No. 6,27,645 B are only suitable for two-stroke engines. If such an engine has multiple cylinders, a separate silencer must also be built and assembled for each cylinder. Therefore, manufacturing and assembly costs go up.

SUMMARY OF THE INVENTION An object of the present invention is to provide a muffler which has at least one partly blockable connection passageway and which can avoid the disadvantages of conventional mufflers. The muffler, in particular, starting from German patent DE 195 03 322 A, the blocking member should be able to move as little as possible by the pulsation of the exhaust gas. In addition, the adjusting means must be sufficiently durable against high temperatures and the adjusting means and in particular the movable parts of the adjusting means must be able to be arranged at least largely and mainly completely within the housing of the muffler. It should also be kept as far as possible from the collection of hard impurities and / or condensate and / or other liquids in the chamber of the adjusting means which are connected to the control line. The adjusting means should also be able to greatly adjust the blocking member of the valve. Furthermore, open the blockable passageway, and the gas flowing through the connecting passageways should make the flow noise as low as possible and the back pressure as low as possible. In addition, the valve means and the adjusting means of the muffler and in particular the muffler used to block and empty the connection passages must not only be robust and have a long service life but also be able to operate without failure. In addition, the silencer and the valve means and the adjustment means of the silencer must be economically manufacturable.

The object of the present invention is achieved by a silencer having the features of claim 1.

Preferred improvements of the muffler appear in the dependent claims.

The silencer according to the invention can be built in, for example, an exhaust for a four stroke engine having a plurality of cylinders. The inlet of the muffler according to the invention is provided in all cylinders or two or more of the engine, for example via a discharger part connected in series, such as a pipe, a converter and optionally another front muffler. Can be connected with the cylinder. However, the silencer according to the present invention can also be used in a two-stroke engine having only one cylinder. Since the muffler can also be arranged relatively far below the engine, the exhaust gas is cooler and has a lower pressure variation when flowing into the muffler than when it is already flowing out of the engine.

In particular, the present invention has the advantage that the pulsation of the exhaust gas hardly moves the blocking member, and in particular, does not cause periodic opening and closing of the valve.

In addition, the present invention has the advantage that the limit stop of the high-pressure chamber and the remaining valve means can also be made of parts that are resistant to heat as well as corrosion until the gas reaches a high temperature. These parts ensure long life and trouble-free operation of the valve means. In addition, it should be noted that the adjusting body of the adjusting body, in particular the adjusting body, in which the high-pressure chamber of the adjusting means is arranged movably by means of fixed parts, that is to say within the box wall and the box. The boundary can be formed by). Therefore, when forming the boundary of the high-pressure chamber of the adjusting means of the silencer according to the present invention, unlike the case of many conventional silencers, no deformable flexible membrane, deformable corrugated pipe, or other deformable parts are required.

Further, according to the present invention, it is possible to form a silencer to move the blocking member away from the valve seat when opening the valve. As a result, when the exhaust gas circulates around the blocking member with the valve open, it does not produce flow noise and high back pressure.

The subject matter of the present invention is described based on the embodiment shown in the drawings.

The silencer 1 shown in various driving states in FIGS. 1 and 3 is provided for use as part of an exhaust for an internal combustion engine. The muffler 1 has a housing 3 shown in simplified form, the housing being in cross section, for example an approximately circular or elliptical case 3a and two end walls 3b, 3c arranged at the end of the case. ).

The housing 3 surrounds the housing interior 5, for example one or more partition walls, ie two partition walls 7 and 9 which extend transverse to the case 3a and are fixed to the case. Include. The two partition walls allow gas to pass through at least in some places, that is, with holes formed, and divide the housing interior 5 into three interior regions 5a, 5b, 5c.

The muffler has an inlet 11 with an inlet tube 13 protruding from the end wall 3b into the housing interior 5. The inlet pipe is fixed to the end wall 3b and to the partition walls 7 and 9, for example, through two partition walls 7 and 9, and the outlet 13a leading to the inner region 5c and It has an axis 15. The muffler also has two or more outlets. In other words, a first outlet 21 having a first outlet tube 23 and a second outlet 25 having a second outlet tube 27 are provided. The two outlet pipes 23, 27 protrude from the end wall 3c into the housing interior 3 and extend, for example, through the partition walls 7, 9 to the interior region 5a. The two outlet pipes 23, 27 are also fixed to the end wall 3c and the partition walls 7, 9, for example. The first outlet pipe 23 has a small mechanism 23a which is kept open at an end located inside the housing. Since the second outlet pipe 27 has an air outlet 27a at an end located inside the housing and a valve means 31 near the air outlet, the second outlet 25 is sometimes shut off so that gas is almost never leaked. Can be.

The inlet tube 13 is connected to the internal combustion engine, usually through other exhaust parts, outside the housing 3 or near the end wall 3b of the housing. The two outlet tubes 23, 27 have, for example, a pipe section which projects outwardly from the housing 3 and leads to the surrounding atmosphere, or is connected to the surrounding atmosphere via additional pipes.

The valve means 31 has a valve 33 which can be recognized in various driving states in FIGS. 2 and 4, the valve being connected to or provided with an adjustment means 35 used for operation. The valve means 31 to valve 33 and the adjustment means 35 have a common housing, represented by a box 41 in the following. The box 41 has a box axis 43 and a fixed box wall 44. The box wall comprises a generally cylindrical and cross-sectional box case 45 surrounding the box axis 43 and two end walls 47 and 49 that are tightly coupled to the ends of the case 45, respectively. Equipped.

At the outer edge of the end wall 47 is a bending flange having a portion parallel to the box case and adjacent to the box case, one or more ring-shaped stiffening ribs and / or stiffening grooves, or the like. It is provided. The end wall 47 is, for example, small in size and has no holes. The other end wall 49 is ring-shaped, with a flat ring-shaped section 49a and a collar 49b near the inner edge of the ring-shaped section, the collar being curved outwardly away from the box and the other end wall 47 or At the same time it is curved, it is tangent-bending, adjacent to the outer surface of the second outlet pipe 27 and fixed to the second outlet pipe. Accordingly, the box 41 is firmly coupled to the second outlet pipe 27 and, for example, is not only adjacent to the partition wall 7 but also fixed to the partition wall, but may be spaced apart from the partition wall. The box is located at least partly or entirely in the housing 5.

The innermost ring-shaped region in the flat section 49a of the box 41 end wall 49 forms the valve seat 49c, which is a flat ring-shaped support surface on the side facing the box interior 57 side or It has a bearing surface. The valve seat 49c is arranged directly in and / or on the side of the passageway near the mouthpiece of the blockable passageway of the second outlet, thus forming a boundary of the mouthpiece, and the ring-shaped support surface inner edge of the valve seat surrounds the mouthpiece. do. The outer ring-shaped region of the flat section 49a of the end wall 49 surrounding the valve seat has, for example, a plurality of gas passage holes 49d distributed along the circumference, the gas passage holes being a box. It leads to the inner region 57c. The box axis 43 also naturally forms the axis of the valve seat 49c and at least approximately coincides with the axis of the straight end section of the second outlet pipe 27 that is connected to the box. It should be noted here that, in the manufacture of the silencer, the entire box with the valve seat is made, and then the box is connected with the outlet pipe 27 together with the valve seat and installed in the silencer, so that the box shaft is Is exactly coincident with the axis. On the other hand, the axis of the outlet tube may be slightly inclined or inclined toward the box axis and change position at the same time due to manufacturing inaccuracies in some cases.

The box 41 includes two partition walls 53 and 55. Each partition wall has a flat disk perpendicular to the box axis 43 and has collars 53a to 55a at the edges. The collar projects from the disk to the side opposite the valve seat, is adjacent to the inner surface of the box case 45 and fixed to the box case. At this time, the partition wall 55 located at least close to the valve seat 49c is coupled to the box case at least to some extent or completely so that the gas does not leak. The partition wall 53 further away from the valve seat 49c has a cap of the gas passage hole 53b, thus allowing gas to pass therethrough. The box 41 surrounds the box interior 57, which is divided by three partition walls 53, 55 into three interior regions 57a, 57b, 57c. The inner region 57a and the middle inner region 57b furthest from the valve seat are interconnected by the gas passage hole 53b, while the inner region adjacent to the middle inner region 57b and the valve seat 49c. The 57c are separated from each other so that at least some gas does not leak.

The box case 45 has a ring-shaped area near each of the two ends, and the ring-shaped area has a plurality of gas passage holes 45a to 45b distributed along the circumference. The gas passage hole 45a leads to the inner region 57a, while the gas passage hole 45b communicates to the inner region 57c of the box. The box case also has an opening 45c arranged between the gas passage holes 45a and 45b near the circumference, the opening being an intermediate inner region 57b existing between the two partition walls 53 and 55. Through. The opening 45c functions as a control line connection, and is hermetically coupled to the gas and the control line 59 made of a curved tube near the end of the control line connection. The control line 59 protrudes through the hole in the case of the inlet tube 13 into the connecting passage bordering the inlet tube and leaks at least some degree of gas from the inlet tube near the hole in the case of the inlet tube. And a curved section positioned in the inlet tube with a straight end section 59a which is not only airtight but also substantially coaxial with respect to axis 15, but which is airtightly coupled. The subassembly 59b having an end section is located in a plane at least approximately perpendicular to the axis 15 of the inlet tube, approximately concentric with the inlet tube, and towards the inlet tube region located above the control line. The outer diameter of the control line 59 is certainly smaller than the inner diameter of the inlet tube 13. Thus, there is an empty ring-shaped area of the connecting passage which surrounds the end section 59a without interruption between the inner surface of the inlet tube 13 and the straight end section 59a of the control line parallel to the axis 15. The cross section of the control line connecting passage is much smaller than that of the inlet connecting passage, and generally amounts to 50%, to 5%, for example approximately 15% to 35% of the cross section of the inlet connecting passage.

The main mechanism 59b of the control line 59 is naturally located above the inlet pipe 13 in the inlet pipe 13 and spaced apart from the outlet at a distance of at least one times the inner diameter of the inlet pipe 13. And mainly at least three times.

In the middle inner region 57b of the box 41, a bush 61 coaxial with respect to the box axis 43 is arranged so as not to move. The bush protrudes into the central holes of the two partition walls 53 and 55 and is fixed to the partition wall so that at least some gas does not leak. The bush is an uninterrupted hole 61a that is coaxial with respect to the box axis.

The valve 33 is adjustable to intercept the connecting passage of the valve seat 49c and the second outlet pipe 27 from time to time at least approximately not leaking, that is to say movable in parallel to the box axis 43. The blocking member 65 is provided. The blocking member 65 has a valve body 67, ie a plate-shaped valve disc 67. The valve body is usually made of a flat, round and shaped metal plate or disc, having a hole in the center, and is fixed to the rod 69 by screws 71 through the plate. The rod 69 penetrates through the hole 61a of the bush 61 and is guided to the bush so as to be movable with some clearance. The valve disc has a ring damping element 73 near the outer edge of the side facing towards the valve seat 49c and on the valve seat with the damping member in the shut off position of the valve shown in FIGS. 1 and 2. Is placed on. The valve disc has a ring-shaped damping member 75 on the side opposite the valve seat, the damping member surrounding the end of the rod 69 and the partition wall 66 in the opening position of the valve shown in FIGS. 3 and 4. ) And / or bush 61. The damping member 75, together with the partition wall 55 and / or bush 61, forms a sling that determines the open position of the valve disc. The two damping members 73, 75 are, for example, slightly deformable, for example a fleece formed of wire pieces, for example one or more wire mesh layers n or wire pieces. And the like and secured to the disk of the valve disc via, for example, a number of point-formed welded joints.

The valve body or valve disc 67 has a first surface 67a on the side opposite the valve seat and a second surface 67b on the valve seat side. The flat support surface outer diameter of the valve seat 49c and the outer diameter of the valve disc 67 are certainly smaller than the inner diameter of the box case 45 and reach up to 90% of the inner diameter of the box case, for example, approximately 70% to 80%. . Thus, at any position between the circumferential edge of the valve disc and the box disc, there is a ring-shaped, fairly wide hollow area inside the box. The cross section of the gas passage holes 49b and 49c of the box case 45 and the cross section of the end wall 49 of the box 41 are much larger than the cross section of the passage of the second outlet pipe 27.

The adjusting means 35 has an adjusting organ which is fixed in shape so as to be able to slide along the box axis in the box 41. The regulating body has as its main components an adjusting body 77 which is fixed in shape, ie a circular and at least usually flat metallic adjusting plate or adjusting disk 77. The adjusting body 77 is arranged to be slidable in the inner region 57a of the box 41, has a hole in the center, and a rod 69 end section projecting into the inner region 57a near the hole. Is fixed to. The adjusting body 77 has a first surface 77a on the side of the valve seat and a second surface 77b on the side opposite the valve seat. Since the outer diameter of the adjusting body 77 is slightly smaller than the inner diameter of the box case 45, and is generally 0.5 mm to 3 mm, for example, about 1 mm to 2 mm, an empty ring gap (the gas passing between the box case and the adjusting body) ring gap; 79). The ring gap completely surrounds the adjusting body without interruption, and the width of the ring gap reaches at least approximately 0.25 mm to 1.5 mm, such as about 0.5 mm to 1 mm, to meet the desired diameter difference. The cross section of the ring gap 79 is primarily smaller than the passage cross section of the control line 59 and amounts to 60%, even smaller, of 50% of the maximum control line passage cross section. The inner diameter of the box case 45 and the diameter of the adjusting body 77 may also be at most 15%, at least 1%, throughout the cross section of the area inside the box 57 where the passage surface of the ring gap 79 mainly comprises the adjusting body, For example, approximately 3% to 10%.

A shell 81 is fixed on the side opposite the valve seat of the adjustment disk. The shell is at least mostly cylindrical as well as circular in cross section, with the end opposite the adjusting disk open. The outer diameter of the cylindrical main part of the shell is certainly smaller than the inner diameter of the box case 45 and amounts to 70%, at least 30%, for example, approximately 45% to 55% of the maximum box case inner diameter. The adjusting means also has a spring means comprising a spring 83 formed by a pressure screw spring. One end of the spring 83 is adjacent to the end wall 47 of the box 41 and the center is determined by the rise of the end wall 47 protruding toward the inside of the box. The other end of the spring 83 is in contact with the adjusting body 77. The spring, for example, protrudes into the shell 81 and has an outer diameter slightly smaller than the inner diameter of the shell 81. Instead the spring also has a slightly larger diameter than the shell and can enclose the shell.

The plate- or disc-shaped adjusting body 77 has two inner box areas 57a including the adjusting body and a box inner area 57b connected to the inner area 57a through the gas passage hole 53b. It is divided into chambers. The two chambers are hereinafter referred to as the first chamber 87 or the high pressure chamber 87 and the second chamber 89 or the low pressure chamber 89. The high pressure chamber 87 is a partial region of the inner region 57b and the inner region 57a which is connected to the inner region 57b by the gas passage hole 53b and located on the valve seat side of the adjusting body 77. Is formed by. Therefore, the high pressure chamber 87 is connected to the inlet pipe 13 by the control line 59. The low pressure chamber 89 is located between the end wall 47 and the adjusting body 77, and includes a box 41 as well as a silencer surrounding the box by the gas passage hole 45a of the box case 45. It is connected with the inner region 5a.

The parts of the silencer described above all consist of a temperature resistant metal material which is at least 600 ° C. and for example up to at least 700 ° C., or at least 800 ° C. The spring 83 is made of a nickel base alloy, for example well known as Inconel. The remaining part is made of steel, for example. The metal parts of the silencers which are tightly coupled to each other are, for example, welded together.

In the following, a number of characteristics are described which are associated with the driving and driving of the muffler 1. The internal combustion engine connected to the muffler supplies hot gas, ie exhaust gas, which flows pulsating into the muffler when driven. At this time, the flow rate and pressure of the exhaust gas are changeable, and usually increase with the increase of the rotation speed and the power of the engine. The noise caused by the ejector and the flowing exhaust gas passing through the silencer belonging to the ejector is caused by the pulsation of the exhaust gas flow, especially at relatively low rotational speeds and at low flow rates. As the rotational speed increases and the flow rate increases, the flow noise generated by the exhaust gas in the passage of the passage becomes important and dominant.

When the internal combustion engine is stopped and after supplying the exhaust gas only to a small flow rate to the muffler after start, the valve body or the valve disc 67 of the valve 33 is located in the shut-off position so that the second outlet ( Since the passage of 25 is blocked so that the gas hardly leaks, the discharge gas can actually flow out of the housing interior 5 only through the first outlet 21. The result is particularly good attenuation of noise caused by pulsations of the exhaust gas flow.

If the flow rate of the exhaust gas supplied to the muffler is not only increased but also exceeds a certain opening limit, the valve body or valve disc 67 of the valve is automatically moved to the open position by the adjusting means 35 and the second outlet 24 is provided. By emptying the passage of), the exhaust gas can flow out from inside the housing through the two outlets 21, 25. This results in less flow noise and lower back pressure than when only the first outlet is open. If the flow rate of the exhaust gas supplied to the muffler falls below the cutoff limit, the valve disc is moved back to the cutoff position. 1 and 3, a plurality of gas flows generated in the blocked to open positions are indicated by arrows.

After this drive has been described in general, many details of valve operation will now be described in more detail. It should be noted first that the exhaust gas flows through the passage of the second outlet 25 in the general flow direction in the case of a valve which is at least partially or fully open. This general flow direction is parallel to the axis of the cavity of the box, valve seat and passage section following the valve seat in the valve seat 49c and passage section following the valve seat. The flat support surface of the valve seat is thus directed towards the space region located above the valve seat in relation to the general flow direction. This spatial region, which faces the support surface of the valve seat and borders the support surface, is of course formed by the inner region 57c of the box, which is surrounded by and bounds the box through the gas passage hole 45b. It is connected to the inner region 5a and, for example, to the inner region 5b of the housing interior 5 via the gas passage hole 49d and the wall 7 through which the gas passes.

The spring 83 is subjected to an initial prestress, and in any driving state, i.e. when the engine is stopped and in operation, and at any position of the valve body or valve disc 67, the regulating body 77, That is, elasticity is applied to the adjusting plate or the adjusting disk. This elasticity is transmitted to the valve body or the valve disk 67 by the rod 69, and presses the valve body or the valve disk toward the valve seat 49c.

When the internal combustion engine supplies the exhaust gas to the muffler, the exhaust gas further applies a force to the regulating body 77 in the manner described in more detail, from the regulating body via the rod 69 to the valve body or valve disc 67. In addition to, it can also be applied directly to the valve disk.

If the blocking member 65 is in the blocking position shown in FIGS. 1 and 2, the exhaust gas flowing into the inner region 57c of the box 41 is at a pressure aimed at the valve seat and borders the inner region 57c. Application on the first surface 67a of the valve disc 67. The second outlet pipe 27 comprises gas, ie air and / or exhaust gas, the gas having an atmospheric pressure and applying pressure to the region of the second surface 67b of the valve disc. At this time, the valve disc is located in the support surface of the valve seat 49c, that is, borders with the passage area located above the valve seat without being mounted on the support surface, the passage being the second outlet pipe 27 and the collar ( Surrounded by 49b). The gas pressure in the blocking position of the inner region 57c is greater than in the second outlet tube 27, and the exhaust gas present in the inner region 57c is larger than the gas having atmospheric pressure in the second outlet tube. As it reaches the surface of the valve disk, the gas reaching the valve disk applies a force on the valve disk that is generally aimed at the valve seat. This force, which the gas directly applies on the valve disc, is expressed below as retention force and added to the elasticity in the same direction.

Most of the exhaust gas supplied to the inlet 11, ie, the largest part, when the internal combustion engine is driven flows through the outlet 13a of the inlet pipe 13 into the empty area of the housing interior 5. However, the exhaust gas also flows from the inlet pipe 13 through the control line 59 into the high pressure chamber 87 of the box 41 and then through the ring gap 79 into the low pressure chamber 89 of the box, It exits the box through the gas passage hole 45a and flows into the silencer inner region 5a surrounding the box. At this time, a pressure difference is generated on the ring gap 79. In this case the end section 59a of the control line arranged inside the inlet tube 13 acts as a pressure probe, similar to the Potot tube, and is located near the element 59b of the control line. The total pressure of the exhaust gas flowing through the inlet pipe, i.e. the total of static and dynamic pressure, is detected. This pressure of the exhaust gas is transferred into the first chamber to the high pressure chamber 87 of the box 41. The discharge gas in the high pressure chamber 87 has a higher pressure than the discharge gas in the low pressure chamber 89, and the magnitude of the pressure in the low pressure chamber is approximately the same as in the inner region 5a of the housing. The plate- or disc-shaped adjustment body 77 functions as a compression force sensor for the exhaust gas flowing through the box. Exhaust gas applies forces opposing each other in the two chambers 87 and 89 to the two surfaces 77a and 77b of the regulating body 77, which in turn are directed away from the valve seat and oppose the elasticity. It is a force. The force exerted by the exhaust gas to the adjusting disk is shown below as an opening force.

Here are a number of explanations for the change in pressure of the exhaust gas.

As the silencer 1 is mentioned at the outset, it is mainly connected to two or more engine cylinders and arranged relatively far from the engine upstream exhaust, so that the periodic acoustic pressure caused by the engine's intermittent exhaust gas supply and the rotation speed is constant The fluctuation is already somewhat balanced and smoothed when the exhaust gas flows into the control line 59.

The cross section of the box interior 57 and in particular the region of the high pressure chamber 87 adjacent the control body 77 is much larger than the passage cross section of the control line. The result is a further balance of pressure fluctuations caused by intermittent exhaust gas supply. The pulsation of the exhaust gas also causes pressure fluctuations that are approximately synchronous and approximately the same size on both sides of the adjusting body. The forces exerted on both sides of the adjusting body by this acoustic pressure fluctuation are thus at least inclusively supplemented with each other. Since the pressure probe of the total pressure of the exhaust gas formed by the control line 59 is detected at the inlet near the element of the control line, the pressure difference between the high pressure chamber 87 and the low pressure chamber 89 depending on the average flow rate Is relatively large. As a result, the spring 83 can be assigned to cause a relatively large elasticity. For this reason the adjustment means thus move the valve shutoff member 65 of the valve only in accordance with the pressure associated with the nearly average flow rate. The valve, on the other hand, does not open and close, or at least not actually open and close, through the acoustic pressure fluctuations caused by the intermittent exhaust gas supply.

If the internal combustion engine supplies the exhaust gas to the silencer only at a small flow rate after starting, and the opening force applied by the exhaust gas to the regulating body is less than the combined elastic and support forces, the valve disc remains in the shut off position. Increasing the flow rate also increases the opening force exerted on the adjusting body and when the opening limit is reached, the opening force is equal to the combined elastic and support forces. When the flow rate increases above the opening limit, the opening force exerted by the exhaust gas on the adjusting body pushes the adjusting body 77 and pushes the valve disk 67 connected with the adjusting body away from the valve seat 49c. At this time, displacement of the valve disc occurs in the connecting passage of the second outlet 25 in a manner that is contrary to the general flow direction of the exhaust gas generated after the valve disc is separated from the valve seat. As soon as the valve disc is slightly off the valve seat, the exhaust gas not only flows from the interior of the housing 5 through the interior area 57c of the interior of the box 57 into the passage of the second outlet pipe, but also through the passage and then into the surrounding atmosphere. Flows inward. In this case the gas pressure inside the housing is lowered, in particular the gas pressure, which comes in contact with the first surface 67a of the valve disc 67, is lowered. Furthermore, in particular, the holding force that the gas applies to the valve disc is at least approximately zero. On the other hand, the difference between the pressures reaching the two surfaces 77a and 77b of the regulating body and the opening force to the regulating body differ only slightly when the valve is opened. The force towards the valve seat, which is made up of a total of elasticity and bearing force, thus decreases almost suddenly when the valve disc falls from the valve seat, which is certainly less than the opening force. Although the flow rate slightly exceeds the opening limit, the valve disc is therefore pushed relatively far from the valve seat and already secured by the sling when it slightly exceeds the opening limit and immediately reaches the open position shown in FIGS. 3 and 4.

If the valve is in the open position, the exhaust gas can no longer apply force to the valve disc. When the flow rate of the exhaust gas decreases, the valve remains open, so that the opening force exerted by the exhaust gas on the adjusting body becomes smaller than the elastic force applied by the spring to the adjusting body in the open position. If the flow rate goes further down, the spring pushes the adjusting body and the valve disc toward the valve seat. When the flow rate of the exhaust gas supplied to the muffler drops to the cutoff limit, the valve disc again reaches the coating on the valve seat and shuts off the second outlet pipe. The gas then again applies a bearing force to the valve disk, which further forces the valve disk to be elastic with respect to the valve seat. The cutoff limit of the flow rate is slightly different from the open limit. In other words, the cutoff limit of the flow rate is slightly less than the open limit. In order for the valve disc to push from the open position shown in FIGS. 3 and 4 to the shut off position shown in FIGS. 1 and 2, the change in flow rate and exhaust gas pressure must be slightly larger than the valve disc being pushed in reverse. However, in the case of the valve seat, the exhaust gas flowing into the second outlet pipe 27 has a general flow direction at the beginning of the valve seat and the second pipe, and the general flow direction is the same as the displacement when the valve disc is pushed to the blocking position. In addition, only a relatively small change in flow rate and exhaust gas pressure is required to push the valve disc from the open position to the shut off position. In addition, the reduction of the flow rate often occurs in the braking process of the motor vehicle. At this time, the valve disc is likewise immediately moved from the open position to the shut off position.

Thus, the valve is usually fully closed or fully open. If the valve is at least partially open and in particular the valve disc is in the open position shown in FIGS. 3 and 4, the exhaust gas is passed through the gas passage holes 45b and 49d from the area inside the housing 9 surrounding the box 41. And through the partition wall 7 through which the gas passes, into the interior region 57c of the box, and then through the valve disc 67 without actually restraining near the valve seat, the passage of the second outlet pipe 27. It can flow inside. The flow of gas therefore does not cause any severe flow noise even when passing through the valve seat. Clearly to mention, according to the above description, not only the holding force applied by the gas directly to the valve disc but also the opening force applied by the gas to the adjusting body also helps to adjust the valve disc, so that the valve disc itself is It also works as a part.

The ring gap 79 existing between the box case 45 and the adjusting body 77 is wider than the radial clearance of the rod 69 in the bush 61, so that the adjusting body is not compressed at all even at high temperatures. Guarantee the point. Damping members 73 and 75 prevent the valve disc from causing chattering due to vibration of the muffler in the closed or open position. The damping member 73 also acts as a predetermined sealing at the shut off position of the valve disc. It has already been mentioned that the bush 69 leading the rod 69 with a gap may likewise comprise at least one ring-shaped damping member of wire mesh or wire fleece or the like. The box and spring are also arranged such that the valve disc is pushed at relatively large intervals when the valve is driven. The spacing mainly leads to at least 25% and for example at least 50% of the diameter inside of the second outlet pipe 27.

Gas flowing into the low pressure chamber 89 through the ring gap 79 may cause audible gas oscillation in some cases. The shell 81 divides the interior of the hollow of the low pressure chamber, prevents gas vibrations from occurring, and in some cases pushes the frequency of the vibrations further caused to an inaudible upper region. The valve is also sturdy and heat resistant to high temperatures, as well as low cost and can be mounted in a silencer.

The exhaust gas may transport soot particles and / or other solids and / or liquid impurities into the box 41 as much as possible when using a muffler. In particular, there is also the possibility of condensate being generated and reaching the box during cold start. As already explained, when driven, the exhaust gas flows from the high pressure chamber 87 of the box through the ring gap 79 into the low pressure chamber 89 of the box and out of the low pressure chamber. This exhaust gas flowing through the box blows solid and liquid impurities reaching the box back out of the box, thereby contributing to the prevention of failure.

Another silencer, which shows the schematic parts in FIGS. 5 and 6, has an inlet tube 113 and two outlet tubes, including an axis 115, which is only schematically indicated by dotted lines, of which two of the outlet tubes are shown. Only the second outlet pipe 127 is shown. This outlet tube has, for example, a circular element 127a, which element lies in a plane perpendicular to the axis 129 of the outlet tube 127. The two tubes 113, 127 and the first outlet tube (not shown) may be arranged somewhat similarly to the corresponding tubes of the muffler 1 shown in FIGS. 1 to 4, for example.

The valve means 131 shown in FIGS. 5 and 6 replaces the valve means 31 shown in FIGS. 1 to 4 and includes a valve 133. The valve means 131 has or is provided with an adjusting means 135 and is connected with the adjusting means. The adjusting means 135 comprises a box 141 having a metal box wall 145. The box wall includes a front wall 145a, a back wall 145b opposite the front wall, two side walls 145c facing each other (one of which is not shown in FIG. 6), and It has a front wall 145d. Walls 145a, 145c, 145d are usually flat, while back wall 145b is curved. The front wall 145a has a circular opening 145e that functions as a control line connection. The box 141 usually has an open side opposite the front wall 145d and has an opening therein which forms a gas passage hole 145f, which is divided into two parts through the outlet pipe 127. The projection 149 fixed to the box wall projects away from the box onto the box side opposite the front wall 145d and usually has a flat plate-shaped main portion. The main part is parallel to the front wall and lies approximately in the same plane as the front wall. The outlet tube end forming the sub-portion 127a of the second outlet tube protrudes into the opening of the projection 149, and the opening of the projection is partially projected by a collar that projects away from the projection onto the invisible projection side. The boundary is determined. The outlet pipe 127 is firmly coupled with the box wall 145 and the projection 149. In other words, the back wall 145b and the projection 149 are welded to the box wall. The axis 129 of the outlet tube 127 approximately or exactly coincides with the axis defined through the opening of the projection 149. The area of projection surrounding this opening serves as valve seat 149c. The valve seat has a flat seat surface perpendicular to the axis of the projection opening on the side opposite the collar. The box wall has two eyes 153 near where it is connected to the projection 149, or is firmly coupled to the two eyes. The eye has an end section to which a bearing bolt 155 is fixed, the bearing bolt restricting a swivelling axis 156. Box 141 includes box interior 157. The pivot shaft 156 is located approximately in the plane between the valve seat 149c and the opening 145e defined by the valve seat 149 at approximately the edge inside the box and / or slightly outside the box interior. The pivot axis is also parallel to the flat seat surface of the valve seat 149c and perpendicular to the opening of the projection 149 but offset relative to the axis of the projection opening.

The control line 159 is firmly and hermetically coupled to the box front wall near the opening 145e of the box front wall 145a, ie an welded end, and an inlet pipe 113 and positioned at the inlet pipe 113. It has an end section 159a that is approximately coaxial with respect to the axis 115 and has an element 159b. The apparatus may be similar in arrangement and size as in the control line 59 shown in FIGS. 1 and 3.

The valve 133 has an adjustable shutoff member 165 having a plate-shaped valve body 167 formed from a valve flap, which valve flap is likewise denoted 167 and pivot shaft 156 below. I can turn around. The valve flap has a circular main section. The circular main section is rigidly engaged with a hub 169, which is mounted by a bearing bolt 155 and can pivot around the bearing bolt by means of a dog 167a. The hub is hollow and has a cylindrical case 169a and two end walls 169b. The valve body to the valve flap 167 is mostly made of a fixed metal plate, and a ring-shaped damping member, that is, a slightly deformable damping member 173, is fixed to the valve seat 149c side of the plate. The damping member is formed of wire pieces, for example similar to the damping members 73 and 75 described above, and lies on the valve seat near the closed valve.

The adjusting means 135 has an adjusting engine fixed in shape. The adjusting engine has a fixed body 177 which is fixed in shape as a main component. The adjusting body consists of a generally rectangular and flat plate and is fixed to the case 169a of the hub 169 at one of the edges, i.e. not only welded, but also can pivot around the pivot axis 156, hereinafter the adjusting plate. Or as an adjustment flap 177. The adjustment flap is at least usually located inside the box 157. An empty gap through which gas passes between the edges of the adjustment flap towards the two sidewalls 145c of the box and the rear wall 145b that is coaxially curved with respect to the pivot axis 156; 179) exists. The gap 179 extends along the three edges of the rectangular adjustment flap and is therefore rectangular and approximately U-shaped or C-shaped.

The edge of the adjusting flap 177 towards the hub 169 is welded to the case of the hub only through a portion of its length, for example, only in two fixing sections spaced apart from one another, for example. There may then be a gap between the aforementioned edges of the adjusting flap and the remaining, unwelded sections of the hub, in which case a gaseous narrow gap as well. There is also a gap between the pivotable hub and the edge of the hub side front wall 145a.

Portions of the gap 179 extending along the three edges of the adjustment flap may be similar in width to the gap 79 of the adjustment means shown in FIGS. The gap 79 may also have a surface similar to that presented for the ring gap 79 when compared to the cross section of the box interior 157, optionally with a gap between the hub and hub side adjustment flap edges. At this time, the cross section of the inside of the box 157 is measured at a cutting plane that is radial to the pivot axis.

The hollow hub includes a spring 183, that is, a threaded torsion spring that surrounds the bearing bolt 155. One end of the invisible spring 183 is bent inward and protrudes into the hole of the bearing bolt 155, thereby being incapable of pivoting with the bearing bolt and the box wall. The other end of the spring 183 shown in FIGS. 5 and 6 is curved outwardly and protrudes through the hole of the cylindrical casing 169a of the hub, thus contacting the hub 169 and closing the valve flap. Torque, which tends to squeeze towards valve seat 149, is applied to the hub.

The adjusting body 167 to the adjusting flap 167 divides the inside of the box including the adjusting body to the adjusting flap into a first chamber 187 or a high pressure chamber 187 and a second chamber 189 or a low pressure chamber 189. do. The high pressure chamber 187 is adjacent to the opening 145e through which the control line 159 passes into the box. The low pressure chamber 189 is connected to the silencer inner region surrounding the box through the gas passage hole 145f of the box 41.

If the internal combustion engine supplies the exhaust gas to the inlet tube 113 in the manner indicated by the arrows in FIGS. 5 and 6, a portion of this exhaust gas flows into the high pressure chamber 187 of the box via the control line 159, The gap 179 and, optionally, between the hub 169 and the hub side adjustment flap edge, flows into the low pressure chamber of the box. This exhaust gas then flows out of the box through the gas passage hole 145f of the box and enters the remaining interior area of the silencer adjacent to the box. When the exhaust gas is supplied, a pressure difference occurs over the adjusting flap. This pressure difference applies a force to the adjusting flap. This force and the torque resulting from it pivot the valve flap away from the valve seat.

If no exhaust gas is supplied to the inlet tube 159 or only a very small amount, the valve flap of the blocking member 165 rests on the valve seat 149c and at least approximately hermetically closes the second outlet tube. do. If the flow rate and pressure of the exhaust gas supplied is greater and the force that gas applies to the adjusting flap exceeds the opening limit, the adjusting flap 177 is pre-turned in the direction shown by arrow 191 in FIG. 6. This causes the valve flap to pivot in the direction indicated by arrow 193 and separate from the valve seat. As a result, the valve opens, so that the exhaust gas can flow out of the muffler through the second outlet pipe 127. The regulating flap and the valve flap can pivot when the valve is opened, for example, until the regulating flap 177 appears in the second outlet tube 127, so that the second outlet tube also functions as a limit stop.

As described above, the silencer with the valve means 131 shown in FIGS. 5 and 6 can be formed and operated similarly to the silencer 1 with the valve means 31 described with reference to FIGS. Can be.

The two silencers and the valves of the silencer described above can be changed in many respects. For example, the features of the two valve means and the adjustment means shown in FIGS. 1 to 6 can be combined with one another in a slightly modified manner if necessary in various ways. Thus, for example, the gas passage hole 45a may be replaced by a unique large hole, or the gas passage hole 145f may be replaced by a plurality of holes.

In addition, only two or more partition walls 7 and 8 or only one partition wall may be arranged inside the housing, or no partition wall may be arranged at all. In addition, the valve seat may be directly formed in the second outlet pipes 27 to 127, and may be formed of a body, which is one component together with the second outlet pipe. In such cases, consideration should be given to the manufacture so that the axis of the pipe or pipe part forming the valve seat has exactly the desired position and orientation in relation to the box and the adjustable barrier member. The valve seat may also have a conical support surface instead of a flat support surface. The conical support surface is tapered upward in relation to the general flow direction of the exhaust gas, and towards the space region located above the valve seat as the support surface of the valve shown in FIGS. 1 to 6.

The partition wall 55 or 53 of the box 41 may also be formed as an end wall of the box, the valve seat is formed and / or fixed to the second outlet pipe, and the box is provided by means of fastening means through which gas passes. It may be fixed to the second outlet pipe and / or the valve seat. Such fastening means may have a number of supports, for example, distributed around the box axis and the valve seat, with gas passage holes between the supports. The box is then spaced from the valve seat so that the support surface of the valve seat is directly adjacent to the empty interior area inside the housing. The box may optionally protrude slightly from the housing at the end opposite the valve seat. The adjusting body 77 may consist of an axially thick piston instead of a relatively thin plate or disc.

In some cases it may be provided with at least one further outlet which is continuously open and / or at least one further outlet which can be blocked by the valve, in addition to the outlet which is still open and the outlet which can be shut off by the valve.

The plate in which the valve body and / or the adjustment body are fixed may be made of ceramic instead of metallic material.

There may also be connecting tubes and / or inner tubes which are arranged completely inside the housing, which connects the various inner regions of the muffler with one another. It is also possible to arrange the valves in place of, or in addition to, the valves used to block the outlet, to block the internal passages connecting the various interior regions of the muffler housings to one another, in other words the openings of the passages.

The silencer according to the invention is provided with at least one connectable passageway at least partially and can avoid the disadvantages of conventional silencers.

Claims (14)

Has a housing (3) surrounding the housing interior (5), one or more passages for directing gas and valve means (31, 131), The valve means may include valve seats 49c and 149c arranged in and / or in the passageway and / or in the side to side of one or more of the passageways and adjusting means 35 and 135. Blocking elements 65 and 165 which are adjustable in position and located on a supporting surface of the valve seats 49c and 149c in a blocking position and which at least partially block the passage. And The adjusting means (35, 135) is a box (41), 141, having a box wall (44, 145) and a box interior (57, 157) surrounded by the box wall, the box interior And coupled with the blocking members 65, 165 and the inside of the box 57, 157 to a high pressure chamber 87, 187 and a low pressure chamber 89, 189. With adjusting bodies 77 and 177 and spring means for creating elasticity, The elasticity causes the blocking members 65 and 165 to move toward the valve seats 49c and 149c, whereby control lines 59 and 159 are present to direct gas into the high pressure chamber 87. 187, a flowing gas, in particular a pulsation and flowing internal combustion engine, which applies a force opposite the elasticity to the regulating bodies 77, 177. In the muffler for exhaust gas of There is a gap (gap, 79, 179) through which gas passes between the box wall (44, 145) and the adjusting body (77, 177), the gap being the high pressure chamber (87, 187) the low pressure chamber (89, 189), the low pressure chamber (89, 189) is connected to the inner region (5a) of the housing interior (5) Silencer characterized in that. The method of claim 1, The passage and the valve means 31, 131 are formed such that gas is guided past the passage in a general flow direction when driven and when the passage is emptied, and the blocking members 65, 164 are configured to empty the passage. A muffler which is movable upstream in the general flow direction away from the valve seat (49c, 149c). The method according to claim 1 or 2, The muffler has two or more outlets 21, 23, each outlet 21, 23 having a passageway leading out of the housing interior 5 to at least one of these passages. One is still open, and at least one of these passageways forms a corresponding passageway or one passageway at least partially blocked by the valve means (31, 131). The method according to any one of claims 1 to 3, The muffler has an outlet 13a leading into the housing interior 5, the control lines 59, 159 having scavenging ports 39b, 159b, the apparatus being inlet Located in the passageway of the inlet pipe above the outlets 13a, 113a of the pipes 13, 113, and towards the area of the inlet pipes 13, 113 located above the apparatus, the inlet pipe ( Muffler, characterized in that it has a surface which is measured at an angle with respect to 13, 113, said surface being smaller than the cross section of said inlet tube (13, 113) passageway. The method according to any one of claims 1 to 4, The boxes 44 and 141 are arranged at least partially or entirely in the housing interior 5, and the inner region 5a of the silencer interior 5, which is connected to the low pressure chambers 89 and 189. A silencer adjacent to the box walls 45 and 145 and connected to the low pressure chambers 89 and 189 via one or more gas passage holes 45e and 145f present in the box wall. . The method according to any one of claims 1 to 5, The box walls 45 and 145 have an inner surface, the adjusting bodies 77 and 177 are fixed in shape and have an edge on the inner surface of the box walls 44 and 145. And the gap (79, 179) extends uninterrupted along the entire edge of the adjusting body (77, 177) on the inner surface side of the box wall (44, 145). The method according to any one of claims 1 to 6, The box 41 has an axis 43 and a box case 45 surrounding the axis, the blocking member 65 and the adjusting body 77 are firmly coupled to each other and the box 41 And a ring gap 79 through which the gas passes, not only completely surrounding the adjusting body 77 but also without interruption. The method of claim 7, wherein One or more sections of the box case 45 surrounding the adjusting body 77 are cylindrical in cross section and protrude into the low pressure chamber 89 and at least a portion of the cylindrical shell in a circular cross section. ) 81 has an outer diameter and is fixed to the adjusting body 77, wherein the outer diameter is 70% to 30% of the inner diameter of the section of the box case 42 surrounding the adjusting body 77 and the shell 81. Silencer characterized by the. The method according to claim 7 or 8, The box 41 is rigidly coupled or coupled with the valve seat 49c and simultaneously forms the valve seat, and the box case 45 has a case section having the gas passage holes 45b. silencer, characterized in that the case section surrounds an inner region (57c) of the box (41), in which a valve disk (67) can be pushed out. The method according to any one of claims 1 to 6, The silencer characterized in that the blocking member (165) and the adjusting body (177) are firmly coupled to each other and can pivot around a swivelling axis (156) of the cavity. The method of claim 10, The silencer (156) is arranged approximately at the edge of the inside of the box (145) and / or outside of the inside of the box. The method according to any one of claims 1 to 11, The blocking members 65 and 165 have a plate fixed in shape and damping elements 73 and 173 fixed to the plate, and the blocking members 65 and 165 together with the damping member. Silencer is positioned in the blocking position on the valve seat (49c, 149c) and the damping member (73, 173) is formed mainly of wire pieces. The method according to any one of claims 1 to 12, The support surfaces of the valve seats 49c and 149c are not only flat, but are arranged perpendicularly to the axes 43 and 129 defined by the blockable passageway, and are arranged in the vicinity of the opening of the blockable passageway. Silencer, characterized in that surrounding. The method according to any one of claims 1 to 13, The valve means 31, 131 have a sling, which sling restricts the movement of the blocking members 65, 165 facing away from the valve seats 149c, 49c and opens for the blocking member. Silencer characterized by defining an opening position.

Images