WASTE-HEAT UTILIZATION ASSEMBLY OF AN INTERNAL COMBUSTION ENGINE AND METHOD FOR OPERATING A WASTE-HEAT UTILIZATION ASSEMBLY

Abstract

The invention relates to a waste-heat utilization assembly (1) of an internal combustion engine (50), comprising a circuit (2) that conducts a working medium, wherein a pump (6), a distribution valve block (7), two evaporators (10, 11), an expansion machine (3), and a condenser (4) are arranged in the circuit (2) in the flow direction of the working medium. The two evaporators (10, 11) are arranged in a parallel connection, and the parallel connection begins at the distribution valve block (7) and ends at a node point (8). A temperature sensor (21) for determining the outlet temperature of the working medium at the expansion machine (3) is arranged between the expansion machine (3) and the condenser (4).

Claims

1-15. (canceled)

16. A waste-heat utilization arrangement (1) of an internal combustion engine (50) having a circuit (2) which conducts a working medium, wherein a pump (6), a distributor valve block (7), at least two evaporators (10, 11), an expansion machine (3) and a condenser (4) are arranged in the circuit (2) in a flow direction of the working medium, wherein the at least two evaporators (10, 11) are arranged in a parallel circuit, and the parallel circuit begins at the distributor valve block (7) and ends at a junction (8), and wherein a temperature sensor (21) for determining the outlet temperature of the working medium from the expansion machine (3) is arranged between the expansion machine (3) and the condenser (4).

17. The waste-heat utilization arrangement (1) as claimed in claim 16, characterized in that a pressure sensor (20) for determination of the inlet pressure of the working medium into the expansion machine (3) is installed between the junction (8) and the expansion machine (3).

18. The waste-heat utilization arrangement (1) as claimed in claim 16, characterized in that a collecting vessel (5) is arranged between the condenser (4) and the pump (6), and a further pressure sensor for determining the inlet pressure of the working medium into the pump (6) is installed between the collecting vessel (5) and the pump (6).

19. A method for operating a waste-heat utilization arrangement (1) of an internal combustion engine (50) having a circuit (2) which conducts a working medium, wherein a pump (6), at least one evaporator (10, 11), an expansion machine (3) and a condenser (4) are arranged in the circuit (2) in a flow direction of the working medium, wherein an outlet temperature (T.sub.21) from the expansion machine (3) is determined between the expansion machine (3) and the condenser (4), wherein a control unit (60) regulates the pump (6) as a function of the outlet temperature (T.sub.21) from the expansion machine (3) such that the outlet temperature (T.sub.21) lies above the condensation temperature (T.sub.K) of the working medium only by an optimized temperature difference (ΔT), wherein the optimized temperature difference (ΔT) is less than 25 K.

20. The method as claimed in claim 19, characterized in that the control unit (60) increases the mass flow of the working medium through the pump (6) if the outlet temperature (T.sub.21) from the expansion machine (3) is higher than the sum of the condensation temperature (T.sub.K) and the optimized temperature difference (ΔT), and in that the control unit (60) reduces the mass flow of the working medium through the pump (6) if the outlet temperature (T.sub.21) from the expansion machine (3) is lower than the sum of the condensation temperature (T.sub.K) and the optimized temperature difference (ΔT).

21. The method as claimed in claim 19, characterized in that, for different operating states of the waste-heat utilization arrangement (1), the optimized temperature difference (ΔT) is stored in a characteristic map as a function of the exhaust-gas state variables of the internal combustion engine (50), specifically at least one exhaust-gas temperature and at least one exhaust-gas mass flow or at least one exhaust-gas volume flow, and in that, during the operation of the waste-heat utilization arrangement (1), the respective operating state of the waste-heat utilization arrangement (1) is determined and the optimized temperature difference (ΔT) is regulated to the values stored in the characteristic map for the respectively determined operating state.

22. The method as claimed in claim 19, wherein at least two evaporators (10, 11) are arranged in a parallel circuit between a distributor valve block (7) and a junction (8), characterized in that an inlet pressure (p.sub.20) of the working medium into the expansion machine (3) is determined between the junction (8) and the expansion machine (3), or an inlet pressure (p.sub.22) of the working medium into the at least two evaporators (10, 11) is determined between the pump (6) and the at least two evaporators (10, 11), wherein the distributor valve block (7) divides the mass flow of the working medium between the at least two evaporators (10, 11), and wherein the control unit (60) controls and regulates the distributor valve block (7) as a function of the inlet pressure (p.sub.20) of the working medium into the expansion machine (3), or as a function of the inlet pressure (p.sub.22) of the working medium into the at least two evaporators (10, 11), respectively, such that the inlet pressure (p.sub.20, p.sub.22) is maximized.

23. The method as claimed in claim 19, wherein at least two evaporators (10, 11) are arranged in a parallel circuit between a distributor valve block (7) and a junction (8), characterized in that an inlet temperature of the working medium into the expansion machine (3) is determined between the at least two evaporators (10, 11) and the expansion machine (3), wherein the distributor valve block (7) divides the mass flow of the working medium between the at least two evaporators (10, 11), and wherein the control unit (60) controls and regulates the distributor valve block (7) as a function of the inlet temperature of the working medium into the expansion machine (3), such that the inlet temperature is maximized.

24. The method as claimed in claim 22, characterized in that the inlet pressure (p.sub.20) of the working medium into the expansion machine (3) is determined by virtue of the pressure upstream of the at least two evaporators (10, 11), or an inlet temperature of the working medium into the expansion machine (3), being used as a substitute variable.

25. The method as claimed in claim 22, characterized in that the control unit (60) actuates the distributor valve block (7) and regulates the distribution of the mass flow of the working medium to the at least two evaporators (10, 11) by way of extreme-value regulation.

26. The method as claimed in claim 22, characterized in that the regulation of the outlet temperature (T.sub.21) of the working medium from the expansion machine (3) is performed more quickly in terms of time than the regulation of the inlet pressure (p.sub.20) of the working medium into the expansion machine (3), or in that a multi-variable regulator is used which optimally regulates the outlet temperature (T.sub.21) of the working medium from the expansion machine (3) and the inlet pressure (p.sub.20) of the working medium into the expansion machine (3) simultaneously.

27. The method as claimed in claim 22, characterized in that an inlet temperature (T.sub.24) of the working medium into the expansion machine (3) is determined upstream of the expansion machine (3), wherein the control unit (60) calculates an expander efficiency using the difference between the inlet temperature (T.sub.24) and the outlet temperature (T.sub.21) of the working medium into and out of the expansion machine (3) and controls and regulates the mass flow of the working medium through the pump (6) and/or the distributor valve block (7) as a function of the expander efficiency.

28. The method as claimed in claim 22, characterized in that an expander rotational speed (rpm.sub.25) or an expander torque is determined at an output shaft of the expansion machine (3), wherein the control unit (60) regulates the pump (6) and/or the distributor valve block (7) by way of extreme-value regulation as a function of the expander rotational speed (rpm.sub.25) or as a function of the expander torque.

29. The method as claimed in claim 22, characterized in that an expander rotational speed (rpm.sub.25) is determined at an output shaft of the expansion machine (3), and in that the control unit (60) varies the mass flow of the working medium through the pump (6) and/or through the distributor valve block (7) by means of an excitation signal with a fixed frequency, filters said frequency out of the expander rotational speed (rpm.sub.25) using a bandpass filter, and evaluates the phase position in relation to the excitation signal, and thus calculates a changed actuation signal for the pump (6) and/or the distributor valve block (7).

30. The method as claimed in claim 22, characterized in that an exhaust-gas temperature and an exhaust-gas mass flow and/or exhaust-gas volume flow is stored in a characteristic map for different operating states for each evaporator (10, 11), and in that, during the operation of the waste-heat utilization arrangement (1), the respective operating state of the waste-heat utilization arrangement (1) is determined, and the control unit (60) calculates a component of the actuation of the pump (6) and/or of the distributor valve block (7) in a manner dependent on said characteristic map and controls and regulates the pump (6) and/or the distributor valve block (7) in a manner dependent on said calculation.

31. The method as claimed in claim 19, wherein a collecting vessel (5) is arranged between the condenser (4) and the pump (6), and an inlet temperature (T.sub.23) and an inlet pressure (p.sub.23) of the working medium into the pump (6) are determined between the collecting vessel (5) and the pump (6), wherein, for different operating states of the waste-heat utilization arrangement (1), a cavitation threshold is stored in a characteristic map as a function of the inlet temperature (T.sub.23) and the inlet pressure (p.sub.23), and in that, during the operation of the waste-heat utilization arrangement (1), when the cavitation threshold is approached, the inlet temperature (T.sub.23) and/or the inlet pressure (p.sub.23) are regulated such that cavitation in the pump (6) is prevented.

32. The method as claimed in claim 19, wherein the optimized temperature difference (ΔT) is less than 5 K.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0051] FIG. 1 schematically shows a waste-heat utilization arrangement according to the invention of an internal combustion engine.

[0052] FIG. 2 schematically shows the regulation of the waste-heat utilization arrangement according to the invention of an internal combustion engine, as has been shown in FIG. 1.

[0053] FIG. 3 schematically shows an exemplary embodiment of the waste-heat utilization arrangement according to the invention of an internal combustion engine with an associated regulation diagram.

DETAILED DESCRIPTION

[0054] FIG. 1 schematically shows a waste-heat utilization arrangement 1 according to the invention of an internal combustion engine 50 having a circuit 2 which conducts a working medium.

[0055] The internal combustion engine 50 has, at its outlet, an exhaust-gas tract 52 through which the exhaust gas is discharged from the internal combustion engine. The exhaust-gas tract 52 branches, at an exhaust-gas distributor valve 55, into an exhaust-gas duct 53 and a recirculation duct 54. In the exhaust-gas duct 53 there are arranged one or more exhaust-gas aftertreatment systems 51, such as for example particle filters, and the exhaust gas is, after flowing through the exhaust-gas duct 53, released into the surroundings 59. The recirculation duct 54 opens into the internal combustion engine 50 again, such that, for the combustion process, exhaust gas is mixed with fresh air; the aim here is that of minimizing the nitrogen emissions of the internal combustion engine 50.

[0056] The exhaust-gas distributor valve 55 controls the distribution of the mass flow of the exhaust gas into the exhaust-gas duct 53 and into the recirculation duct 54. It is normally the case that a significant fraction of the exhaust gas is conducted into the recirculation duct 54 predominantly in the part-load range of the internal combustion engine 50, whereas virtually no exhaust gas is conducted into the recirculation duct 54 in the full-load range.

[0057] The waste-heat utilization arrangement 1 of the internal combustion engine 50 uses thermal energy from the exhaust gas of the internal combustion engine 50 by virtue of the fact that, in at least one evaporator 10, 11 which is arranged in the circuit 2, the exhaust gas releases thermal energy to the working medium of the circuit 2. In the exemplary embodiment illustrated in FIG. 1, a first evaporator 10 is arranged in the exhaust-gas duct 53 and a second evaporator 11 is arranged in the recirculation duct 54. In alternative embodiments, it is also possible for further evaporators or only a single evaporator to be provided.

[0058] A collecting vessel 5, a pump 6, the at least one evaporator 10, 11, an expansion machine 3 and a condenser 4 are arranged in the circuit 2 in the flow direction of the working medium. In embodiments with a parallel arrangement of multiple evaporators 10, 11 in the circuit 2, a distributor valve block 7 is arranged upstream of the evaporators 10, 11; in these embodiments, the working medium is merged again at a junction 8 downstream of the evaporators 10, 11. Unless described otherwise, it will hereinafter always be assumed that two evaporators 10, 11 are arranged in a parallel circuit in the line circuit 2, as illustrated in FIG. 1.

[0059] In parallel with respect to the expansion machine 3 there is arranged a bypass duct 30 via which, by means of valve arrangements, the working medium can be conducted past the expansion machine 3, for example if the temperature of the working medium upstream of the expansion machine 3 is too low. The bypass duct 30 may in this case also run through the housing of the expansion machine for the purposes of preheating the expansion machine 3.

[0060] According to the invention, multiple sensors for determining temperatures and pressures of the working medium are arranged at various locations in the circuit 2: [0061] A temperature sensor 21 between the expansion machine 3 and the condenser 4 for the purposes of determining the outlet temperature T.sub.21 of the working medium from the expansion machine 3. [0062] A pressure sensor 20 between the junction 8 and the expansion machine 3 for the purposes of determining the inlet pressure p.sub.20 of the working medium into the expansion machine 3. [0063] A further temperature sensor 23 between the collecting vessel 5 and the pump 6 for the purposes of determining the inlet temperature T.sub.23 of the working medium into the pump 6. [0064] A further pressure sensor 22 between the pump 6 and the distributor valve block 7 for the purposes of determining the outlet pressure p.sub.22 of the working medium from the pump 6. [0065] Two additional temperature sensors 10a, 11a for the purposes of determining the two outlet temperatures T.sub.10a, T.sub.11a of the working medium from the two evaporators 10, 11. Here, the first additional temperature sensor 10a is installed between the first evaporator 10 and the junction 8, and the second additional temperature sensor 11a is installed between the second evaporator 11 and the junction 8. [0066] A rotational speed sensor and/or a torque sensor at an output shaft of the expansion machine 3 for the purposes of determining the rotational speed of the expansion machine, hereinafter referred to as expander rotational speed rpm.sub.25, and/or for determining the torque of the expansion machine, hereinafter referred to as expander torque.

[0067] According to the invention, it is not imperatively necessary for all of the sensors to be arranged as illustrated in FIG. 1. In alternative embodiments, it is even possible to dispense with sensors, or for the sensors to be arranged differently, because the pressures and temperatures to be determined may also be determined using substitute variables. In particular, the pressure sensor 20 upstream of the expansion machine 3 is subject to high loads, and must function reliably even in the presence of the high temperatures of the evaporated working medium. It is thus alternatively possible for alternative pressure sensors to be positioned upstream of the evaporators 10, 11, which pressure sensors are exposed only to relatively low temperatures. From the pressures thus determined upstream of the evaporators 10, 11, it is then also possible to calculate an inlet pressure of the evaporated working medium into the expansion machine. Alternatively, it is even possible for the inlet pressure into the expansion machine 3 to be calculated from an inlet temperature of the evaporated working medium into the expansion machine 3.

[0068] The rotational speed sensor and/or torque sensor at the output shaft of the expansion machine 3 is required only if the pump 6 and/or the distributor valve block 7 is to be controlled as a function of the expander rotational speed rpm.sub.25 and/or as a function of the expander torque.

[0069] Furthermore, it is self-evidently also possible for sensors to be used which acquire multiple variables (for example pressure and temperature) simultaneously.

[0070] FIG. 2 shows a regulation diagram of the waste-heat utilization arrangement according to the invention of an internal combustion engine, as has been described in FIG. 1. FIG. 2 shows the arrangement of a control unit 60 for the acquisition and processing of the data provided by the sensors arranged in the waste-heat utilization arrangement 1. The exemplary embodiment of FIG. 2 is in this case initially restricted to the data acquired by the pressure sensor 20, by the temperature sensor 21 and by the further temperature sensor 23, and to data transmitted from the internal combustion engine 50 to the control unit 60.

[0071] For the division of the various regulation regimes and control regimes, the control unit 60 is divided into a controller 61, a fluid mass flow regulator 62 and a fluid mass flow distribution regulator 63, wherein this division relates only to the software but not to the hardware of the control unit 60. Here, the fluid mass flow regulator 62 is the main regulator, and the fluid mass flow distribution regulator 63 is the secondary regulator.

[0072] The control unit 60, more specifically the fluid mass flow regulator 62, acquires the outlet temperature T.sub.21 of the working medium from the expansion machine 3, compares the outlet temperature T.sub.21 with a setpoint temperature predefined by the controller 61, and thus calculates a setting value for the actuation of the pump 6. The setpoint temperature may in this case be dependent on other variables within the waste-heat utilization arrangement 1 or else on variables of the internal combustion engine 50.

[0073] It is the aim of the regulation to achieve that the outlet temperature T.sub.21 is higher than the condensation temperature T.sub.K of the working medium only by an optimized temperature difference ΔT. The optimized temperature difference ΔT, and thus also the setpoint temperature for the outlet temperature T.sub.21, may vary as a function of various data, for example of the operating point of the internal combustion engine 50, of expected future operating points of the internal combustion engine 50 and of temperatures and pressures of the working medium at various locations in the waste-heat utilization arrangement 1. In typical operating states of the waste-heat utilization arrangement 1, the optimized temperature difference ΔT is less than 25 K, preferably less than 5 K.

[0074] The control unit 60 regulates the mass flow of the working medium through the pump 6 as a function of the outlet temperature T.sub.21 of the working medium from the expansion machine 3 as follows: [0075] If the outlet temperature T.sub.21 is higher than the sum of the condensation temperature T.sub.K and the optimized temperature difference ΔT, the mass flow of the working medium through the pump 6 is increased. [0076] If the outlet temperature T.sub.21 is lower than the sum of the condensation temperature T.sub.K and the optimized temperature difference ΔT, the mass flow of the working medium through the pump 6 is reduced. [0077] If the outlet temperature T.sub.21 is equal to the sum of the condensation temperature T.sub.K and the optimized temperature difference ΔT, the mass flow of the working medium through the pump 6 is not changed.

[0078] In the regulation regimes, it should be noted that the optimized temperature difference ΔT may be not only a specific value but also a temperature range. For this case, the temperature range would advantageously encompass at most a temperature interval of 10° C., because otherwise the regulation of the pump 6 would no longer be optimized.

[0079] The regulation of the mass flow of the working medium through the pump 6 may also be performed taking into consideration the two exhaust-gas state variables of the internal combustion engine 50 of exhaust-gas temperature and exhaust-gas mass flow, specifically by virtue of the optimized temperature difference ΔT being varied as a function of said two variables, as follows: [0080] In the presence of increasing exhaust-gas temperature, the optimized temperature difference ΔT is reduced. [0081] In the presence of increasing exhaust-gas mass flow, the optimized temperature difference ΔT is reduced. [0082] In the presence of falling exhaust-gas temperature, the optimized temperature difference ΔT is increased. [0083] In the presence of falling exhaust-gas mass flow, the optimized temperature difference ΔT is increased.

[0084] The change in the optimized temperature difference ΔT leads to a change in the setpoint value for the outlet temperature T.sub.21, and thus the fluid mass flow regulator 62 also changes the setting value for the mass flow of the working medium through the pump 6. Normally, for this purpose, the rotational speed and thus the delivery rate of the pump 6 are changed.

[0085] Furthermore, the regulation of the mass flow of the working medium through the pump 6 may also be performed taking into consideration the inlet temperature T.sub.23 of the working medium into the pump 6, as described below: [0086] In the presence of increasing inlet temperature T.sub.23, the throughflow of the working medium through the pump 6 is increased. [0087] In the presence of falling inlet temperature T.sub.23, the throughflow of the working medium through the pump 6 is reduced.

[0088] Here, it is clear to a person skilled in the art that combinations of the above-described regulation regimes and actuation regimes for the pump 6 may be used.

[0089] It is the object of the fluid mass flow distribution regulator 63, that is to say of the secondary regulator, to actuate the distributor valve block 7, and thus divide the mass flow of the working medium between the two evaporators 10, 11, such that the inlet pressure p.sub.20 of the working medium into the expansion machine 3 is maximized. For this purpose, the pressure sensor 20 determines the inlet pressure p.sub.20 where possible upstream of the expansion machine 3, alternatively also upstream of the two evaporators 10, 11, and transmits this to the control unit 60, more specifically to the fluid mass flow distribution regulator 63.

[0090] The actuation of the distributor valve block 7 by means of the control unit is, for this purpose, preferably performed by way of extreme-value regulation. That is to say, the distributor valve block 7 changes the distribution of the mass flow of the working medium between the two evaporators 10, 11 to a small extent and then compares said change with a subsequent change in the inlet pressure p.sub.20: [0091] If the inlet pressure p.sub.20 increases as a result of this measure, the distributor valve block 7 continues the change in the distribution of the mass flow in the same way. The target variable of the inlet pressure p.sub.20 is then in phase with the excitation signal. [0092] By contrast, if the inlet pressure p.sub.20 decreases as a result of this measure, then the distributor valve block 7 changes the distribution of the mass flow in the opposite direction. The target variable of inlet pressure p.sub.20 was then initially out of phase with the excitation signal, and was thereupon brought into phase with the excitation signal by way of a phase shift of the latter.

[0093] Example: the distributor valve block 7 changes the distribution of the mass flow such that the mass flow through the first evaporator 10 is increased and that through the second evaporator 11 is reduced. If the inlet pressure p.sub.20 is reduced as a result, that is to say if the target variable of the inlet pressure p.sub.20 is out of phase with the change in the distribution of the mass flow, then the actuation of the distributor valve block 7 is changed in the opposite direction, that is to say a phase shift is effected; that is to say, the mass flow through the first evaporator 10 is reduced and the mass flow through the second evaporator 11 is increased, such that the target variable of inlet pressure p.sub.20 is increased, that is to say is in phase with the change in the distribution of the mass flow. This is continued until the inlet pressure p.sub.20 decreases again, that is to say a new phase shift occurs. The maximum inlet pressure p.sub.20 has then been reached.

[0094] In further advanced regulation regimes, it is also possible for the change in the distribution of the mass flow through the distributor valve block 7 to be performed as a function of the operating point of the internal combustion engine 50. For example, at full load of the internal combustion engine 50, the second evaporator 54 arranged in the recirculation duct 54 is flowed through with only relatively little exhaust gas, such that, at the start of the full-load state, the distributor valve block 7 can also be actuated such that the mass flow of the working medium into the second evaporator 11 is reduced and, accordingly, the mass flow into the first evaporator 10 is increased.

[0095] The regulation diagram provides that the outlet temperature T.sub.21 of the working medium from the expansion machine 3 is regulated more quickly in terms of time than the inlet pressure p.sub.20 of the working medium into the expansion machine 3. That is to say: it is primarily the case that the fluid mass flow regulator 62, that is to say the main regulator, actuates the pump 6, and it is secondarily the case that the fluid mass flow distribution regulator 63, that is to say the secondary regulator, actuates the distributor valve block 7.

[0096] FIG. 3 schematically shows an exemplary embodiment of the waste-heat utilization arrangement according to the invention of an internal combustion engine with an associated regulation diagram. The only difference in relation to the waste-heat utilization arrangement of FIG. 1 and FIG. 2 is in this case that an additional temperature sensor 24 is arranged between the junction 8 and the expansion machine 3 for the purposes of determining the inlet temperature T.sub.24 of the working medium into the expansion machine 3. The control unit 60 can thus calculate an expander efficiency using the difference between the inlet temperature T.sub.24 and the outlet temperature T.sub.21 of the working medium into and out of the expansion machine 3 respectively. The mass flow of the working medium through the pump 6 and/or the distributor valve block 7 is controlled as a function of the expander efficiency. For example, in the presence of low expander efficiency, the mass flow through the pump 6 is reduced, and in the presence of high expander efficiency, the mass flow through the pump 6 is increased. The actuation of the distributor valve block 7 is advantageously performed taking into consideration the operating point of the internal combustion engine 50. For example, at full load of the internal combustion engine 50 and in the presence of a low expander efficiency, the distributor valve block 7 is actuated such that almost the entire mass flow of the working medium is conducted through the first evaporator 10 arranged in the exhaust-gas duct 53, and almost no mass flow is conducted through the second evaporator 11.

[0097] As a further advancement of the regulation diagram discussed immediately above taking into consideration the expander efficiency, the expander rotational speed rpm.sub.25 and/or the expander torque are/is determined, and the regulation and/or control algorithms for the pump 6 and the distributor valve block 7 are expanded to include these variables. In this case, too, use may be made of the principle of extreme-value regulation as already discussed above, with the aim of maximizing a combination of expander rotational speed rpm.sub.25 and expander efficiency or maximizing a combination of expander torque and expander efficiency.

[0098] For the extreme-value regulation regimes described above, it is advantageously possible for a bandpass filter to be used in order to filter out any disturbance variables from the target variable to be evaluated. Here, the excitation signal, for example a small change in the actuation of the distributor valve block 7 such that the distribution of the working medium between the first evaporator 10 and the second evaporator 11 is changed slightly, is provided with a fixed frequency. Said fixed frequency can be filtered out of the response signal, for example the change in rotational speed of the output shaft of the expansion machine. In this way, disturbance variables, for example other loads on the output shaft, are filtered out, and it can be checked whether the response signal is in phase with the excitation signal or out of phase with the excitation signal.

[0099] In further optimized embodiments of the software for the control unit 60, state variables of the exhaust gas of the internal combustion engine 50, for example exhaust-gas temperature and exhaust-gas mass flow, are also taken into consideration for the generation of an excitation signal. For example, in the event of an increase of the exhaust-gas temperature, it is also possible for the throughflow of the working medium through the pump 6, as an excitation signal for the extreme-value regulation, to be increased, because it can be assumed that a response signal—e.g. the expander efficiency—is in phase with the excitation signal.

[0100] It is likewise possible for expected state variables, for example impending travel under full load based on the route planner, to be incorporated into the software for the control unit 60.

[0101] For various variables to be regulated, for example the optimized temperature difference ΔT, the inlet pressure p.sub.20 of the working medium into the expansion machine 3 or the inlet temperature T.sub.23 of the working medium into the pump 6, it is possible for characteristic maps to be established in advance. In these characteristic maps, there are stored values, optimized for particular operating states of the waste-heat utilization arrangement 1, for the variables to be regulated. The operating states are characterized by various other state variables, for example the two exhaust-gas state variables of the internal combustion engine 50 of exhaust-gas temperature and exhaust-gas mass flow, or the rotational speed of the internal combustion engine. During the operation of the waste-heat utilization arrangement 1, the operating state is determined on the basis of said state variables and, correspondingly, an optimum value for the variables to be regulated is read out. By means of regulation algorithms, the variable to be regulated is subsequently set to said optimum value.