EP3058289A1

EP3058289A1 - Absorption refrigerating machine

Info

Publication number: EP3058289A1
Application number: EP13785816.3A
Authority: EP
Inventors: Fabian Schmid; Thomas Brendel; Marius MÜLLER; René HAHN
Original assignee: Universitaet Stuttgart
Current assignee: Universitaet Stuttgart
Priority date: 2013-10-18
Filing date: 2013-10-18
Publication date: 2016-08-24
Also published as: WO2015055159A1

Abstract

The invention relates to an absorption refrigerating machine (1) comprising a circulated working substance, in different mixing ratios of a solvent and a refrigerant depending on the circulating process, a high-pressure area (2) with a generator (14) generating the refrigerant from the solvent while heat is supplied, as a first component, and a condenser (20) condensing generated refrigerant, as a second component, a low-pressure area (3) with an evaporator (25) evaporating the refrigerant while heat is extracted, as a third component, and an absorber (28) for the absorption of refrigerant vapour in the solvent, as a fourth component, a refrigerant expansion valve (24), arranged between the high-pressure area and the low-pressure area, a solvent expansion valve (30), arranged between the high-pressure area and the low-pressure area, and also a working substance pump (8), arranged between the absorber and the generator, and also possibly a deflegmator (10), arranged between the generator and the condenser, as a fifth component, and also possibly a solvent heat exchanger (23), as a sixth component. In order to lower the costs of an absorption machine and increase its efficiency, at least one component is formed in itself or in combination with at least one other component as a plate heat exchanger.

Description

Absorption chiller

The invention relates to an absorption refrigeration machine according to the preamble of claim 1.

Absorption refrigerators serve, for example, the cooling of rooms, where heat is used as drive energy. In this case, a solvent consisting of a solvent and a refrigerant is subjected to a cyclic process in which the refrigerant is expelled from the solvent and re-absorbed by means of different components and heat supply or withdrawal. Typical working substances may be ammonia / water mixtures in which ammonia is used as the refrigerant and water as the solvent, mixtures of lithium bromide and water in which water is used as the refrigerant, and the like. The phase changes of the refrigerant and the mixing ratios of the working substance take place in appropriately designed, arranged in the cycle components. A cyclic process includes at least one high-pressure operating section having a compressor driving the refrigerant with heat supply from the solvent as a first component and a second refrigerant expelled refrigerant condensing condenser, a low-pressure section having a third evaporator evaporating the refrigerant under heat removal, and an absorber for absorbing Refrigerant vapor in the solvent as the fourth component, a arranged between the high-pressure region and low-pressure refrigerant expansion valve, arranged between the high-pressure region and low pressure area solvent expansion valve and arranged between the absorber and expeller agent pump. To improve the separation of refrigerant and solvent may optionally be provided between the expeller and condenser dephlegmator as a fifth component and a solvent heat exchanger as the sixth component. EP 2 584 287 A1 shows one possible form of absorption chiller. Due to the nature of the design of the components, for example using a heated container as an expeller, the efficiency of the absorption chiller, for example, their coefficient of performance in the form of the quotient of the heat extracted from the environment and the heat used for this purpose is not optimal. Furthermore, the individual components require a large amount of space. Furthermore, so-called plate heat exchangers, for example from WO 201 1/003496 A2 are known for exchanging heat between two fluids, in which a plurality of juxtaposed plates form two flow channels with a large surface area for the two fluids in heat exchange. Operation under reduced pressure and for the separation of three-phase mixtures with such plate heat exchangers is not provided.

The object of the invention is the advantageous development of an absorption chiller. The training should improve the coefficient of performance. The training is intended to achieve a compact design. Furthermore, a design should reduce the number of components. Furthermore, the production is to be simplified and the cost of production to be reduced.

The object is solved by the subject matter of claim 1. The dependent of the claim 1 claims give advantageous embodiments of the subject matter of claim 1 again.

The proposed absorption chiller includes for performing a cyclic process such as thermodynamic cycle processes present in different mixing ratios of a solvent and a refrigerant agent, preferably an ammonia / water mixture with ammonia as a refrigerant, an aqueous lithium bromide solution with water as a refrigerant or the like. The cyclic process is subdivided into one for ammonia / water mixtures below atmospheric pressure and for an aqueous lithium bromide solution above the

At atmospheric pressure working high pressure area and a low pressure area with working below the pressure of the high pressure area pressure. In the high pressure range and low pressure range, at least the following components of the cycle are provided:

- A in the high pressure region, the refrigerant driven by heat from the solvent expeller driving, an expelled refrigerant condensing condenser and optionally arranged between expeller and condenser dephlegmator. The dephlegmator can also be provided as a rectifier for further purification of the refrigerant.

- An evaporator evaporating in the low pressure range, the refrigerant under heat removal and an absorber for the absorption of refrigerant vapor in the solvent.

For the separation of the high and low pressure ranges, a refrigerant expansion valve for the controlled transport of the refrigerant from the high-pressure region into the low-pressure region rich.

A solvent expansion valve for the controlled transport of the solvent or a mixture of the working substance discharged from the refrigerant from the high-pressure region and in the low-pressure region.

The supply of the adjusted in the absorber to the substantially original mixing ratios of the working substance by means of a arranged between the absorber and expeller working fluid pump as circulating pump. Before the circulating pump, a collecting container may be provided for the working substance. To form the proposed absorption chiller effectively in terms of coefficient of performance, production cost and compactness, at least one of the components is formed alone or in combination with at least one further component as a plate heat exchanger. This means that, for example, the expeller, the condenser, the evaporator and additionally provided components such as solvent heat exchangers, precoolers and the like can be designed as a plate heat exchanger and several of these components can be combined into a single component. In this case, a plate heat exchanger in ammonia / water mixtures must be adapted to the specific requirements of the individual components, for example, be adapted to pressures below atmospheric pressure, the treatment of liquid and gaseous phase systems of the working material and the like.

For the purposes of the disclosure, a "rich solution" is to be understood as meaning a working substance in its original composition, for example ammonia-rich working substance having a concentration of, for example, 50% by weight of ammonia to understand. Refrigerant vapor is the still more or less proportions of the solvent containing gaseous refrigerant. Refrigerant means the condensed, liquid refrigerant.

In an advantageous embodiment of the proposed absorption chiller, a dephlegmator is provided between the absorber and the expeller with a supply container connected between the dephlegmator and the expeller

Dephlegmator cooled via a separator, solvent-contaminated, run between the expeller and condenser refrigerant vapor by means of a refrigerant-enriched, cooled by the supplied from the working fluid pump in the expeller agent. For this purpose, the expeller is preferably formed as a plate heat exchanger, the master container and the separator are provided to secure its function in this environment. The rich preheated in the dephlegmator Solution enters the reservoir and then flows through the plate heat exchanger. Here, the refrigerant is desorbed as ammonia. The mode of operation takes place here without forced flow, so that even in the dephlegmator and in a solvent heat exchanger downstream of the solvent pump, expelled refrigerant vapor can be separated in the feed tank and can rise directly into the dephlegmator. This can lead to the refrigerant being saturated with refrigerant in the generator. This constant mixing of the agent at the entrance to the expeller leads to a stable operation of the plate heat exchanger and thus to a stable operation of the entire absorption chiller. Furthermore, fluctuations in the volume flow conveyed by the working fluid pump can be compensated by the reservoir. In the separator, the flow velocity of the refrigerant vapor is preferably, for example, by cross-sectional widening of the access, a baffle plate and / or reduced. As a result, less ammonia-poor solution is entrained by the refrigerant vapor, so that the deposition of the cooling steam is improved. The separator may have surface-enlarging, solvent-promoting elements such as Raschig rings. Through an opening at the bottom of the separator, the poor solution is deposited. In this way, the plate heat exchanger can be proposed in functional unit with the storage tank, which sets a constant level in the plate heat exchanger, and the separator discharging the poor solution as a three-component assembly corresponding to a container expander with reduced dimensions and improved separation properties. Another advantage of this functional unit is its not forced flow operation. As a result, condensate rich in refrigerant in the dephlegmator can flow directly into the feed tank without being disadvantageously fed to the poor solution, as is the case, for example, in conventional expellers.

As already mentioned above, a solvent heat exchanger can be provided between the separator and the absorber. The latter exchanges heat between the working fluid enriched with refrigerant, ie the rich solution and a refrigerant depleted in the refrigerant, from the separator via the solvent expansion valve to the absorber, ie the poor solution. After the solvent heat exchanger, an absorber precooler can be arranged and thus preceded by the absorber which is operated with cooling medium, for example externally controlled by a 3-way valve supplied cooling water, an external recooling unit or the like and compared to the depleted refrigerant refrigerant further cooling causes. This absorber precooler can be designed as a plate heat exchanger. An absorption chiller designed as a plate heat exchanger as an absorber precooler can also be designed with a conventional expeller in an advantageous manner. By inserting the Absorbervorkühlers the poor solution can be cooled particularly effectively before entering the absorber, so that the absorption of gaseous refrigerant in the absorber improved and the thermally coupled at least via lines evaporator can be operated at lower temperatures or an increase in the refrigerant line and a improved coefficient of performance can be achieved. The absorption process of the vaporous refrigerant in the poor solution is preferably divided into two areas. The poor solution is injected into the absorber, as disclosed, for example, in WO 1998/012487 A1. Then it comes in the spray cone to a pre-absorption of refrigerant vapor to saturation. The remaining refrigerant vapor and the saturated as rich solution flow into the plate column of the plate heat exchanger, where they are further cooled by the cryogen. Thereby, a further saturation due to the increasing with decreasing temperature absorption coefficient can be achieved. The absorber pre-cooler lowers the inlet temperature of the poor solution in the spray cone and thus the degree of pre-absorption. This leads to an improved absorption in absorption chillers also in the form of heat pumps, especially when the evaporator temperatures are low and thus the pressure in the low temperature range drops and the absorber temperatures must therefore be low.

In connection or independent of equipped with a trained as a plate heat exchanger expeller and / or Absorbervorkühler absorption chillers, an absorption chiller may be advantageous, the dephlegmator and condenser are designed as a common component as a unit in the form of a triple heat exchanger. By combining the dephlegmator and the capacitor, a single assembly is achieved that manages with less space and less manufacturing costs. Here, the individual plates can be arranged one behind the other, so that only two cover plates and six connections are required. For this purpose, the triple heat exchanger advantageously has a refrigerant channel passing through the refrigerant vapor and two channels of the dephlegmator and the condenser arranged one behind the other along the refrigerant channel. In contrast to two individual heat exchangers thus material, weight, manufacturing costs such as welding costs and costs can be saved. Corresponding to the solvent heat exchanger, a refrigerant heat exchanger can be provided, which carries out a heat exchange between a guided between the condenser and evaporator refrigerant flow of condensed refrigerant and a guided between evaporator and absorber refrigerant vapor. Such a refrigerant heat exchanger may be formed as a plate heat exchanger. Furthermore, a refrigerant reservoir can be provided between the condenser and the refrigerant heat exchanger. Furthermore, the capacitor may be formed of a plate heat exchanger. In a particularly advantageous manner, evaporators,

Refrigerant heat exchanger and refrigerant reservoir form a common 3-way heat exchanger. The triple heat exchanger may be formed as a unit from a single component such as plate heat exchanger, wherein the triple heat exchanger with a continuous flow for the refrigerant, separated from the refrigerant expansion valve in the high pressure region and the low pressure region refrigerant channel and two arranged along the refrigerant channel in a row Channels of the refrigerant heat exchanger and the evaporator forms. In this case, the channel of the refrigerant heat exchanger can receive the refrigerant reservoir. In other words, two heat exchangers and the refrigerant reservoir are housed in only one component by appropriate arrangement of the plates of a plate heat exchanger. The integrated in this integrated refrigerant heat exchanger at the same time serves as a refrigerant reservoir. With a large, high-level refrigerant reservoir, the maximum heat transfer decreases due to a reduced transfer area. However, the necessary transfer area is also lower due to a lower heat flux. It may be advantageous that the temperature of the

Refrigerant heat exchanger and the evaporator can be well below the ambient temperature and can be reduced by the lower total surface area of the combined component compared to separate components of the heat input into the absorption chiller. This leads to an increase in the number of these. Furthermore, the one-piece design of evaporator, refrigerant heat exchanger and refrigerant reservoir leads to material, weight and cost savings.

In summary, the formation of an absorption refrigerating machine with at least one plate heat exchanger results in itself or in total at least the following main advantages:

The use of a plate heat exchanger to expel refrigerant in the expeller leads to weight reduction and increased compactness of Absorptionskäl- temaschine. Here, the plate heat exchanger works in functional unit with a Reservoir and a separator. The interconnection is a system that is not forced through. In particular, the expulsion is stabilized by the open system consisting of expeller, storage tank and separator, since the coolant vapor expelled by the preheating is removed before the expeller, just like plate heat exchangers. Thus there is always just boiling solution at the entrance to the expeller. This subsequently leads to a stabilization of the entire cycle process. The use of the combination of a dephlegmator with a condenser increases the compactness of the absorption chiller and reduces necessary weld joints, weight, cost and pressure losses.

The same advantages are offered by a heat exchanger for the combination of refrigerant reservoir, refrigerant heat exchanger and evaporator. In addition, a heat input into the refrigerant heat exchanger and into the evaporator can be reduced. A filling amount of the refrigerant reservoir and thus its integration into the refrigerant heat exchanger whose fill level correspond to the required transfer area of the refrigerant heat exchanger in the case of different operating states of the absorption refrigerating machine with different capacities.

The absorber pre-cooler ensures that at low evaporator temperatures and high absorber temperatures, the absorption can be carried out with a higher degree of efficiency and thus increases the coefficient of performance of the absorption chiller. Since the mass flow is only divided into two partial mass flows.

The invention will be explained in more detail with reference to the embodiments illustrated in Figures 1 to 5. Showing:

FIG. 1 shows a schematic diagram of an absorption refrigerating machine,

2 shows a capacitor and dephlegmator combining plate heat exchanger in a schematic representation,

FIG. 3 shows a refrigerant heat exchanger, cold-storage reservoir and evaporator-combining plate heat exchanger,

Figure 4 shows the plate heat exchanger of Figure 3 in a schematic overview of functions

and

Figure 5 shows the expeller of the absorption chiller of Figure 1 in a schematic

Overview of functions.

1 shows the absorption chiller 1 in a schematic representation with the high-pressure region 2 and the low-pressure region 3 shown schematically. The absorption chiller 1 is operated in a thermodynamic cycle, wherein the externally supplied energy essentially takes place via the heating circuit 4, which can be fed by waste heat from heat-generating technical processes and combustion plants such as natural gas firing, solar thermal energy and the like. The thermodynamic cycle continues to output heat component amounts to the outside via the recooling circuits 5, 6. The cooling capacity of the absorption chiller is provided via the refrigeration cycle 7, which is for example by means of a brine in connection with an external air conditioner or the like. The thermodynamic cycle is carried out by means of a working substance consisting of a mixture of a refrigerant and a substance absorbing this, which emit heat when mixed and absorb heat when they are separated. In this case, the refrigerant is expelled through the various phases of the cycle from the absorbent in the gas phase, condensed in pure form and evaporated again and reunited with the absorbent. In this case, evaporation takes place at low temperature with removal of heat at the heat exchanger of the refrigeration cycle 7. Working substances are, for example, ammonia / water mixtures in which ammonia serves as a refrigerant and water as a solvent such as absorbent, aqueous lithium bromide solutions in which water as the refrigerant and lithium bromide serves as an absorbent, or the like. The following embodiment will be described with reference to a working substance of ammonia and water.

The description of the thermodynamic cycle is started at the transition of the ammonia-rich working substance from the low-pressure region 3 into the high-pressure region 2. Here, the ammonia-rich working substance is transferred via line 9 into the dephlegmator 10 by means of the preferably electrically operated working fluid pump 8. Between the working fluid pump 8 and the dephlegmator 10 takes place in the solvent heat exchanger 1 1, a heat exchange between the ammonia-rich working fluid of the line 9 and the recirculated in line 12 low-ammonia working fluid. In the dephlegmator 10, the ammonia-rich working substance is preheated by the guided in the line 13, expelled in the expeller 14 by supplying heat to the heating circuit 4 refrigerant vapor. To stabilize the expulsion in the expeller 14 of this, the feed tank 15 and the separator 16 are turned on. By preheating the ammonia-rich working substance in the dephlegmator 10 by the warmer refrigerant vapor enters this preheated in the expeller 14 a. At the same time, water entrained by the cooling of the refrigerant vapor in the dephlegmator 10 condenses with a high proportion of ammonia, which is supplied to the feed tank 15 by means of the line 64 and is thus utilized efficiently. Due to the open connection between container 15, expeller 14 and separator 16 adjusts itself in the sense of communicating tubes in this one level of the liquid solution. When a predetermined level is exceeded low ammonia working fluid flows into the separator 16 and from there in line 12. Then ammonia-rich working material from the master tank 15 is tracked in the expeller 14. The expeller 14 is in this case preferably designed as a plate heat exchanger 17, which is partially filled with ammonia-rich working fluid. Due to the large heat exchange surface of the plate heat exchanger 17 and the forming phase transition gas / liquid without forced flow due to the open formation of expeller 14, feed tank 15 and separator 16 a particularly effective expulsion of the refrigerant vapor is achieved. Furthermore, just as much ammonia-rich working substance is supplied to the expeller 14, as is promoted by desorption and the associated reduction in the density in the separator 16. Furthermore, 15 pulsations and delivery fluctuations of the working fluid pump 8 are compensated in the storage tank. Overall, this allows an improved stabilization of the entire absorption chiller 1 can be achieved. In the separator 16, the flow rate is reduced for example by cross-sectional widening of the conduit 18 and / or a baffle plate. By a surface enlargement in the separator 16, for example by Raschig rings and the like, a first deposition of entrained in the refrigerant vapor water.

The refrigerant vapor in the form of gaseous, only slightly contaminated with water ammonia enters via the line 19 from the dephlegmator 10 in the condenser 20 a. There, this is liquefied by removal of heat by means of the recooling circuit 5. The dephlegmator 10 and / or the condenser 20 may be formed as separate plate heat exchangers. In a particularly advantageous manner, the dephlegmator 10 and the condenser 20 are combined to form a unit forming plate heat exchanger 21. In this case, the plate heat exchanger 21 forms a triple heat exchanger, in which the refrigerant vapor is passed continuously and the dephlegmator 10 a first, cooled by the guided in the line 9 ammonia-rich working fluid cooling stage and the condenser 20 a second, through the recooling circuit. 5 cooled cooling stage forms. As a result, the structure of the absorption chiller 1 is simplified, since instead of a separate dephlegmator and a separate capacitor 20 only a single plate heat exchanger 21 with six connections and two end plates is necessary.

The condensed refrigerant is passed from the condenser 20 or from the plate heat exchanger 21 in the reservoir 22 and from there into the refrigerant Heat exchanger 23. In the refrigerant heat exchanger 23, a further cooling takes place by means of the now by the refrigerant expansion valve 24 in the

Low pressure range 3 transferred and behind the evaporator 25 in the conduit 26 through the refrigerant heat exchanger 23 guided gaseous refrigerant. In the low-pressure region 3, the refrigerant vaporizes in the evaporator 25 and thus removes heat from the working substance in the refrigeration cycle 7, for example a cooling brine, so that the actual cooling process such as room air conditioning, room cooling, cooling system and the like is initiated outside the absorption refrigeration machine 1. Advantageously, the refrigerant heat exchanger 23, the evaporator 25, the reservoir 22 and

10 summarizes the refrigerant expansion valve 24 to form a structural unit in the form of the plate heat exchanger 27. In this case, the volume of the plate heat exchanger 27 in the region of the refrigerant heat exchanger 23 is preferably expanded so that the reservoir 22 can be accommodated therein. Between the two regions assigned to the refrigerant heat exchanger 23 and the evaporator 25, the refrigerant

15 expansion valve 24 is arranged.

In the evaporator 25 and finally in the refrigerant heat exchanger 23, the refrigerant is completely evaporated and transported via the line 26 into the absorber 28. Here, for example, from WO 98/012487 A1 known absorption method of low ammonia working substance from the separator 16 via the

Solvent heat exchanger 1 1, the absorber precooler 29 and the solvent expansion valve 30 transported in the absorber 28 and the ammonia-poor working fluid and the refrigerant vapor combined to the ammonia-rich working fluid which is supplied via the line 32 and the reservoir 33 of the working fluid pump 8, whereby the cycle process running is held. The absorber 28 and the absorber precooler

25 29 are each separately cooled by means of the 3-way valve 34 from the recooling circuit 6, for example, cooling water and the like. Alternatively, the absorber precooler 29 can be cooled by a separate recooling plant. The controlled pre-cooling of the ammonia-lean working substance, the absorption can be controlled in an improved manner. The absorber precooler 29 is preferably in the form of plate heat

30 transformer formed and can with the solvent heat exchanger 1 1 form a unit to form a single plate heat exchanger 35 with two areas similar to the plate heat exchanger 21.

2 shows the plate heat exchanger 21 of Figure 1 in a schematic exploded view with the two end plates 36, 37 and arranged therebetween 35 separating plates 38, 39, 40, 41, 42. By appropriate arrangement of the partition plates 38, 39, 40, 41, 42, the separation is achieved in the dephlegmator 10 and in the condenser 20 of Figure 1 in terms of a triple heat exchanger. Here, the refrigerant vapor in the line 19 of Figure 1 along all the separator plates 38, 39, 40, 41, 42 from the port 43 to the port 44 is performed. The ammonia-rich agent for dephlegmation of the refrigerant vapor 5 is passed between the ports 45, 46 via the partition plates 41, 42. The recooling circuit 5 for condensing the refrigerant vapor to form the condenser 20 is guided between the connections 47, 48 via the separating plates 38, 39.

FIG. 3 shows a schematic exploded view and with reference to FIG. 1

10, the plate heat exchanger 27, which combines the function of the refrigerant heat exchanger 23 and the evaporator 25 in itself in the form of a 3-fold Wärnmeübertragers. The two end plates 49, 50 between them include the partition plates 51, 52, 53, 54, 55 a. The refrigerant flows along the refrigerant channel 65 over the entire plate heat exchanger 27. The refrigerant heat exchanger 23 is characterized by the between

15 plate 49 and the partition plates 51, 52 provided refrigerant channel 66 and the

Evaporator represented by the refrigerant channel 67 formed by the partition plates 54, 55 and the end plate 50. At the connection 56, the liquid refrigerant from the condenser 20 enters the plate heat exchanger 27 and exits again at the connection 57 in order to be discharged from the high-pressure region 2 into the low-pressure region via the refrigerant expansion valve 24.

20 area 3 to be transferred. Subsequently, the condensed refrigerant enters the plate heat exchanger 27 again at the connection 58 and is evaporated there and cools the condensed refrigerant at the separating plates 51, 52. Subsequently, the refrigerant vapor exits again at the port 59 and is then transferred to the absorber. Between the terminals 60, 61 and the partition plates 54, 55 circulates the

25 cooling brine of the refrigeration cycle 7. Within the volume of the partition plates 51, 52, the refrigerant reservoir 66 is still the reservoir 22 accommodated for the refrigerant.

FIG. 4 shows a schematic representation of a detail of the absorption chiller 1 of FIG. 1 with expeller 14, designed as a plate heat exchanger, the receiver tank 15, the separator 16 and the dephlegmator 10. In the dephlegmator

30 10 flows through the line 9 ammonia-rich working fluid, which is preheated by the guided in the conduit 13 refrigerant vapor. In the dephlegmator, ammonia-rich working substance is condensed out. As a result, water contaminants of the refrigerant vapor are conducted into the feed tank 15. The heated generator 14 drives from the ammonia-rich working water hydrous ammonia, ie refrigerant vapor from the

35 passed over the separator 16 and further purified by means of Raschigringe 62. The purified vaporous ammonia rises via the line 13 in the dephlegmator 10. The low-ammonia working substance is passed via the line 12 to the absorber.

5 shows a schematic representation of the plate heat exchanger 27 of Figures 1 and 3. In the plate heat exchanger 27 refrigerant heat exchanger 23 and evaporator 25 are combined. In the refrigerant heat exchanger 23 at the same time the reservoir 22 is housed for the condensed refrigerant. The level of the condensed refrigerant behaves proportional to the heat flow to be transferred in the refrigerant heat exchanger 23. In a large heat flow to be transmitted, due to a large temperature difference between gaseous refrigerant and condensed refrigerant, the level is high and thus the heat exchange surface is large, so that this heat flow can also be transmitted.

LIST OF REFERENCE NUMBERS

1 absorption chiller

2 high pressure area

3 low pressure area

5 4 heating circuit

5 recooling circuit

6 recooling circuit

7 refrigeration cycle

8 fluid pump

10 9 line

10 dephlegmator

1 1 Solvent heat exchanger

12 line

13 line

15 14 exporters

15 storage containers

16 separators

17 plate heat exchangers

18 line

20 19 pipe

20 capacitor

21 plate heat exchangers

22 reservoir

23 refrigerant heat exchangers

25 24 Refrigerant expansion valve

25 evaporator

26 line

27 plate heat exchangers

28 absorbers

30 29 Absorber precooler

30 solvent expansion valve

31 line

32 line

33 collection containers

35 34 3-way valve 35 plate heat exchangers

36 end plate

37 end plate

38 separating plate

5 39 Partition plate

40 separating plate

41 separating plate

42 separating plate

43 connection

10 44 Connection

45 connection

46 connection

47 connection

48 connection

15 49 end plate

50 end plate

51 separating plate

52 separating plate

53 separating plate

20 54 Partition plate

55 separating plate

56 connection

57 connection

58 connection

25 59 connection

60 connection

61 connection

62 Raschig rings

63 assembly

30 64 line

65 refrigerant channel

66 refrigerant channel

67 refrigerant channel

Claims

claims

1. absorption refrigeration machine (1) containing a guided in a cycle, depending on the cycle in different mixing ratios of a solvent and a refrigerant present working fluid, a high pressure area (2) with a refrigerant with heat from the solvent driving expeller (14) as a first component and an expelled refrigerant condensing condenser (20) as a second component, a low-pressure region (3) with a refrigerant evaporating heat removal evaporator (25) as a third component and an absorber (28) for absorbing refrigerant vapor in the solvent as the fourth component, a between high-pressure region (2) and low-pressure region (3) arranged refrigerant expansion valve (24) arranged between the high-pressure region and low-pressure region solvent expansion valve (30) and between the absorber (28) and expeller (14) arranged working fluid pump (8) sowi e optionally a dephlegmator (10) arranged between the expeller (14) and the condenser (5) as the fifth component and optionally a solvent heat exchanger (23) as the sixth component, characterized in that at least one component is used alone or in combination with at least one further component Plate heat exchanger (17, 21, 27, 35) is formed.

2. absorption chiller (1) according to claim 1, characterized in that between the absorber (28) and the expeller (14) a dephlegmator (10) with a between dephlegmator (10) and expeller (14) connected to the original container (15) is provided in which the dephlegmator (10) comprises a solvent-contaminated refrigerant vapor led via a separator (16) between the expeller (14) and the condenser (20) by means of a refrigerant-enriched refrigerant from the working fluid pump (8) to the expeller (14 ) cooled working fluid.

3. absorption chiller (1) according to claim 2, characterized in that between the separator (16) and the absorber (28), a solvent heat exchanger (1 1) between the refrigerant-enriched agent and a depleted of the refrigerant from the separator (16) via the

Solvent expansion valve (30) to the absorber (28) guided working material is provided.

4. absorption refrigeration machine (1) according to claim 3, characterized in that between the solvent heat exchanger (1 1) and the absorber (28) operated with a cold medium, compared to the depleted of the refrigerant agent effective Absorbervorkühler (29) is provided.

5. absorption chiller (1) according to claim 4, characterized in that the Absorbervorkühler (29) is designed as a plate heat exchanger.

6. absorption chiller (1) according to one of claims 1 to 5, characterized in that a dephlegmator (10) and the condenser (20) are formed as a common component in the form of a 3-fold heat exchanger.

7. absorption refrigeration machine (1) according to claim 6, characterized in that the triple heat exchanger is formed with a continuous refrigerant flow for the refrigerant channel and two along the refrigerant channel successively arranged channels of the dephlegmator (10) and the capacitor (20).

8. absorption chiller (1) according to one of claims 1 to 7, character- ized in that for the heat balance between a capacitor between

(20) and evaporator (25) guided refrigerant flow and a between capacitor (20) and absorber (28) guided refrigerant vapor a refrigerant heat exchanger (23) is provided.

9. absorption refrigerating machine (1) according to claim 8, characterized in that between the condenser (20) and the refrigerant heat exchanger (23) a

Reservoir (22) is provided.

10. absorption chiller (1) according to claim 8 or 9, characterized in that the evaporator (25), refrigerant heat exchanger (23) and reservoir (22) form a common triple heat exchanger.

1 1. Absorption refrigerating machine (1) according to claim 10, characterized in that the triple heat exchanger with a continuous flow for the refrigerant, from the refrigerant expansion valve (24) in the high pressure area (2) and the low pressure area (3) separated refrigerant channel (65) and two along the refrigerant channel (65) arranged one behind the other refrigerant channels (66, 67) of the refrigerant heat exchanger (23) and the evaporator (25) is formed.

12. absorption chiller (1) according to claim 1 1, characterized in that the refrigerant passage (66) of the Kältemittelwärmeübertragers (23) receives the reservoir (22).