EP1045214A2 - Absorption heat pump and method for operating an absorption heat pump - Google Patents

Abstract

A burner (2) vaporises a refrigerant solution into an condenser (13) containing a heat exchanger feeding a radiator (34) and absorber (6) back to the boiler (1) in a closed circuit. Refrigerant then passes through a throttle valve (12) and an evaporator (11) to provide cooling. The system is controlled by a regulator (17) according to data from an outside thermostat (14), a back flow thermostat (15) a forward flow thermostat (16).

Description

The present invention relates to an absorption heat pump and a method for operating an absorption heat pump.

In absorption heat pump systems, a solution containing a refrigerant is heated in a cooker, for example by means of a gas or oil burner, electrically or with the aid of additional heat exchangers by means of waste heat or solar energy, in order to expel refrigerant as refrigerant vapor from the solution. The refrigerant vapor is brought to a high temperature level or high pressure level by this process. The refrigerant vapor is then condensed against a heating medium in a condenser and thus supplies the heating medium with heat. The strongly cooled and expanded refrigerant is evaporated in an evaporator against a medium that supplies ambient energy to the refrigerant and then fed to at least one absorber.

The solution depleted of refrigerant from the cooker is fed to the absorber via a heat exchanger, where the solution depleted of refrigerant is combined with refrigerant that has passed through the evaporator. The resulting heat of solution is made available to the expeller process and the consumer or is only dissipated to the consumer. The resulting refrigerant-rich solution from the absorber is pumped by means of a solution pump from the low-pressure level of the absorber, which corresponds approximately to the evaporation pressure, to a high-pressure level and is returned to the cooker. Finally, the heating medium heated in the condenser is fed to a consumer and the heating medium cooled by the consumer is returned to the condenser.

If the heating of the cooker is switched off in an absorption heat pump system, the concentration stratification prevailing in the operation of the absorption heat pump in the cooker is reduced and brought to the level of the low-refrigerant solution. During an unsteady start-up process, a concentration stratification required for the steady-state operating state can be built up in the cooker only by gradually adding rich solution. After switching off the cooker, considerable startup times and energy losses must therefore be accepted when such a system is put back into operation.

In order to overcome these problems, EP-B-0 202 432 proposes a clocking absorption heat pump system in which the high-pressure part and the low-pressure part are blocked by means of solenoid valves in order to minimize the restart losses. A disadvantage of this technique is that when the burner output changes, e.g. can be caused by temperature fluctuations, heat pump operation is not always guaranteed.

The invention is therefore based on the object of providing an absorption heat pump and a method for operating an absorption heat pump of the type described at the outset, in which or in which the energy losses which occur when the absorption heat pump is started up are minimized while reliable operation of the heat pump is nevertheless continuously ensured.

This object is achieved in a method for operating an absorption heat pump, as defined in the preamble of claim 1, which is based on EP-B-0 202 432, in that the outside temperature and the temperature of the heating medium are measured and the output of the The burner is set as a function of the measured temperature values, that the amount of refrigerant supplied to the evaporator is regulated, that the amount of solution depleted in refrigerant supplied to the at least one absorber is regulated, and that the delivery rate of the solution pump is also regulated.

Accordingly, the object is further achieved in an absorption heat pump, as defined in the preamble of claim 22, which is also based on EP-B-0 202 432, in that there are further provided: a first control device which arranged one outdoors External sensor for measuring the outside temperature, at least one heating medium sensor for measuring the temperature of the heating medium, and a first controller for regulating the output of the burner as a function of the measured temperature values, a second regulating device for regulating the amount of refrigerant supplied to the evaporator, a third regulating device for regulating the amount of solution depleted in refrigerant supplied to the at least one absorber, and a fourth regulating device for regulating the delivery quantity of the solution pump.

The solution according to the invention, which enables modulating operation of the absorption heat pump by means of the control and regulating circuits mentioned, minimizes unsteady start-up losses, while at the same time ensuring reliable heat pump operation. A cycle operation, as was provided in the systems proposed in the prior art, is prevented by the modulating technology.

For reasons of clarity, the control and regulation processes involved in the concept according to the invention, ie the burner control, the condensate throttle control, the solution throttle control and the solution pump control, are separated from one another described. However, it goes without saying that in the method and the device according to the invention all four of the control and regulation processes mentioned are implemented simultaneously.

FIG. 1

eine schematische Darstellung des Aufbaus einer Absorptionswärmepumpe sowie einer darin verwendeten Brennersteuerung nach der Erfindung zeigt;

FIG. 2 bis 4

Darstellungen ähnlich FIG. 1 sind, in welchen Ausführungsbeispiele der gemäß dem vorliegend beschriebenen Absorptionswärmepumpenkonzept verwendeten Kondensatdrosselregelung veranschaulicht sind;

FIG. 5 bis 7

Darstellungen ähnlich FIG. 1 sind, in welchen Ausführungsbeispiele der gemäß dem vorliegend beschriebenen Absorptionswärmepumpenkonzept eingesetzten Lösungsdrosselregelung veranschaulicht sind; und

FIG. 8

eine Darstellung ähnlich FIG. 1 ist, in welcher ein Ausführungsbeispiel einer gemäß dem vorliegend beschriebenen Absorptionswärmepumpenkonzept verwendeten Lösungspumpenregelung dargestellt ist.

The invention, the preferred exemplary embodiments of which are specified in the subclaims, is explained in detail below with reference to the drawings, in which

FIG. 1

shows a schematic representation of the structure of an absorption heat pump and a burner control used therein according to the invention;

FIG. 2 to 4

Representations similar to FIG. 1, in which exemplary embodiments of the condensate throttle control used according to the absorption heat pump concept described here are illustrated;

FIG. 5 to 7

Representations similar to FIG. 1, in which exemplary embodiments of the solution throttle control used according to the absorption heat pump concept described here are illustrated; and

FIG. 8th

a representation similar to FIG. 1, in which an embodiment of a solution pump control used according to the absorption heat pump concept described here is shown.

As shown in FIG. 1 is indicated schematically, an absorption heat pump comprises a cooker or expeller 1, in which a solution containing a refrigerant is heated by means of a burner 2 in order to expel refrigerant as refrigerant vapor from the solution. In the embodiment according to FIG. 1, the refrigerant vapor is fed in a line 30 via a rectifier 3 to a condenser 13, in which the refrigerant vapor is condensed against a heating medium. The heating medium heated in this way is in turn fed into a line 32, the so-called preliminary to a consumer 34, for example a radiator.

Heating medium which has passed the consumer 34 returns to the absorption heat pump via a line 36, the so-called return. In particular, the heating medium cooled in the consumer 34 can be heated in an exhaust gas heat exchanger 9 against hot exhaust gas emerging from the burner 2, which is released into the atmosphere at 44 or is otherwise disposed of or processed, before it is fed to an absorber 6. After passing through the absorber 6, which can be, for example, a plate heat exchanger, the heating medium is fed again in a line 38 to the condenser 13, so that a closed heating medium circuit results.

The refrigerant, which has been greatly cooled and expanded against the heating medium in the condenser 13, is fed in a line 40 to an aftercooler 10, from which it is supplied to an evaporator 11 via a throttle point 12. Ambient energy is supplied to the refrigerant in the evaporator 11, which may in particular be heat that is generated in the surroundings (indicated at 42 in FIG. 1) of the building to be heated by the consumer 34, for example in the ground, in water, in air , especially stored in brine.

Refrigerant, which leaves the evaporator 11, is again passed through the aftercooler 10 and from there to the absorber 6. In the absorber 6 or, as shown in FIG. 1, in a mixer 46 arranged in front of the absorber, the refrigerant is mixed with solvent which has left the cooker 1 via a line 48. The resulting heat of solution is made available to the expeller process in the cooker 1 and the consumer 34 or is only dissipated to the consumer 34. The refrigerant-rich solution leaving the absorber 6 is pumped after passing through a solution reservoir 7 by means of a solution pump 8 from the low-pressure level of the absorber 6, which corresponds approximately to the evaporation pressure, to a high-pressure level and is fed again to the cooker 1. Here, the solution rich in refrigerant can be absorbed by the absorber 6 as shown in FIG. 1 shown are passed over the rectifier 3 and a heat exchanger 4, in which the solution rich in refrigerant is subjected to a heat exchange against the refrigerant vapor leaving the cooker 1 or the solvent leaving the cooker 1. Refrigerant, which already condenses in the rectifier 3, is returned to the cooker 1 via a return 50.

The general structure of the present absorption heat pump described so far is common to all of the exemplary embodiments described below and will therefore not be described again in the description of the remaining drawings. The following description focuses primarily on the individual control and regulation aspects of the inventive concept. As already mentioned, not all control and regulation aspects are shown at the same time in the individual drawings, but the burner control, the condensate throttle control, the solution throttle control and the solution pump control are explained in succession on the basis of schematic partial drawings.

Referring to FIG. 1, the components relating to the burner control are first described. The aim of the absorption heat pump burner control is to achieve burner output control that is adapted to the heat requirements of the building to be heated, in order to ensure continuous operation of the absorption heat pump. The concept described here, unlike the known systems described at the outset, is based on the knowledge that, with suitable control and regulation of the system, it is quite sensible and energetically worthwhile not to switch off the absorption heat pump entirely when the heating requirement is reduced, but to regulate it down, because the losses that otherwise occur when the system is restarted outweigh the energy savings achieved by the shutdown.

When set up according to FIG. 1, an external sensor 14 for measuring the ambient temperature and a heating medium sensor for measuring the temperature of the heating medium are provided, wherein the heating medium sensor can be designed as a return sensor 15 for detecting the return temperature or as a flow sensor 16 for detecting the return temperature. The outside sensor 14 and the return sensor 15 and / or the flow sensor 16 are connected to a controller 17, the output of which is connected to the burner 2. The burner 2 is a controllable burner with a power consumption of, for example, 4 to 18 kW. The controller 17 compares the measured return or flow temperature with a setpoint and throttles the burner output when the return or flow temperature approaches the setpoint. The regulation can take place according to preset heating curves. On the one hand, the burner output can be directly related to the measured outside temperature by assigning certain values for the burner's power consumption to certain outside temperature values. For example, a burner output of 4 kW could be assigned to an outside temperature of +15 ° C, while the burner output should be 13 kW at an outside temperature of -15 ° C. However, the flow and / or the return temperature can also serve as control parameters for the burner output. For example, a return temperature of 25 ° C can be assigned to an outside temperature of +15 ° C, while a return temperature of 45 ° C can be assigned to an outside temperature of -15 ° C. In addition to comparing the setpoint and actual value of the return or flow temperature, the temperature spread of the heating medium, i.e. the difference between flow and return temperature, serve as control parameters. The types of control mentioned can be implemented individually or together. The burner control described thus modulates the entire heat energy generated by the absorption process to modulate the heat demand of the building to be heated, which can change continuously, for example, through individual settings (e.g. radiators are closed) or due to external influences (variation of solar radiation etc.).

In order to ensure the condensation of the refrigerant in the condenser over the entire modulating heat pump operation in the modulating burner control described above, the condensate throttle is regulated according to the concept described here. The condensate throttle control also has the task of avoiding an unnecessarily high condensation pressure and thus contributes to an improvement in the overall efficiency.

As follows with reference to FIGN. 2 to 4 is explained in detail, the condensate throttle can take place with the aid of several different control parameters. In particular, as shown in FIG. 2 is illustrated, by means of a pressure sensor 18, the pressure p _KKein of the refrigerant _{vapor entering} the condenser 13 is measured. This pressure value p _KKein can then be converted into a temperature _value T _KKein with the aid of Ziegler's fundamental _{equation familiar to the person skilled in the art} . The temperature _value T _KKein calculated in this way is then compared with a reference temperature by means of a controller 19, in the illustrated example a PID controller, in order to form an output signal for controlling a continuously controllable actuator. In the case of FIG. 2 embodiment is used as the reference temperature, the temperature T _flow of the heating medium emerging from the condenser 13, which is measured by means of a temperature sensor 16. If the temperature difference T _KKein - T _{Vorlauf is} less than a predetermined setpoint of, for example, 1 to 4 K, the amount of refrigerant supplied to the evaporator 11 is reduced by means of the adjustable throttle point 12, which can be designed, for example, as a pulse-width modulated valve. If, on the other hand, the said temperature difference is greater than the predetermined target value, the amount of refrigerant supplied to the evaporator 11 is increased. The setpoint ensures that condensate subcooling of approx. 2 to 5 K always occurs. If the difference T _KNo - T _{flow is} equal to the specified setpoint, the valve position is optimal.

A variant of the condensate throttle control of FIG. 2 is shown in FIG. 3 outlined. Instead of the pressure sensor 18 (FIG. 2), a temperature sensor 20 is provided here, which _detects the temperature T _KKaus of the refrigerant emerging from the condenser 13. This temperature T _KKaus is in turn compared with the temperature T _flow of the heating medium emerging from the condenser 13. The prevailing condensate _supercooling can be assessed on the basis of the temperature difference between the flow temperature T _flow , which corresponds to the condensation temperature, and the temperature T _{KK from} the condensate, which is determined using a controller 19. If a setpoint is specified for the condensate subcooling, the throttle point 12 can be opened or closed completely or partially based on a comparison between the temperature difference mentioned and this setpoint. The setpoint value for the condensate subcooling is preferably in the range between 2 and 5 K.

Another variant of the condensate throttle control of FIG. 2 is shown in FIG. 4 shown. The embodiment of FIG. 4 differs from that of FIG. 3 in that the temperature of the heating medium is not measured at the outlet of the condenser 13 but at its inlet. The temperature T _KKaus of the refrigerant emerging from the condenser 13 measured by means of a temperature sensor 20 is then compared with the temperature T _HKein of the heating means entering the condenser 13 measured by means of a temperature sensor 21, the controller 19 preferably _comprising a difference _former for this purpose. As in the above exemplary embodiments, the temperature difference resulting from the comparison of the two temperatures mentioned can in turn be compared with a Setpoint value compared and the throttle point are regulated depending on this comparison.

• der Durchfluß und somit die Konzentration der an Kältemittel armen Lösung nehmen zu,
• der spezifische Lösungsumlauf wird größer,
• das Lösungsfeld wird weiter zusammengezogen,
• die Konzentrationsdifferenz und damit auch die Temperaturdifferenz zwischen Kesselfuß und Kesselkopf des Kochers verringert sich,
• die Konzentration der reichen" Lösung im Absorber wird kleiner
• der Niederdruck sinkt.

Referring to FIGN. 5 to 7, the solution throttle control used in the present absorption heat pump concept is explained below. The solution throttle 5 shown in the drawings determines the flow of the low-refrigerant solution which is discharged from the cooker 1 via the heat exchanger 4 and which is mixed in the mixer 46 (FIG. 1) with refrigerant emerging from the aftercooler 10 before it flows into the Absorber 6 is initiated. By adjusting the solution throttle 5, the absorber operated at low pressure or the evaporation pressure is influenced. The aim of this regulation is to keep the low pressure in every operating state of the heat pump so that the evaporator 11 absorbs the maximum possible energy and at the same time it is ensured that an unnecessarily high mass flow of the solution, which is low in refrigerant, does not occur. If the solution throttle 5 is opened, this has a number of effects:

• the flow and thus the concentration of the low-refrigerant solution increase,
• the specific solution circulation increases,
• the solution field is further contracted
• the difference in concentration and thus also the temperature difference between the kettle foot and kettle head of the cooker is reduced,
• the concentration of "solution in the absorber becomes smaller
• the low pressure drops.

Closing the solution throttle has corresponding opposite effects.

According to FIG. 5, the temperature T _KVein of the refrigerant supplied to the evaporator 11 is measured by means of a temperature sensor 22. With the aid of a second temperature sensor 23, the temperature T _KVaus of the refrigerant emerging from the evaporator 11 is _detected . A PID controller 26 forms a difference from the two measured temperature values and, based on the result of the difference formation, applies an actuating signal to the solution throttle 5. In particular, the ascertained temperature difference is compared with a predetermined setpoint value, similarly to the methods described above, a particularly preferred range for this setpoint value of 7 to 10 K being achieved in the embodiment described here. If the temperature difference determined is greater than the predetermined setpoint, the solution throttle 5 is closed; If the determined temperature difference is smaller than the specified target value, the solution throttle 5 is opened. The regulation of the solution throttle 5 can also be done by measuring the flow temperature, as described with reference to FIG. 2 and 3 has been explained, influenced by the setpoint for the difference between the temperature T _KVein the evaporator 11 supplied refrigerant and the temperature T _KVaus of the refrigerant emerging from the evaporator 11 is varied depending on the flow temperature T _flow . For example, the control can be designed so that the setpoint for the temperature difference mentioned on the evaporator at a flow temperature of 30 ° C is, for example, 14 K, while this setpoint is lowered to, for example, 7 K at a flow temperature of 50 ° C.

In the case of FIG. 6 outlined variant of the solution throttle control according to FIG. 5, the temperature T _KVein of the refrigerant supplied to the evaporator 11 measured by the temperature sensor 22 is compared with the temperature T _MVein of the medium supplied to the evaporator 11 (brine, water, air, etc.) measured by means of a temperature sensor 24. Based on this comparison, the controller 26 delivers an actuating signal to the solution throttle 5 as a function of a predetermined target value.

Another variant of the solution throttle control is shown in FIG. 7, wherein the pressure p _KVaus of the refrigerant emerging from the aftercooler 10 and the temperature T _KVaus of the refrigerant emerging from the evaporator 11 are measured by means of a pressure transducer 28. The measured pressure value can then be converted into a temperature value in a manner similar to that described above with reference to the condensate throttle control used here, and can be compared with the temperature value measured by means of the temperature sensor 24. The temperature difference determined in this way is then compared with a predetermined target value in order to obtain a control signal for the solution throttle 5. The in FIG. The arrangement of the pressure transducer 28 and the temperature sensor 24 shown in FIG. 7 could also be modified such that both transducers are arranged at essentially the same point in the process flow. In particular, both the pressure transducer 28 and the temperature sensor 24 could be placed between the aftercooler 10 and the mixer 46 or between the evaporator 11 and the aftercooler 10.

FIG. 8 shows an embodiment of the solution pump control used in the present absorption heat pump concept. As with reference to FIG. 1, the solution leaving the absorber 6 and rich in refrigerant after passing through the solution reservoir 7 is pumped by means of a solution pump 8 from the low pressure level of the absorber 6 to a high pressure level and fed again to the cooker 1. In the case of FIG. The exemplary embodiment of the solution pump control shown in FIG. 8 is detected by means of a float 29 arranged in the solution reservoir 7, advantageously a magnetically inductive float, and the fill level of the solution reservoir 7 is detected and, based on the measured fill level, the speed of the solution pump 8 and thus the solution mass flow are adapted to the process.

Claims (34)

Process for operating an absorption heat pump at the (a) in a cooker (1) a solution containing a refrigerant is heated by means of a burner (2) in order to expel refrigerant as refrigerant vapor; (b) the refrigerant vapor is condensed in a condenser (13) against a heating medium in order to supply heat to the heating medium; (c) the refrigerant from the condenser to an evaporator (11), in which it is evaporated against a medium, and then fed to at least one absorber (6); (d) refrigerant-depleted solution is fed from the cooker via a heat exchanger (4) to the at least one absorber, where the refrigerant-depleted solution combines with refrigerant that has passed through the evaporator; (e) the refrigerant-rich solution is pumped from the absorber to a high pressure level by means of a solution pump (8) and is fed back to the cooker; and (f) the heating medium heated in the condenser (13) is supplied to a consumer and the heating medium cooled by the consumer is returned to the condenser;
characterized in that (g) the outside temperature and the temperature of the heating medium are measured and the output of the burner (2) is set as a function of the measured temperature values; (h) regulating (19) the amount of refrigerant supplied to the evaporator (11); (i) regulating the amount of the solution depleted in refrigerant to the at least one absorber (6); and (j) the delivery rate of the solution pump (8) is regulated. Method according to Claim 1, characterized in that the refrigerant emerging from the condenser (13) is brought into indirect heat exchange with refrigerant emerging from the evaporator (11) before it is fed to the evaporator (11). Method according to Claim 1 or 2, characterized in that the temperature (T _return ) of the heating medium is measured after it has passed through the consumer (return temperature). A method according to claim 3, characterized in that the return temperature (T _return ) is measured repeatedly and (g ₁ ) the measured value of the return temperature is compared with a target value; and (g ₂ ) the burner output is throttled when the measured value of the return temperature approaches the setpoint of the return temperature. Method according to one of claims 1 to 4, characterized in that the temperature (T _flow ) of the heating medium supplied to the consumer by the condenser is measured (flow temperature). A method according to claim 5, characterized in that the flow temperature (T _flow ) is measured repeatedly and (g ₁ ) the measured value of the flow temperature is compared with a target value; and (g ₂ ) the burner output is throttled when the measured value of the flow temperature approaches the setpoint of the flow temperature. Method according to one of the preceding claims, characterized in that the return temperature (T _return ) and the flow temperature (T _forward ) are measured repeatedly and (g ₁ ) the difference between the measured values of the flow temperature and the return temperature is formed for each measurement; and (g ₂ ) the burner output is throttled if the difference in one measurement is smaller than in the previous measurement. Method according to one of the preceding claims, characterized in that the outside temperature (T _A ) is measured repeatedly and the burner output is increased as the outside temperature drops. Method according to one of the preceding claims, characterized in that (h ₁ ) the pressure (p _KKein ) of the refrigerant _{vapor entering} the condenser (13) and the temperature (T _flow ) of the heating medium emerging from the condenser are measured; and (h ₂ ) the amount of refrigerant supplied to the evaporator (11) is set as a function of the measured pressure and temperature values (p _KKein , T _Vorlauf ). A method according to claim 9, characterized in that (h ₂₁ ) the measured pressure value (p _KKein ) is converted into a temperature _value (T _KKein ) and by means of the temperature _value thus calculated (in Kelvin) and the flow temperature (in Kelvin) according to the following formula (I) $${\text{A = T}}_{\text{No}}{\text{- T}}_{\text{leader}}\text{- B}$$ where B has a value between 0.5 and 10 K, preferably between 1 and 4 K,
a manipulated variable A is calculated; and (h ₂₂ ) the amount of refrigerant supplied to the evaporator (11) is increased when A is greater than zero; and (h ₂₃ ) the amount of the refrigerant supplied to the evaporator (11) is reduced when A is less than zero. Method according to one of claims 1 to 8, characterized in that (h ₁ ) the temperature (T _KKaus ) of the refrigerant emerging from the condenser (13) and the temperature (T _flow ) of the heating medium emerging from the condenser are measured; and (h ₂ ) the throttle point (12) is set as a function of the measured temperature values (T _KKaus , T _Vorlauf ). A method according to claim 11, characterized in that (h ₂₁ ) the difference of the measured temperature values is compared with a target value D according to the following formula (II); $${\text{C = (T}}_{\text{leader}}{\text{- T}}_{\text{KKaus}}\text{) - D}$$ to obtain a manipulated variable C, where D has a value between 1 and 10 K, preferably between 2 and 5 K; and (h ₂₂ ) the amount of refrigerant supplied to the evaporator (11) is increased when C is greater than zero; and (h ₂₃ ) the amount of the refrigerant supplied to the evaporator (11) is reduced when C is less than zero. Method according to one of claims 1 to 8, characterized in that (h ₁ ) the temperature (T _KKaus ) of the refrigerant emerging from the condenser and the temperature (T _HKein ) of the heating medium entering the condenser (13) are measured; and (h ₂ ) the throttle point (12) is set as a function of the measured temperature values (T _KKaus , T _HKein ). A method according to claim 13, characterized in that (h ₂₁ ) the difference between the measured temperature (T _KKaus ) of the refrigerant emerging from the condenser and the temperature (T _HKKein ) of the heating medium entering the condenser (13) is calculated; and (h ₂₂ ) the throttle point (12) is set depending on the calculated difference. Method according to Claim 14, characterized in that the said measuring and calculation processes are carried out repeatedly and the opening area of the throttle point (12) is reduced when the temperature difference increases or is increased when the temperature difference decreases. Method according to one of the preceding claims, characterized in that (i ₁ ) the temperature (T _KVein ) of the refrigerant supplied to the evaporator (11) and the temperature (T _KVaus ) of the refrigerant emerging from the evaporator (11) are measured; and (i ₂ ) the amount of the refrigerant-depleted solution supplied to the at least one absorber (6) is set as a function of the measured temperature values (T _KVein , T _KVaus ). A method according to claim 16, characterized in that (i ₂₁ ) the difference between the measured temperature values (T _KVein , T _KVaus ) is compared with a target value F according to the following formula (III): $${\text{E = (T}}_{\text{KVo}}{\text{- T}}_{\text{KVaus}}\text{) - F}$$ to obtain a manipulated variable E; and (i ₂₂ ) the amount of refrigerant-depleted solution supplied to the at least one absorber (6) is increased if E is greater than zero; and (i ₂₃ ) the amount of refrigerant-depleted solution supplied to the at least one absorber (6) is reduced if E is less than zero. Method according to one of claims 1 to 15, characterized in that (i ₁ ) the temperature (T _KVein ) of the refrigerant fed to the evaporator (II) and the temperature (T _MVein ) of the medium fed to the evaporator (11) are measured, and (i ₂ ) the amount of the refrigerant-depleted solution supplied to the at least one absorber (6) is set as a function of the measured temperature values (T _KVein , T _MVein ). A method according to claim 18, characterized in that (i ₂₁ ) the difference between the measured temperature values (T _KVein , T _MVein ) is compared with a target value H according to the following formula (IV): $${\text{G = (T}}_{\text{MVein}}{\text{- T}}_{\text{KVo}}\text{) - H}$$ in order to obtain a manipulated variable G; and (i ₂₂ ) the amount of refrigerant-depleted solution supplied to the at least one absorber (6) is increased if G is greater than zero; and (i ₂₃ ) the amount of the refrigerant-depleted solution supplied to the at least one absorber (6) is reduced if G is less than zero. Method according to one of claims 1 to 15, characterized in that (i ₁ ) the pressure (p _KVaus ) of the refrigerant emerging from the evaporator (11) and the temperature (T _KVaus ) of the refrigerant emerging from the evaporator (11) are measured, and (i ₂ ) the amount of the refrigerant-depleted solution supplied to the at least one absorber (6) is set as a function of the measured pressure and temperature values (p _KVaus , T _KVaus ). A method according to claim 20, characterized in that (i ₂₁ ) the measured pressure value (p _KVaus ) is converted into a temperature _value T _evaporation and by means of the temperature _value calculated in this way (in Kelvin) and the temperature (T _KVaus ) of the refrigerant emerging from the evaporator (11) according to the following formula (V ) $${\text{L = T}}_{\text{Evaporation}}{\text{- T}}_{\text{KVaus}}\text{- M}$$ where M preferably has a value between 4 and 15 K,
a manipulated variable L is calculated; and (j ₂₂ ) the amount of refrigerant-depleted solution supplied to the at least one absorber (6) is increased when L is less than zero; and (j ₂₃ ) the amount of the refrigerant-depleted solution supplied to the at least one absorber (6) is reduced if L is greater than zero. Method according to one of the preceding claims, characterized in that (j ₁ ) the refrigerant-rich solution coming from the absorber is passed through a solution reservoir (7), (j ₂ ) the level in the solution reservoir is measured, and (j ₃ ) the delivery rate of the solution pump (8) is set as a function of the measured level. Absorption heat pump with (a) a cooker (1) for receiving a solution containing a refrigerant; (b) a burner (2) for supplying heat to the cooker (1) to generate refrigerant vapor; (c) a capacitor (13); (d) a conduit assembly (30) for transferring refrigerant vapor from the cooker to the condenser; (e) a line arrangement (32, 36) for transferring a heating medium heated in the condenser by means of condensing refrigerant vapor from the condenser to a consumer (34) and for returning heating medium cooled by the consumer to the condenser; (f) an evaporator (11) for evaporating the refrigerant against a medium; (g) a throttle point (12) and a line arrangement (40) for transferring refrigerant from the condenser (13) to the throttle point (12) and from the throttle point to the evaporator (11); (h) at least one absorber (6) and a line arrangement for transferring refrigerant from the evaporator to the absorber; (i) a line arrangement (48, 38) for transferring the solution depleted of refrigerant in the cooker to the at least one absorber; and (j) a solution pump (8) to pressurize refrigerant-rich solution derived from the absorber to a high pressure level and a line arrangement for transferring the high-pressure refrigerant-rich solution to the cooker;
marked by (k) a first control device which has an outdoor sensor (14) for measuring the outside temperature, at least one heating medium sensor (15, 16) for measuring the temperature of the heating medium, and a first controller (17) for controlling the output of the burner ( 2) depending on the measured Temperature values; (l) second control means (16, 18, 19, 20, 21) for controlling the amount of the refrigerant supplied to the evaporator (11); (m) a third regulating device (22, 23, 24, 26, 28) for regulating the amount of the solution depleted in refrigerant supplied to the at least one absorber (6); such as (n) a fourth control device (27, 29) for controlling the delivery rate of the solution pump (8). Absorption heat pump according to claim 23, characterized by an aftercooler (10), in which refrigerant emerging from the condenser (13) is brought into indirect heat exchange with refrigerant emerging from the evaporator (11) before it is supplied to the evaporator (11). Absorption heat pump according to claim 23 or 24, characterized in that the first control device has a return sensor (15) arranged between the consumer (34) and the condenser (13) for measuring the temperature (T _return ) of the heating medium after it has passed through the consumer, includes. Absorption heat pump according to one of claims 23 to 25, characterized in that the first control device comprises a _flow sensor (34) arranged between the condenser (13) and the consumer (34) for measuring the temperature (T _flow ) of the heating medium supplied to the consumer by the condenser . Absorption heat pump according to one of claims 23 to 26, characterized in that the second control device comprises a temperature sensor (16) for measuring the temperature (T _flow ) of the heating medium emerging from the condenser (13), a pressure sensor (18) for measuring the pressure (p _KKein ) of the refrigerant _{vapor entering} the condenser (13), as well as a controller (19) which adjusts the amount of refrigerant supplied to the evaporator (11) as a function of the measured pressure and temperature values (p _KKein , T _Vorlauf ). Absorption heat pump according to one of Claims 23 to 26, characterized in that the second control device has a first temperature sensor (16) for measuring the temperature (T _flow ) of the heating medium emerging from the condenser (13) and a second temperature sensor (20) for measuring the temperature (T _KKaus ) of the refrigerant emerging from the condenser, as well as a controller (19) which adjusts the amount of refrigerant supplied to the evaporator (11) as a function of the measured temperature values (T _flow , T _KKaus ). Absorption heat pump according to one of claims 23 to 26, characterized in that the second control device has a first temperature sensor (20) for measuring the temperature (T _KKaus ) of the refrigerant emerging from the condenser (13), a second temperature sensor (21) for measuring the temperature (T _HKKein ) of the heating medium entering the condenser, and comprises a controller (19) which adjusts the amount of refrigerant supplied to the evaporator (11) as a function of the measured temperature values (T _KKaus , T _HKein ). Absorption heat _pump according to one of claims 23 to 26, characterized in that the third control device has a first temperature sensor (22) for measuring the temperature (T _KVein ) of the refrigerant supplied to the evaporator (11), a second temperature sensor (23) for measuring the temperature ( T _KVaus ) of the refrigerant emerging from the evaporator, as well as a controller (26) which adjusts the amount of the solution depleted in refrigerant to the at least one absorber (6) as a function of the measured temperature values (T _KVein , T _KVaus ). Absorption heat _pump according to one of claims 23 to 26, characterized in that the third control device has a first temperature sensor (22) for measuring the temperature (T _KVein ) of the refrigerant supplied to the evaporator (11), a second temperature sensor (24) for measuring the temperature ( T _MVein ) of the medium supplied to the evaporator, as well as a controller (26) which adjusts the amount of the solution depleted in refrigerant to the at least one absorber (6) as a function of the measured temperature values (T _KVein , T _MVein ). Absorption heat _pump according to one of claims 24 to 27, characterized in that the third control device _{comprises a} pressure _sensor (28) for measuring the pressure (p _KVout ) of the refrigerant emerging from the evaporator (11), a temperature sensor (24) for measuring the temperature (T _KVaus ) of the refrigerant emerging from the evaporator, as well as a controller (26) which adjusts the amount of the solution depleted in refrigerant to the at least one absorber (6) as a function of the measured pressure and temperature values. Absorption heat pump according to one of claims 23 to 26, characterized in that the fourth control device a container (7) with a level measuring arrangement (29) for determining the level of a liquid introduced into the container, a line arrangement for transferring the refrigerant-rich solution derived from the absorber (6) to the container (7); and a controller (27) for adjusting the delivery rate of the solution pump (8) in dependence from the measured liquid level. Absorption heat pump according to claim 33, characterized in that the level measuring arrangement (29) has an inductive float.