FR2619857A1 - INTERNAL COMBUSTION ENGINE GROUP - Google Patents

Abstract

The invention relates to an internal combustion engine unit with reciprocating pistons, equipped with a turbocharger supplied by the exhaust gases of the engine and with a power turbine. In order to be able to adapt the power of the turbine of the turbocharger to the existing power requirements of the working machine, without influencing the operation of the internal combustion engine, the exhaust gas bypass duct 8 is divided into a secondary duct 16 and into a supply duct 13 leading to the power turbine 15; there is provided in the secondary duct 16 and in the supply duct 13 respectively an adjusting and closing member 9, 10; these members are controlled together so that the sum of the partial weight flows of exhaust gas passing through the secondary duct 16 and into the supply duct 13 is constant, without modifying the pressure upstream of said members 9, 10, and is equal to the quantity of exhaust gas not necessary for the turbine 5 of the turbocharger fitted to the engine.

Description

The present invention relates to a motor group with

  internal combustion, comprising an internal combustion engine with reciprocating pistons equipped with a turbocharger, using the exhaust gas, and a power turbine, which can receive the exhaust gases not necessary for the operation of the turbocharger by means of an exhaust gas bypass duct which can be closed and leaving the connecting duct between the internal combustion engine and the turbocharger, and which drives a combustion engine.

  work absorbing a variable power.

  A group of this type is known from the European patent published under the number EP 199 165. In this case, the working machine is constituted by a generator which is permanently coupled both with an auxiliary diesel engine and with the power turbine. In this installation, the diesel engine

  Auxiliary must always work when the generator

  rator receives power, and especially -

  when the power turbine produces power that covers or exceeds the requirements of the generator. In this case, the auxiliary diesel engine operates at idle so as to maintain constant the speed of rotation of the power turbine and then, in the case of long distances at a constant speed provided for a

  cruise, there is always a variety of

  power requirements. A disadvantage encountered in this respect, however, is the heavy soiling

  auxiliary diesel engine idling.

  When the power of the power turbine exceeds the power requirement of the generator, the speed of rotation increases excessively and the motor is uncoupled by the overspeed protection system. The object of the invention is to arrange an internal combustion engine group of the type defined above so that, under such operating conditions, the auxiliary diesel engine is stopped and the power of the power turbine can be reduced. adapted to the current requirements without the operation of the internal combustion engine with reciprocating pistons

either influence.

  According to the invention, this problem is solved in that the exhaust gas bypass duct is divided into a secondary duct leading to the exhaust pipe and into a supply duct for the power turbine, in that the secondary duct and the supply duct are respectively associated with an adjustment and closure member, in that the adjustment and closure members are jointly controlled so that

  that the sum of the weight flows of exhaust gas

  respectively flowing into the secondary duct

  the supply duct is constant, without variation of the pressure before the regulating

  shutter for any setting and be equal to the quantity

  exhaust gas not required for the turbo-

  compressor. Other features and advantages of the invention will be highlighted later in the

  description, given by way of non-limiting example, in

  1 is a schematic representation of a group with an internal combustion engine, FIG. 2 represents a first embodiment of the adjustment and shutter members in a schematic sectional view, FIGS. 5 show three diagrams, FIG. 6 represents a second embodiment of the adjustment and shutter members, and

  Figure 7 represents a third form of

  adjustment and shutter elements.

  The internal combustion engine group of FIG. 1 comprises an internal reciprocating internal combustion engine 1 which is provided with an exhaust gas collecting duct 2 and a supercharging air collecting duct 3. The duct

  exhaust manifold 2 is connected through

  a link pipe 4 with a turbine

  5 of a turbocharger. Turbocharger turbine 5

  it drives via a shaft 6 a compressor 7 which supplies the compressed air, if necessary via an air cooler.

  supercharging, to the air intake duct

3.

  Connecting duct 4 leaves an exhaust gas bypass duct 8, which leads to two regulating and shut-off devices 9, 10.

  short circuit 11, which comprises a short-circuit valve

  circuit 12 normally closed. The adjustment and closure member 9 controls the passage to a supply conduit 13, which leads to a power turbine via a quick-closing valve 14, normally open. The adjustment and closure member 10 controls the flow in a secondary duct 16. The short-circuiting duct 11 and the secondary duct 16 open into an exhaust duct 17 connected downstream of the power turbine 15 and which channels furthermore in the open air the exhaust gases that have passed through the turbine

  15 and turbine 5 of the turbocharger.

  The power turbine 15 is in drive connection, via a gear transmission 18 and a clutch 19, preferably arranged as a separating clutch, with a generator 20. In addition the drive movement

  of a regulator 21 is taken at the output of the transmission

  The regulator 21 senses the actual speed of rotation of the power turbine as a control variable, it compares this magnitude with the desired setpoint for the speed of rotation and, in case of a difference between the two values. , it applies a control command to an actuating device 22 acting on the two regulating and closing members 9, 10 so as to modify the amount of exhaust gas passing through the power turbine 15. In place of A regulator sensing the speed of rotation of the power turbine 15, it is also possible to use a regulator responsive to the power absorbed by the power turbine. In addition, an auxiliary diesel engine 24 can be coupled with the generator via

of a splitter coupling 23.

  The pressure drop in the short pipe

  circuit 11 is chosen so that it corresponds to

  to the pressure drop in the power turbine, in the conduits 13 and 16 connected upstream and

  in the adjustment and shutter members 9, 10.

  This can be achieved either by

  ci in correspondence of the short-circuiting conduit 11

  proper, either by the incorporation of a strangling

  25. The purpose of this measure is to maintain

  laughing the pressure in the ducts 4 and 8 also when the power turbine 15 must be stopped,

  for example because of a disturbance.

  Figure 2 represents in particular the

  structure of regulating and shutter members 9, 10.

  The regulating and closing member 9 comprises a valve cone 26, which determines in cooperation with an outer wall 27 of the valve the free passage opening in the conical surface A. In a similar way, adjusting and closing member 10 comprises a valve cone 28, which cooperates with an outer wall 29 of the valve and which determines the size of a passage opening in the conical surface B. The two valve cones 26, 28 therefore determine the division of the weight stream of exhaust gas arriving via the bypass duct 8 into two partial weight streams of exhaust gas respectively in the supply duct 13 and the secondary duct 16. The valve cone 26 is securely attached to an actuating bar 31, which can be moved in the direction of the arrow a or

  in opposite direction by means of the actuating device 22.

  The valve cone 28 is mounted on a sleeve 32, which can slide on the actuating rod 31. The parts 31, 32 constitute an actuating mechanism for the joint adjustment of the adjustment and closure members 9, 10 On an appendage 33 of the sleeve 32 is articulated one end of a lever 34 at the other end of which is hingedly attached a

  The lever 35 is mounted so that

  on the actuating bar 31. The free end

  the lever 35 bent carries a roller 36, which is moved

  ble in a slot 37 of a slider 38. The slider

  38 is movable in fixed guides 39 perpendicularly

  The portions 33 to 39 form an actuator for changing the relative position of the valve cones 26, 28. By a movement of the slider 38 in the direction of the arrow b, the sleeve 32 is moved. by means of the levers, 34 in the opposite direction to the direction of the arrow a on the

  31. There then occurs a variation of

  the position of the valve cone 28 with respect to

  valve cone 26. By this main advantageous means

  In the case of ship training units, it is possible to adapt the adjusting and shut-off devices 9, 10 to different weight currents of exhaust gas which pass through the control duct.

  exhaust gas bypass 8 for one and the same

  1 internal combustion engine with reciprocating pistons

  native. This case occurs when the ship moves alternately in cold areas and areas

hot.

  The adjustment and closure members 9, 10 are arranged and controlled so that the sum of the partial weight flows of exhaust gas passing through the secondary duct 16 and the supply duct 13 remains constant. To obtain this

  result in the case of regulating and closing

  9, 10 shown in FIG. 2, a given configuration is given to the valve cone 26 of the adjustment and closure member 9. For this valve cone 26, in cooperation with the outer wall 27 of the valve the dependency relationship, shown in Figure 3, of the relative diameter of the

  valve relative to the relative stroke of the valve.

  In this respect, the ratio of the valve travel y to a given point and the maximum valve travel Ymax has been plotted on the abscissa.

  ordered the ratio between the diameter of the cone of

  In the passage plane A and the maximum diameter of the valve cone 26, the curve portion dv1 shows that the valve cone 26 reaches, for a valve stroke "0", its maximum value in the plane A , that is to say, it closes the opening passage, while against, for the valve stroke "1", the opening passage located

  in plane A is completely open.

7 2-6 2619857

  Between these two points, it is possible to calculate, for each intermediate position of the valve cone 26, the free section of passage. The result is indicated in FIG. 4. In this figure, the relative valve stroke has also been plotted on the abscissa, whereas the ratio between the free passage surface of the regulating member and the regulating member has been plotted on the ordinate. shutter 9 Avl or the adjustment and shutter member 10 Av2 and the maximum free passage area of the adjustment and shutter member 9 Avlmax- This relationship is represented by the curve portion Avl for the adjustment and shutter 9.

  The diagram shown in Figure 5 represents

  the relationship, known by one measurement, between the flow passing in the power turbine 15 and the pressure upstream of this turbine. For this purpose, we have

  the pressure upstream of the power turbine

  this, expressed in bars (10 5Pa) and ordinate the relative flow passing through the power turbine, expressed by the ratio between the weight flow m at a point of

  any work and maximum throughput ma.

  The ratios for the power turbine 15 are characterized by the solid line curve. On the diagram, it has also been worn, using several lines in phantom, different relative sections of opening Avl, compared to Avlmax, the adjusting member and shutter 9. We realize in addition, in the case of a predetermined pressure of 3.1 x 105 Pa in the exhaust gas bypass duct 8 of the installation, the upstream pressure of the power turbine can be reduced by a reduction of the relative proportion of opening, to reduce not only the flow of exhaust gas in the turbine

  power but simultaneously also its power.

8 26 1 9 8 57

  Upstream and downstream of the adjustment and closure member

  In the case of total opening, there is practically the same pressure for the total opening, since it is only necessary to expect a loss of flow corresponding to an order of magnitude of one per cent of the pressure. Upstream

  the adjustment and closure member 10, it also reigns

  The downstream pressure of this organ, however, is about the pressure of the surrounding atmosphere since the secondary duct 16 opens into the open air. For this pressure difference, however, there is obtained a maximum opening of passage between the valve cone 28 of the regulating and closing member 10 and the outer valve wall 29 by an order of magnitude of about 20 percent.

  the maximum opening of the regulating organ

  ge and shutter 9, to let all the exhaust gas unnecessary for the turbine 5 of the turbocharger into the exhaust pipe 17, without there occurring a pressure increase upstream of the organ setting and shutter 10 and therefore reaction effects on the turbine 5

turbocharger.

  According to Figure 5, the flows are

  weightings of exhaust gases that are unloaded

  through the adjustment and closure member

  10 in the intermediate positions of the adjustment and closure member 9, since the sum of these two weight flows of exhaust gas must remain constant so that no reaction effect occurs on the turbine 5 of the turbocharger. Because the ratio of the weight flow of gas

  exhaust system passing through the regulator and ob-

  ration 10 in a given intermediate position and the maximum weight flow of exhaust gas is

9 2619857

  equal to the ratio between the corresponding free passage opening and the maximum free passage opening, the curve part designated A v2 in Figure 4 is then obtained. From this part of the curve, it is then possible to determine in addition, depending on a predetermined valve stroke, the part of

  curve designated dv2 in Figure 3 and therefore

  the shape of the valve cone 28.

  FIG. 4 is represented in broken line by another portion of curve Av. This again defines the sum of the free openings for the passage of the two adjustment and closure members 9,

for different settings.

  From the description made above,

  it is deduced that the adjustment and closure member 10 exerts a certain throttling effect which must be such that, when the regulating and closing member 10 is completely open, the pressure drop between the connecting pipe 4 and the exhaust duct 17 corresponds to the pressure drop across the

  turbine 5 of the turbocharger. If the strangling action

  the adjustment and shutter member 10 was not sufficient in this respect, it is then possible

  to incorporate in the secondary duct 16 a choke

  In this regard, it is advantageous that the free passage opening of the throttle 30 can be adjusted in order to adapt, for example, the installation arranged in a vessel to different operating conditions, for example to conditions of operation. tropical environment or Arctic environment, because the amount of exhaust gas discharged by the internal combustion engine reciprocating piston 1 is function, for a

  same power, the temperature of the environment.

  In this case we could do without the action

32 to 39.

2619857

  When the internal combustion engine with reciprocating pistons 1 produces a determined power and when the turbine 5 of the turbocharger does not require the totality of the quantity of exhaust gas supplied by the engine, then the amount of exhaust gas no required to enter the exhaust gas bypass duct 8. If now the generator 20 must absorb all the power that can be provided by the power turbine 15 to supply electrical consumption devices,

  the adjustment and closure member 9 is then complete.

  open while the regulator and

shutter 10 is closed.

  When now consumer devices

  The generator 15 is disconnected so that the generator consumes less power, the power turbine 15 tries to increase its rotation speed and this is however captured by the regulator 21. This sends a control command to the actuating device 22. which in turn moves the actuating rod 31 in the direction of the arrow a. Thus, the partial weight flow of exhaust gas that is supplied to the power turbine 15 is decreased and simultaneously the valve cone 28 releases a passage opening to the secondary conduit 16. Because the entire weight current of exhaust coming through

  through the bypass duct 8 is constantly

  discharged by the two passage openings, no reaction effect occurs on the turbine of the turbocharger. The operation of the reciprocating piston engine 1 is thus not influenced by

  load variations of the power turbine.

  In the embodiment of Figure 6, there is provided in the secondary duct 16 and in the supply duct 13 respectively a member 11i 2619857 setting and shutter 40, 41. Each adjusting member and shutter comprises a valve butterfly 42, 43, which is fixedly mounted on a drive shaft 44, 45. Each drive shaft 44, 45 carries an appendage 46, 47, on which is articulated one of the ends of a lever 48, 49. The other end of each lever 48, 49 is articulated respectively on an axis 50, 51 of a roller 52, 53. The pins 50, 51 are mounted on the levers 54, 55. The free end the lever 54 is held by a fixed bearing 56 while the free end of the lever 55 is connected to an actuator 57 which is itself mounted on a fixed bearing 58. Between the two levers 54, 55 is stretched a spring The pulling spring 59 holds the two rollers 52, 53 against a cam 60. The control cam 60 is mounted on a control shaft 61, which can be rotated in the direction of the arrow c or in the opposite direction by means of an actuating device controlled by the

regulator and not shown.

  Parts 46 to 55, 60, 61 constitute

  thus an actuating mechanism. The governing body

  57 carries at its free end a lock 62 to

  whose help it can be fixed in different posi-

  on a locking plate 63 installed in a fixed position. Thus the parts 57, 62, 63 constitute an actuating device for modifying the

  relative positions of the throttle valves 42, 43.

  Figure 6 shows the assembly in an average setting position. When the control shaft 61 is rotated in the direction of the arrow c, the lever 55 is pivotally displaced in the direction of the arrow d. The drive shaft 45 then rotates so that the throttle valve 43 is more open. As a result of the disposition of the tension spring 59, the roller 52 follows the corresponding contour of the control cam 60 so that the lever 54 pivots in the same direction as the lever 55. This causes, via the actuating shaft 44, a movement of the throttle valve 42 in the closing direction. The butterflies 42, 43 are arranged in this respect and arranged in such a way that, in

  one of the limit positions, they can close completely

  the intake duct 13 or the secondary duct

16.

  The rotation of the actuating shaft 61 is ensured by means of an operating device, not shown, which can be controlled in the same manner as the operating device 22 of FIG. 1 as a function of the speed of rotation. rotation of the

power turbine.

  By pivoting the actuating member 57 after opening the latch 62, the mutual position of the

  two valve butterflies 42, 43 may be modified.

  Thus, the two adjustment and shut-off members 41, 42 can be adapted to exhaust gas flow rates that are different as a function of the ambient temperature and which pass through the control duct.

  exhaust gas bypass 8.

  The embodiment of Figure 7 again involves two adjustment and shutter members 70, 71 with which the free section of passage from the exhaust gas bypass duct 8 to the duct supply 13 and up to the secondary duct 16 is adjustable. Each adjustment and closure member 70, 71 comprises a valve cone 72, 73, which cooperates with a fixed valve seat 74, 75. Each valve cone 72, 73 is mounted on an actuating rod 76, 77 Each rod

  actuator 76, 77 enters a hydraulic cylinder

  78, 79 and carries at its free end a hydraulic piston 80, 81. In the hydraulic cylinder 78 is disposed a pressure spring 82, which tends to maintain the valve cone 72 in the closed position. In the hydraulic cylinder 79 is also disposed a pressure spring 83, which however has a tendency to maintain the valve cone 73 in the

completely open position.

  The set also includes a micro-

  processor 84, which is controlled by a regulator, corresponding to the regulator 21 of Figure 1 and not shown, via a conductor 85, that is to say which receives control pulses when the actual value the rotational speed of the propulsion turbine 15 deviates from the set value of said speed. For this purpose, a family of characteristic curves is stored in the microprocessor 84 so that each position of the valve cone 72 is associated with a corresponding position of the valve cone 73. The microprocessor 84 controls the two valves 86, 87. Each valve 86, 87 is associated with a pressurized fluid inlet duct 88 or 89 and a pressurized fluid outlet duct 90 or 91, as well as with a duct

  connection 92 or 93 with the hydraulic cylinder 78 or 79.

  The microprocessor 84 further receives, via the

  94 and a distance sensor 95, a signal which indicates the position of the piston 80. In addition, the microprocessor receives, via a conductor 96 and from a

  distance sensor 97, a signal which indicates the posi-

piston 81.

  When the microprocessor 84 is warned, via the control pulses transmitted by the driver 85, that the actual speed of the speed

14 2 19857

  of rotation of the power turbine 15 deviates from the reference speed, this microprocessor 84 controls the valve 86. Thus, either the pressurized fluid inlet duct 88 or the pressurized fluid outlet duct 90, is connected to the connecting conduit 92 and thus the piston 80 is moved into the

  direction of opening or in the closing direction.

  Simultaneously, the valve 87 is controlled so that the piston 81 can move in the same direction.

  direction than the piston 80. The control of the two valves

  Weighing 86, 87 is completed as soon as the actual positions of the pistons 80 and 81, and therefore the valve cones 72 and 73, correspond to the necessary setpoints that have been stored in the

  characteristic range of the microprocessor 84.

  To take into account different conditions

  environmental conditions in which the combustion engine

  internal reciprocating piston must work, it is possible to memorize in the microprocessor different families of characteristic curves, which can be activated alternately manually or at

  means of a temperature measuring device.

  The invention is not limited to the examples

  shown and for example it is possible to

  to use other adjustment and shut-off devices

  known. Also the invention is applicable not only to ship training groups but also to groups installed in fixed positions,

  for example groups of power plants.

2619857

Claims (10)

  1. An internal combustion engine unit, comprising an internal combustion engine with reciprocating pistons equipped with a turbocharger, using the exhaust gases, and a power turbine, which can receive the exhaust gases not necessary for operation. of the turbocharger by means of an exhaust gas bypass duct which can be closed and leaving the connecting duct between the internal combustion engine and the turbocharger, and which drives a working machine absorbing a variable power, characterized in that the exhaust gas bypass duct (8) is divided into a secondary duct (16) leading to the muffler and a supply duct (13) for the power turbine (15), in that the the secondary duct and the supply duct are respectively associated with an adjustment and closure member (9, 10, 40, 41,   71), in that the adjusting and shut-off members   (9, 10, 40, 41, 70, 71) are controlled together so that the sum of the weight flows of exhaust gas flowing respectively in the secondary duct and the supply duct (16, 13). ) is constant, without variation of the pressure before the regulating and closing devices (9, 10, 40, 41, 70, 71) for any adjustment and is equal to the quantity of   exhaust gas not necessary for turbocharger seur (5).   2. group with internal combustion engine according to claim 1, characterized in that each adjustment and closure member (40, 41) consists of a   butterfly valve (42, 44, 43, 45).   3. Group with internal combustion engine according to claim 1, characterized in that each adjusting member and shutter (9, 10, 70, 71) is composed 6 61985 7   1 6 of a valve having a conical shutter (26, 28, 72, 73).   4. Group with internal combustion engine selqn   any of claims 1 to 3, characterized in   what is provided a regulator (21), which is   applied the actual rotational speed or power   this actual output of the power turbine (15) as a control variable and which adjusts this actual value to the predetermined setpoint value by control commands applied to the control members   and shutter (9, 10, 40, 41, 70, 71).   5. Internal combustion engine group according to claim 4, characterized in that the regulator is connected to an actuating mechanism (31, 32, 46 to 55, 60, 61) for modifying the positions of the setting and shutter.   Internal combustion engine unit according to claim 5, characterized in that the actuating mechanism (46 to 55, 60, 61) comprises a cam of control (60).   7. Internal combustion engine group according to   one of claims 5 or 6, characterized in that,   to change the sum of the two weight flows   exhaust gases, an actuating device   (33 to 39, 57, 62, 63) acts on the actuating mechanism (31, 32, 46 to 55, 60, 61) to change the relative position of the two adjusting members and shutter (9, 10, 40, 41).   Internal combustion engine unit according to claim 4, characterized in that the regulator   controls a microprocessor (84) for the purpose of   hydraulic or pneumatic control system.   in such a way as to regulate the control members in common and shutter (70, 71).   9. Internal combustion engine group according to 17 2619857   claim 8, characterized in that the micro-   The processor (84) can be switched to different families of characteristic curves which are associated with various relative positions of the adjustment and shutter members (70, 71). 10. Internal combustion engine group according to   any one of claims 1 to 9, characterized   in that the resistance to flow in the conduit   secondary (16) can be modified using a throttle-   (30), preferably adjustable in order to adjust is lying.