CN1688853A

CN1688853A - Absorption refrigerating machine

Info

Publication number: CN1688853A
Application number: CNA038231395A
Authority: CN
Inventors: 井上修行; 入江毅一; 福住幸大
Original assignee: Ebara Corp
Current assignee: Ebara Refrigeration Equipment and Systems Co Ltd
Priority date: 2002-09-26
Filing date: 2003-09-25
Publication date: 2005-10-26
Anticipated expiration: 2023-09-25
Also published as: CN100449229C; CN100412466C; CN1975290A

Abstract

An efficient and compact absorption refrigerating machine using hot water of approx. 60 to 70 1/2 C as a heat source, comprising a regenerator (G), a condenser (C), an absorber (A), an evaporator (E), an auxiliary regenerator (GX), an auxiliary absorber (AX), a low temperature side heat exchanger (XL), and a high temperature side heat exchanger (XH), wherein the lower temperature side heat exchanger (XL) is formed so as to heat dense solution from the regenerator (G) by the auxiliary regenerator(GX) for further concentration and, while cooling dilute solution from the absorber (A), absorb refrigerant steam from the auxiliary regenerator (GX) and exchanges a heat between the dense solution led from the auxiliary regenerator (GX) to the absorber (A) and the dilute solution fed from the auxiliary absorber (AX) to the regenerator (G) and the high temperature side heat exchanger (XH) is formed so as to heat the dilute solution fed from the lower temperature side heat exchanger (XL) to the regenerator (G) with the dense solution led from the regenerator (G) to the auxiliary regenerator (GX).

Description

Absorption refrigerating machine

Technical field

The present invention relates to absorption refrigerating machine, particularly with the cooling residual heat (warm water of water jacket) of engine, the cooling residual heat of process of factory production, the lower warm water of warm water waste heat equitemperature that from boiler waste gas, reclaims, for example, with temperature be the absorption refrigerating machine of the warm water of 60～70 ℃ of degree as thermal source.

Background technology

Though being the waste heat of the ratio lower temperature of 60～70 ℃ of degree, the cooling residual heat equitemperature of the cooling residual heat of engine in actual life (warm water of water jacket), process of factory production exists in a large number, but because the temperature of these waste heats is lower, thereby it seldom is used, be directly or by cooling tower and indirectly that it is discarded mostly.

Is known with the warm water of discharging as the thermal source of heating, the absorption refrigerating machine of manufacturing cold water.The cooling water that Figure 14 makes 7 ℃ of degree of idle call with the cooling water of 30～31 ℃ of degree that cooling tower is formed as cooling source is an example, shows the single-action described with absorbing cycle period on the time-continuing process curve map.

Make the cold-producing medium evaporation by evaporimeter E, shown in the dotted line between the E-A among the figure, move, in absorber A, be absorbed.The weak solution that concentration has reduced is heated by the thermal source from the outside in regenerator G, emit and the cold-producing medium of evaporator evaporation with the refrigerant vapour of amount, turn back to absorber A through concentrating.At this moment, utilized the heat exchanger X (carrying out heat exchange) that is used for recuperation of heat at concentrated solution side X2 and weak solution side X1 place.Make the refrigerant vapour that is produced by regenerator G move shown in the dotted line between the G-C among the figure, C condenses by condenser, forms refrigerant liquid.This refrigerant liquid turns back to evaporimeter E from condenser C.

When evaporating temperature is that 5 ℃, absorber outlet temperature are 35 ℃, adiabatic condensation temperature when being 35 ℃ degree, the solution temperature of regenerator is 69～74 ℃ a degree, and the warm water inlet temperature that constitutes the thermal source of heating just must be 75 ℃ a degree.

That is, with in the absorption refrigerating machine, with the thermal source of 65～70 ℃ warm water as heating, then temperature is low excessively, can not make the cold water of 7 ℃ of degree in single-action.

And, the absorption refrigerating machine that a kind of secondary concentrated type is arranged on the market, it is can be with the warm water of the discharge about 60～65 ℃ thermal source as heating, and the cooling water of 30～31 ℃ of degree that will be formed by cooling tower is made the refrigerator of the cold water below 10 ℃ of idle call as cooling source.

Figure 15 shows the secondary concentrated type of describing and absorbs in the cycle period on the time-continuing process curve map, two regenerator GL, GH have the example under the situation that roughly the same area, two absorber AL, AH also have roughly the same area, that is the example of the cycle period of general area relationship.

Make the cold-producing medium evaporation by evaporimeter E, shown in the dotted line between the E-AL among the figure, move, in absorber AL, be absorbed.

The weak solution that concentration has reduced in low pressure regeneration device GL, is heated by the thermal source from the outside, emits the cold-producing medium that evaporated with the evaporimeter refrigerant vapour with amount, turns back to absorber AL through concentrating.At this moment, utilized the low-temperature side heat exchanger XL (carrying out heat exchange) that is used for recuperation of heat at concentrated solution side XL2 and weak solution side XL1 place.

On the other hand, the refrigerant vapour by low pressure regeneration device GL produces moves shown in the dotted line between the GL-AH among the figure, is absorbed in high pressure absorber AH.The weak solution that concentration has been reduced by high pressure absorber AH heats by the thermal source from the outside in high-pressure regeneration device GH, emit the cold-producing medium that produced with low pressure regeneration device GJ with the refrigerant vapour of cold-producing medium amount, that promptly evaporated with evaporimeter E, turn back to absorber AH through concentrating with amount.Utilized the h XH (carrying out heat exchange) of the recuperation of heat that is used for solution at concentrated solution side XH2 and weak solution side XH1 place.

The refrigerant vapour that is produced by high-pressure regeneration device GH is moved shown in the dotted line between the GH-C among the figure, and C condenses by condenser, forms refrigerant liquid, and this refrigerant liquid turns back to evaporimeter E from condenser C.

As mentioned above, the constitution equipment of secondary concentrated type absorption refrigerating machine is more, install huger, and must produce the same refrigerant vapour of measuring of the refrigerant vapour that is produced with evaporimeter E with high-pressure regeneration device GH and low pressure regeneration device GL secondary, make the thermal efficiency be reduced to common single-action and use below half of type absorption refrigerating machine, thereby be seldom adopted refrigerator in the reality.

And, though the adsorption type freezing machine of the refrigerator that a kind of conduct just can turn round about 65 ℃ discharge warm water as the thermal source of heating is arranged, and huger than secondary concentrated type absorption refrigerating machine owing to this device, price is higher, and hot high pressure efficient is lower again, thereby almost can not use.

Also have the absorption refrigerating machine of a kind of conduct between single-action usefulness type absorption refrigerating machine and secondary concentrated type absorption refrigerating machine, this absorption refrigerating machine is provided with the absorber and the regenerator (Figure 16) of high pressure and low pressure.In this absorption refrigerating machine, although littler and the thermal efficiency is also better than the structure of above-mentioned secondary concentrated type absorption refrigerating machine to a certain extent, but wish to have the better absorption refrigerating machine of a kind of thermal efficiency.

In Figure 16, make the cold-producing medium evaporation by evaporimeter E, shown in the dotted line between the E-A among the figure, move, in absorber A, be absorbed.The absorber outlet weak solution that concentration has been reduced is transported to auxilliary absorber AX, and when cool off by this auxilliary absorber AX, absorption is from the refrigerant vapour (moving shown in the dotted line between the GX-AX among the figure) of above-mentioned auxiliary regenerator GX.

And then, the weak solution from auxilliary absorber AX that thins out is transported to above-mentioned regenerator G, in this regenerator, heat concentrated by thermal source from the outside.The refrigerant vapour that is produced is moved shown in the dotted line between the G-C among the figure, condensed and become refrigerant liquid by above-mentioned condenser C, this refrigerant liquid turns back to evaporimeter E from condenser C.On the other hand, the solution that has been concentrated by regenerator G is heated concentratedly in the auxiliary regenerator GX again by external heat source, turn back to absorber A.The refrigerant vapour that produces moves shown in the dotted line between the GX-AX among the figure, is absorbed in auxilliary absorber AX.

In the solution recycle system of this cycle period, be used for solution is transported to from absorber A the solution pump of the high auxilliary absorber AX of pressure ratio absorber, and to be used for solution be essential from the solution pump that auxilliary absorber AX is transported to regenerator G, and, in order to be transported to regenerator G from whole amounts of auxilliary absorber AX, must carry out the balance control of liquid inventory, this makes system become complicated.

Promptly, when the amount that is transported to regenerator from auxilliary absorber is very few, solution will remain in the auxilliary absorber, the solution amount of regenerator → auxiliary regenerator → absorbers combination is tailed off, finally, the solution pump that is transported to auxilliary absorber from absorber causes cavitation erosion owing to solution amount is not enough, and it can not be turned round.On the other hand, when the amount that is transported to regenerator from auxilliary absorber was too much, because the solution amount deficiency of auxilliary absorber, the solution pump that is transported to regenerator from auxilliary absorber will cause cavitation erosion, thereby it can not be turned round.Therefore, must control etc., make the liquid inventory balance of turnover of auxilliary absorber.

The present invention makes in view of above-mentioned prior art, its objective is provide a kind of to heat exchanger be provided with that improvement has been carried out in the position, efficient is higher and also compact conformation, can be with the warm water of 60～70 ℃ of degree absorption refrigerating machine as thermal source.

Summary of the invention

In order to achieve the above object, as shown in Figure 1, absorption refrigerating machine of the present invention is provided with: produce refrigerant vapour and make the regenerator G of solution concentration; The condenser C that the refrigerant vapour of above-mentioned generation is condensed; Make the evaporimeter E of above-mentioned cold-producing medium evaporation of condensing; By the absorber A of solution with the refrigerant vapour absorption of above-mentioned evaporation; The auxiliary regenerator GX that will heat from the concentrated solution of above-mentioned regenerator G and produce refrigerant vapour and further concentrate; To cool off from the weak solution of above-mentioned absorber A, and the auxilliary absorber AX that will absorb by the refrigerant vapour that above-mentioned auxiliary regenerator GX is produced; In the concentrated solution that imports to above-mentioned absorber A from above-mentioned auxiliary regenerator GX be transported to the low-temperature side heat exchanger XL that carries out heat exchange between the weak solution of above-mentioned regenerator G from above-mentioned auxilliary absorber AX; By being directed into the concentrated solution of above-mentioned auxiliary regenerator GX from above-mentioned regenerator G output, to from above-mentioned low-temperature side heat exchanger XL output and be transported to the h XH that the weak solution of above-mentioned regenerator G heats.

And absorption refrigerating machine also can be, have: produce refrigerant vapour and make the regenerator G of solution concentration; The condenser C that the refrigerant vapour of above-mentioned generation is condensed; Make the evaporimeter E of above-mentioned curdy cold-producing medium evaporation; By the absorber A of solution with above-mentioned vaporized refrigerant vapour absorption; The auxiliary regenerator GX that will heat from the concentrated solution of above-mentioned regenerator G and produce refrigerant vapour and further concentrate; To cool off from the weak solution of above-mentioned absorber A, and the auxilliary absorber AX that will absorb by the refrigerant vapour that above-mentioned auxiliary regenerator GX is produced; Wherein the heat transfer area of above-mentioned auxiliary regenerator GX is set at below 1/3 of heat transfer area of above-mentioned regenerator G, the heat transfer area of above-mentioned auxilliary absorber AX is set at below 2/3 of heat transfer area of above-mentioned absorber A.

And for example as shown in Figure 7, absorption refrigerating machine also can have: produce refrigerant vapour and make the regenerator G of solution concentration; The condenser C that the refrigerant vapour of above-mentioned generation is condensed; Make the evaporimeter E of above-mentioned curdy cold-producing medium evaporation; By the absorber A of solution with the refrigerant vapour absorption of above-mentioned evaporation; To heat from the concentrated solution of above-mentioned regenerator G and the generation refrigerant vapour, and the auxiliary regenerator GX that further concentrates; Will be from the cooling of the weak solution of above-mentioned absorber A, and the auxilliary absorber AX of the refrigerant vapour absorption that will above-mentioned auxiliary regenerator GX be produced; Above-mentioned solution arrives the circulating

path

1,2,3,4 of above-mentioned absorber A according to order process above-mentioned auxilliary absorber AX, the above-mentioned regenerator G that mentions, above-mentioned auxiliary regenerator GX from above-mentioned absorber A; The mechanism of at least one side among the VGH of mechanism, the VGS that the heat-transfer capability of above-mentioned auxiliary regenerator GX is adjusted and the VAW of mechanism, the VAS that the heat-transfer capability of above-mentioned auxilliary absorber AX is adjusted.

And for example as shown in Figure 9, absorption refrigerating machine also can have: produce refrigerant vapour and make the regenerator G of solution concentration; The condenser C that the refrigerant vapour of above-mentioned generation is condensed; Make the evaporimeter E of above-mentioned curdy cold-producing medium evaporation; By the absorber A of solution with the refrigerant vapour absorption of above-mentioned evaporation; To heat from the concentrated solution of above-mentioned regenerator G and the generation refrigerant vapour, and the auxiliary regenerator GX that further concentrates; Weak solution is cooled off, and absorb the auxilliary absorber AX of the refrigerant vapour that is produced by above-mentioned auxiliary regenerator GX, wherein this auxilliary absorber AX is constituted as above-mentioned absorber A outlet weak solution is used as above-mentioned weak solution with the part that this auxilliary absorber AX exports the mixing weak solution of weak solution; The remainder of above-mentioned mixing weak solution is transported to the path 2 of above-mentioned regenerator G; On above-mentioned path 2, the low-temperature side heat exchanger XL that above-mentioned mixing weak solution is heated by the concentrated solution that imports to above-mentioned absorber A from above-mentioned auxiliary regenerator GX in turn; Concentrated solution by importing to above-mentioned auxiliary regenerator GX from above-mentioned regenerator G is to above-mentioned low-temperature side heat exchanger XL output and be transported to the h XH that the mixing weak solution of above-mentioned regenerator G heats.

And, for example as Fig. 5 or shown in Figure 12, also above-mentioned absorber A can be distinguished into low-pressure absorber AL and high pressure absorber AH, above-mentioned evaporimeter E is distinguished into low pressure evaporator EL and high pressure evaporator EH, cold water 10 is at first imported to above-mentioned high pressure evaporator EH, then, chilled cold water 10 is imported to above-mentioned low pressure evaporator.And, for example as shown in Figure 5, also can constitute, to at first import to above-mentioned low-pressure absorber AL from the concentrated solution of above-mentioned auxiliary regenerator GX, absorption is from the refrigerant vapour of above-mentioned low pressure evaporator EL, to import to above-mentioned high pressure absorber AH by the solution that above-mentioned low-pressure absorber AL has absorbed refrigerant vapour, absorb refrigerant vapour, the weak solution that has absorbed this refrigerant vapour will be imported to above-mentioned auxilliary absorber AX from above-mentioned high pressure evaporator EH; Perhaps as shown in figure 12, also can constitute the concentrated solution from above-mentioned regenerator GX is at first imported to above-mentioned low-pressure absorber AL, absorption is from the refrigerant vapour of above-mentioned low pressure evaporator EL, to import to above-mentioned high pressure absorber AH by the solution that above-mentioned low-pressure absorber AL has absorbed refrigerant vapour, absorption is from the refrigerant vapour of above-mentioned high pressure evaporator EH, a part that the above-mentioned high pressure absorber AH that has absorbed this refrigerant vapour is exported the mixing weak solution of weak solution and above-mentioned auxilliary absorber AX outlet weak solution is transported to above-mentioned auxilliary absorber AX, and remainder is transported to above-mentioned regenerator G.

The application is based on the September 26th, 2002 of patent application 2003-166181 number in application on June 11st, patent application 2002-280112 number 1 of application on September 26th, patent application 2002-280111 number 1 of Japanese publication, and the content of these applications forms the application's a part as the application's content.

In addition, can understand the present invention more completely by following detailed description.According to following detailed description, can be clearer and more definite to range of application of the present invention.But detailed explanation and certain embodiments are preferred forms of the present invention, are to put down in writing for illustrative purposes.This is that those skilled in the art can be well understood to all changes in the scope of theme of the present invention and claim, the scheme of change because from these detailed explanations.

The applicant does not really want to present the embodiment that any one is put down in writing to the public, in all change schemes that are disclosed, the alternative, perhaps on literal, be not comprised in the application's the claim scope, but consider from the viewpoint that is equal to mutually, all should be as a part of the present invention.

Description of drawings

Fig. 1 is the fluidal texture figure of the absorption refrigerating machine of expression the present invention the 1st embodiment.

Fig. 2 is the time-continuing process curve map of solution cycle period shown in Figure 1.

Fig. 3 is the refrigerant vapour amount of movement and the warm water inlet temperature of necessity, the chart of the relation between the COP between the expression GX-AX shown in Figure 1.

Fig. 4 is the chart of the relation between the cooling water inlet temperature of refrigerant vapour amount of movement between the expression GX-AX shown in Figure 1 and warm water inlet temperature.

Fig. 5 is the fluidal texture figure of the absorption refrigerating machine of expression the present invention the 2nd embodiment.

Fig. 6 is the time-continuing process curve map of solution cycle period shown in Figure 5.

Fig. 7 is the fluidal texture figure of the absorption refrigerating machine of expression the present invention the 3rd embodiment.

Fig. 8 (a) and (b) are with the time-continuing process curve map after the solution cycle period shown in Figure 7 partial alteration.

Fig. 9 is the fluidal texture figure of the absorption refrigerating machine of expression the present invention the 4th embodiment.

Figure 10 is the fluidal texture figure of the absorption refrigerating machine of expression the present invention the 5th embodiment.

Figure 11 is the time-continuing process curve map with respect to the solution cycle period of Fig. 9.

Figure 12 is the summary construction diagram of the absorption refrigerating machine of expression the present invention the 6th embodiment.

Figure 13 is the time-continuing process curve map with respect to the solution cycle period of Figure 12.

Figure 14 is the time-continuing process curve map of single-action with the absorption cycle period.

Figure 15 is the time-continuing process curve map that the secondary concentrated type absorbs cycle period.

Figure 16 is the time-continuing process curve map that known secondary concentrated type is absorbed the cycle period that cycle period that cycle period is divided into 2 systems connected.

The specific embodiment

Below, explain the present invention with reference to accompanying drawing.Although described below is the expression embodiments of the present invention, scope of the present invention is not limited to these embodiments.

Among Fig. 1, E is that evaporimeter, A are that absorber, G are that regenerator, C are that condenser, AX are that auxilliary absorber, GX are that auxiliary regenerator, XL are that low-temperature side heat exchanger, XH are that h, SP are that solution pump, RP are that refrigerated medium pump, V1 are triple valves, 1～4th, solution stream, the 5th, refrigerant vapour stream, 6, the 7th, refrigerant flow path, the 8th, warm water, the 9th, cooling water, the 10th, cold water.

In the present embodiment, evaporimeter E is formed in the same space with absorber A by means of arrester (エリミネ one ).Equally, regenerator G is formed in another the same space with condenser C by means of arrester.Auxilliary absorber AX, auxiliary regenerator GX, low-temperature side heat exchanger XL, h XH are respectively formed at separately independently in the tank body.

In evaporimeter E,, refrigerated medium pump RP is inserted be configured in the refrigerant flow path 7 that makes the cold-producing medium circulation for cold-producing medium being dispersed in the pipeline that cold water 10 flows.

Auxilliary absorber AX is being connected by solution stream 2 with regenerator G, solution stream 2 is used for weak solution is transported to regenerator G from auxilliary absorber AX, in its way, low-temperature side heat exchanger XL and h XH according to mentioned arranged in order, between auxilliary absorber AX and low-temperature side heat exchanger AX, insert and disposing solution pump SP.

And absorber A is being connected by solution stream 1 with auxilliary absorber AX, and solution stream 1 is used for weak solution is transported to auxilliary absorber AX from absorber A.

Regenerator G is being connected by solution stream 3 with auxiliary regenerator GX, and solution stream 3 is used for concentrated solution is transported to auxilliary absorber GX from regenerator G, inserts in solution stream 3 and is disposing h XH.

Auxiliary regenerator GX is being connected by solution stream 4 with absorber A, and solution stream 4 is used for solution is transported to absorber A from auxiliary regenerator GX, inserts in solution stream 4 and is disposing low-temperature side heat exchanger XL.

And auxiliary regenerator GX is being connected by refrigerant vapour stream 5 with auxilliary absorber AX, and refrigerant vapour stream 5 is used for refrigerant vapour is transported to auxilliary absorber AX from auxiliary regenerator GX.

Between condenser C and evaporimeter E, the refrigerant flow path 6 that cold-producing medium is transported to evaporimeter E from condenser C is being set.

Laying the warm water pipeline 81 that flows through warm water 8 from regenerator G to auxiliary regenerator GX, warm water 8 is as the heat source fluid of heated solution.This warm water 8 flows into regenerator G earlier by warm water pipeline 81, relends and helps warm water pipeline 81 and the auxiliary regenerator GX of inflow.

On the outlet side of the auxiliary regenerator GX of warm water pipeline 81, triple valve V1 is being set, be used for regulating by the warm water amount of auxiliary regenerator GX.Triple valve V1 also can be arranged on the entrance side of auxiliary regenerator GX of warm water pipeline 81.

Cooling water pipeline 91 as the cooling water 9 of the cooling medium that solution is cooled off is flow through is routed to condenser C, lays to auxilliary absorber XA then from absorber A.Cooling water 9 flow into absorber A earlier by cooling water pipeline 91, relends to help cooling water pipeline 91 and flow to condenser C, flow into auxilliary absorber AX then.

In absorption refrigerating machine shown in Figure 1, when the concentrated solution that imports to absorber A is cooled water 9 coolings, absorb the refrigerant vapour of flash-pot E, become weak solution.Weak solution from absorber A is directed to auxilliary absorber AX from stream 1, when being cooled off by cooling water, absorbs the refrigerant vapour from stream 5 that is produced by auxiliary regenerator GX, and then becomes the lower weak solution of concentration.

Boost by solution pump SP from the weak solution that auxilliary absorber AX discharges, enter into low-temperature side heat exchanger XL from stream 2, in low-temperature side heat exchanger XL, carry out heat exchange with the concentrated solution that stream 4 flows to absorber A of passing through from auxiliary regenerator GX, the weak solution temperature rises, on the other hand, the temperature of concentrated solution descends.Then, in h XH, weak solution with carry out heat exchange from the concentrated solution of the auxiliary regenerator GX of the flow direction of regenerator G, the temperature of weak solution further rises, on the other hand, the temperature of concentrated solution descends.

In regenerator G, solution is heated by the warm water 8 as thermal source, produces refrigerant vapour and is concentrated.The concentrated solution that has been concentrated from stream 3 through the heated side of h XH and enter into auxiliary regenerator GX, heat and the generation steam by warm water 8 as thermal source, further be concentrated, pass through the heated side of low-temperature side heat exchanger XL and be directed to absorber A from stream 4, so far, finished one and taken turns the solution cycle period.

In evaporimeter E, cold-producing medium utilizes evaporation latent heat that cold water 10 is cooled off, and becomes refrigerant vapour, is absorbed in the solution of absorber A.The refrigerant vapour that is produced by regenerator G by cooling water 9 coolings, becomes refrigerant liquid and is directed to evaporimeter E from stream 6 in condenser C.

With respect to the cycle period that secondary concentrated type absorption cycle period is divided into 2 systems (Figure 15) in the past, above-mentioned solution cycle period is the cycle period that circulates in 1 system, and the heat energy of the concentrated solution that is heated by auxiliary regenerator GX, the weak solution that flows to regenerator G from auxilliary absorber A, be recovered, and the heat energy of the concentrated solution that is heated by regenerator G in above-mentioned weak solution by further recuperation of heat.

Below, the cycle period on the time-continuing process curve map of use Fig. 2 describes.

The solution cycle period relative with Fig. 1 is indicated on the time-continuing process curve map of Fig. 2.

Present embodiment descends in order to make necessary warm water temperature, utilizes auxiliary regenerator GX and auxilliary absorber AX that cycle period concentration is changed.If set the heat transfer area of auxiliary regenerator GX and auxilliary absorber AX also is fine by the warm water temperature of correspondence.The heat transfer area of shown in Figure 2 is auxiliary regenerator GX be about regenerator G heat transfer area 5%, the heat transfer area of auxilliary absorber AX is about 20% o'clock example of the heat transfer area of absorber A.

In auxiliary regenerator GX,, thereby will assist the heat transfer area of regenerator GX to dwindle because heat source temperature and solution temperature differ bigger.And, according to this temperature relation, making the inlet that is directed to regenerator G as the warm water high temperature side of thermal source, the low temperature side of the outlet of regenerator G is auxiliary regenerator GX, preferably makes warm water import regenerator G earlier, then imports auxiliary regenerator GX.

Make the cold-producing medium evaporation by evaporimeter E, shown in the dotted line between the E-A among Fig. 2, move, in absorber A, be absorbed.

The solution of discharging from absorber A flow into the auxilliary absorber AX with original temperature, concentration, absorbs the GX from Fig. 2 that is produced by auxiliary regenerator GX and moves to the refrigerant vapour of AX, and become the lower weak solution of concentration.This weak solution is heated side XL1 by low-temperature side heat exchanger XL's, by being heated through the concentrated solution that the heated side XL2 of low-temperature side heat exchanger is directed to the absorber A from auxiliary regenerator GX.This weak solution further by h XH be heated side XH1, by being directed to after concentrated solution the auxiliary regenerator GX is heated through the heated side XH2 of h XH, flow into regenerator G from regenerator G.In regenerator G, emit the refrigerant vapour of the refrigerant amount that absorbs by absorber A, become concentrated solution, pass through the heated side XH2 of h XH and flow into and assist among the regenerator GX, heated by external heat source, emit the suitable part of refrigerant amount that is absorbed with auxilliary absorber AX, after further being concentrated, flow among the absorber A through the heated side XL2 of low-temperature side heat exchanger XL.

Like this, in the present embodiment, flow to the potentiality heat of the concentrated solution of absorber A from auxiliary regenerator GX, not to be recovered to flow to the weak solution of auxilliary absorber AX but be recovered to flow to the weak solution of regenerator G, but also the potentiality heat that flows to the concentrated solution of auxiliary regenerator GX from regenerator G is reclaimed from auxilliary absorber AX from absorber A.By this recuperation of heat, the solution temperature that flow into regenerator G is improved, can reduce the necessary heat of heated solution on regenerator G, and, can also make the solution temperature that flow into auxiliary regenerator GX through h heated side XH2, with be not heated side XL2 the situation that the weak solution that flows to regenerator G from auxilliary absorber AX heats compared rising by low-temperature side heat exchanger, can reduce the solution among the auxiliary regenerator GX is heated needed heat.

Fig. 3 and Fig. 4 are the charts that concerns between refrigerant vapour amount of movement between the auxiliary regenerator GX-auxilliary absorber AX of expression and the warm water inlet temperature.

The refrigerant vapour amount that is produced, absorbed by auxilliary absorber AX by auxiliary regenerator GX is the part that efficient reduces with absorption refrigerating machine than single-action, and is if this vapor volume is zero, then suitable with absorption refrigerating machine with single-action; If when identical, then become and the suitable efficient of secondary concentrated type absorption refrigerating machine with the evaporation capacity that evaporates by evaporimeter E.And, by this auxiliary regenerator GX generation, by the refrigerant vapour amount that auxilliary absorber AX absorbs cycle period concentration is changed by above-mentioned, the heat hot source temperature that needs is changed.Fig. 3 is the figure of this relation of expression.This figure will assist the heat transfer area of regenerator GX to get approximately to be regenerator G heat transfer area 15%, with the heat transfer area of auxilliary absorber AX get into about be absorber A heat transfer area 50%, the heat-transfer capability of regenerator G has been applied restriction and the refrigerant vapour amount is changed.

If heat source temperature is 65～70 ℃ a degree for example, the refrigerant vapour amount that moves between auxiliary regenerator GX-auxilliary absorber AX is just passable by half degree of the amount of evaporator evaporation, therefore, when absorption refrigerating machine being designed with this condition, just can below the size of auxiliary regenerator GX, auxilliary absorber AX being got into half of regenerator G, absorber A respectively, energy forms also compacter than the situation of secondary concentrated type absorption refrigerating machine, and efficient is improved.

With the heat transfer area of auxiliary regenerator GX get become be regenerator G heat transfer area 1/3, particularly get about 20%, with the heat transfer area of auxilliary absorber AX get become be absorber A heat transfer area 2/3, particularly get about 60% degree, this makes that the absorber exit concentration is lower than regenerator exit concentration, efficient also than cycle period separated the concentrated type of secondary completely absorption refrigerating machine much better.

When cooling water temperature is reduced, obtain the needed solution concentration of identical cold water temperature and reduce, the needed heat source temperature of solution concentration reduces.Needed warm water temperature when Fig. 4 is illustrated in cooling water temperature and changes.Therefore, the heat source temperature that promptly enables to supply with is identical, and under the situation that cooling water temperature reduces, the refrigerant vapour amount that is absorbed by auxilliary absorber A that auxiliary regenerator GX is produced reduces, and efficient is improved.

If the triple valve V1 that for example is provided with as shown in Figure 1 is used for the warm water amount that imports to auxiliary regenerator GX is regulated, the refrigerant vapour amount that is then produced by auxiliary regenerator GX, absorbed by auxilliary absorber AX can be regulated.In addition, also can in addition bypass of the part of the liquid inventory of auxiliary regenerator GX～all will be flowed to, the vapor volume of generation is changed to some extent, perhaps will flow to a part～all bypasses in addition of the liquid inventory of auxilliary absorber AX, the vapor volume of absorption is changed to some extent.The cooling water flow that flows to auxilliary absorber AX is changed to some extent.

In the present embodiment, adjusting by the refrigerant vapour amount that auxiliary regenerator GX is produced, absorb by auxilliary absorber AX, can make from secondary concentrated type absorption cycle period and change continuously with the efficient that absorbs cycle period to single-action, under the situation that warm water temperature rises, perhaps under the situation such as cooling water temperature reduction, can effectively utilize these measures, efficient is improved.

Among Fig. 5, the symbol identical with Fig. 1 has identical implication, and among Fig. 5, poor for the gateway temperature of utilizing cold water further improved efficient, and the absorber A of above-mentioned absorption refrigerating machine is distinguished into low-pressure absorber AL and high pressure absorber AH; Evaporimeter E is distinguished into low pressure evaporator EL and high pressure evaporator EH.Low-pressure absorber AL and low pressure evaporator EL are formed in the same space by means of arrester; And high pressure absorber AH and high pressure evaporator EH are formed in another the same space by means of arrester.

Cooling water pipeline 91 is to be laid to flow into abreast among low-pressure absorber AL and the high pressure absorber AH, and cold water pipes 10a in series is laid to according to mentioned order flow into low pressure evaporator EL from high pressure evaporator EH.

And solution stream 4 is to be laid to from auxiliary regenerator GX to arrive low-pressure absorber AL through low-temperature side heat exchanger XL.Then, be laid to and make solution import to high pressure absorber AH from low-pressure absorber AL.

In the present embodiment, cold water 10 at first is directed to high pressure evaporator EH, then, the cold water 10 that is cooled is imported to low pressure evaporator EL, and, at first be directed to low-pressure absorber AL from the concentrated solution of auxiliary regenerator GX, the refrigerant vapour from low pressure evaporator EL is absorbed, to import to high pressure absorber AH by the solution that low-pressure absorber AL has absorbed refrigerant vapour, the refrigerant vapour from high pressure evaporator EH is absorbed.

Absorbed the solution of refrigerant vapour by high pressure absorber AH, pass through auxilliary absorber AX from stream 1, be transported to regenerator G from stream 2 through low-temperature side heat exchanger XL, h XH, the solution that has concentrated by regenerator G, import to auxiliary regenerator GX from stream 3 through h XH, import to low-pressure absorber AL from stream 4 through low-temperature side heat exchanger XL again.

Fig. 6 shows the solution cycle period with respect to Fig. 5 on the time-continuing process curve map.The saturation temperature of high pressure evaporator EH increases, and the weak solution concentration that high pressure absorber AH emits reduces.

Like this, can reduce with auxilliary absorber AX making the further needed refrigerant amount of decline of concentration, comparing with situation shown in Figure 1 to make efficient improve.

In Fig. 7, be with the difference of the 1st embodiment of Fig. 1 explanation, be provided with flow control valve VGH, VGS, VAW, VAS.In the present embodiment, these members are triple valves.

The triple valve V1 that illustrates in flow control valve VGH and the 1st embodiment similarly is configured on the warm water pipeline 81.

Flow control valve VGS is configured on the solution stream 3 that connects h XH and auxiliary regenerator GX, and 1 mouth of triple valve VGS is connected with the solution stream 4 that is being connected auxiliary regenerator GX and low-temperature side heat exchanger XL.

Flow control valve VAW is arranged on the outlet side of the auxilliary absorber AX of cooling water pipeline 91.Triple valve VAW also can be arranged on the entrance side of the auxilliary absorber AX of cooling water pipeline 91.

Flow control valve VAS is configured on the solution stream 1 that connects absorber A and auxilliary absorber AX, 1 mouth of triple valve VAS is connected between the auxilliary absorber AX and solution pump SP of solution stream 2, and this solution stream 2 is connecting auxilliary absorber AX and low-temperature side heat exchanger XL.

The time-continuing process cycle period of present embodiment is identical with the time-continuing process cycle period of Fig. 1 explanation.

Fig. 8 represents the time-continuing process cycle period of the modified example of the 3rd embodiment.Shown in Fig. 8 (a), though sacrificed some efficient, omitted low-temperature side heat exchanger XL, can make structure compact more.In addition, shown in Fig. 8 (b), also can make the side XL1 that is heated of low-temperature side heat exchanger XL is the weak solution that flows to auxilliary absorber from absorber.

The refrigerant vapour amount of movement between the auxiliary regenerator GX-auxilliary absorber AX and the relation of warm water inlet temperature are as illustrated in the 1st embodiment.

And, identical with the 1st embodiment, if the triple valve VGH that is used for regulating the warm water amount that is directed to auxiliary regenerator GX as shown in Figure 7 for example is set, the refrigerant vapour amount that is then produced by auxiliary regenerator GX, absorbed by auxilliary absorber AX can be regulated.And, by utilizing solvent valve VGS shown in Figure 7, to flow to a part and even all in addition bypasses of the liquid inventory of auxiliary regenerator GX shown in dotted linely, just can the vapor volume that produce be limited, refrigerant vapour amount mobile between the GX-AX is changed to some extent.In addition, with cooling water valve VAW shown in Figure 7, make a cooling water flow part that flows to auxilliary absorber AX or utilize solvent valve VAS shown in Figure 7, make the liquid inventory that flows to auxilliary absorber AX because of a part and even all changed to some extent by bypass, just can the vapor volume that absorb be limited, the refrigerant vapour amount that moves between the GX-AX is changed to some extent.

In the present embodiment, regulate by the refrigerant vapour amount that auxiliary regenerator GX is produced, absorb by auxilliary absorber AX, just can make from secondary concentrated type absorption cycle period and change continuously with the efficient that absorbs cycle period to single-action, under the situation that warm water temperature rises or under the cooling water temperature under the degradation situation, can effectively utilize these measures and efficient is improved.

Fig. 9 is the summary construction diagram of the absorption refrigerating machine of expression the present invention the 4th embodiment.

As shown in Figure 9, contain in the refrigerator structure of present embodiment: evaporimeter E, absorber A, regenerator G, condenser C, auxilliary absorber AX, auxiliary regenerator GX and low-temperature side heat exchanger XL, h XH.

The difference of present embodiment and the 1st embodiment is, be inhaled into solution pump SP after the solution stream 1a that draws from absorber A and the solution stream 2a interflow of drawing, and the solution stream 1b that flows to auxilliary absorber AX is a branch from the solution stream 2 of being drawn by the outlet of solution pump SP from auxilliary absorber AX.

In such structure, the concentrated solution that is directed among the absorber A is cooled off at the water 9 that is cooled, and absorbs the refrigerant vapour of flash-pot E simultaneously, becomes weak solution.From the weak solution of absorber A with boosting by solution pump SP from the weak solution of auxilliary absorber AX and becoming the state of mixing.Import to auxilliary absorber AX in the part that will mix weak solution, absorb the refrigerant vapour that is produced by auxiliary regenerator GX when cooling off, become the lower weak solution of concentration by cooling water 9.

The mixing weak solution of the remainder that has been boosted by solution pump SP enters into low-temperature side heat exchanger XL, in low-temperature side heat exchanger XL, carry out heat exchange with the concentrated solution that flows to absorber A from auxiliary regenerator GX, the temperature of mixing weak solution is risen, on the other hand, the temperature of concentrated solution reduces.Mix weak solution and enter into h XH subsequently, carry out heat exchange with the concentrated solution that flows to auxiliary regenerator GX from regenerator D in h XH, the temperature of mixing weak solution further rises, and on the other hand, the temperature of concentrated solution descends.In regenerator G, solution is by as the heating of the warm water of thermal source, produces refrigerant vapour and is concentrated.The concentrated solution that has been concentrated is through the heated side of h XH and enter into auxiliary regenerator GX, heat and the generation refrigerant vapour by warm water as thermal source, further be concentrated, pass through the heated side of low-temperature side heat exchanger XL and import to absorber A, finish one and take turns the solution cycle period.In evaporimeter E, cold-producing medium utilizes evaporation latent heat and cold water is cooled off, and becomes refrigerant vapour, and the solution that is absorbed device A absorbs.The refrigerant vapour that is produced by regenerator G by cooling water 9 coolings, becomes cold-producing medium and is directed to evaporimeter E in condenser C.

This solution cycle period is characterised in that, the cycle period that is divided into 2 systems (Figure 15) with the concentrated cycle period of secondary in the past is relative, this solution cycle period is circulated by 1 system, and, by the energy recovery of the auxiliary warmed-up concentrated solution of regenerator GX to flowing to the weak solution of regenerator G from auxilliary absorber AX, by the energy recovery of the warmed-up concentrated solution of regenerator G in above-mentioned weak solution.

In single-action usefulness and the cycle period between the secondary concentrated type in the past, in solution recycle system, the solution pump of the solution pump of absorber outlet and auxilliary absorber outlet is essential, and must carry out balance control to the liquid inventory that passes in and out in the auxilliary absorber.

In the cycle period of present embodiment, owing to be not transported to regenerator G from the solution of auxilliary absorber AX, but be transported to the lower absorber A outlet side of pressure from auxilliary absorber AX, thereby just do not need the solution pump of auxilliary absorber AX outlet.

And, as long as it is just passable that solution is flowed out from auxilliary absorber AX outlet, do not have obstruction even do not carry out flow equilibrium control especially yet, can make compact conformation.

Figure 11 is the cycle period on the time-continuing process curve map, shows the solution cycle period with respect to Fig. 9 on the time-continuing process curve map.

In the refrigerant vapour amount of movement between auxiliary regenerator GX-auxilliary absorber AX, produced, be efficient than single-action with the low part of absorption refrigerating machine by auxiliary regenerator GX by the refrigerant vapour amount of auxilliary absorber AX absorption, if this vapor volume is zero, then be equivalent to the efficient of single-action with absorption refrigerating machine, if the evaporation capacity among itself and the evaporimeter E then becomes the efficient suitable with the secondary concentrated type with amount.

That is, when the refrigerant vapour amount that is produced, absorbed by auxilliary absorber AX by auxiliary regenerator GX reduces, the efficient rising of refrigerator.But, because when cooling water temperature was high, the solution temperature of auxilliary absorber outlet uprised, and adiabatic condensation temperature does not reduce yet, thereby the temperature of the needed heating source of regenerator just uprises.Because when cooling water temperature reduced, the solution concentration step-down of auxilliary absorber outlet also reduced adiabatic condensation temperature, thereby just can suppress the needed heating source temperature of regenerator.Based on cooling water temperature or the physical quantity suitable, be fine to controlling also by the refrigerant vapour amount by auxilliary absorber AX absorption of assisting regenerator GX to be produced with cooling water temperature.

The schematic configuration of Figure 10 there is shown the 5th embodiment as the improvement example of Fig. 9.The absorption refrigerating machine of present embodiment has the method that the refrigerant vapour amount by auxilliary absorber AX absorption that is produced by auxiliary regenerator GX is regulated.

In the present embodiment, have: the heat that adds on auxiliary regenerator GX is regulated (to the GX of heating source import volume adjustings=Figure 10 of the GX triple valve VA that enters the mouth, or to the VB of solution dispersion volume adjusting=Figure 10 of GX) or the absorbability on auxilliary absorber AX regulate (to the VC of cooling water flow adjusting=Figure 10 of AX, or to the VD of solution dispersion volume adjusting=Figure 10 of AX).

Among the figure, valve VA similarly is configured on the warm water pipeline 81 with the described triple valve V1 of the 1st embodiment.

Triple valve VD is configured in from solution pump SP to flow on the solution stream 1b of auxilliary absorber AX, and 1 mouth of triple valve VD is being connected with auxilliary absorber AX.1 mouth of triple valve VD also can be not attached to auxilliary absorber AX, but with the suction side of solution pump SP, that is, solution stream 2a or solution stream 1a are connected.

Triple valve VC is arranged on the outlet side of the auxilliary absorber AX of cooling water pipeline.Triple valve VC also can be arranged on the entrance side of the auxilliary absorber AX of cooling water pipeline.

Triple valve VB is configured on the solution stream 3 that connects h XH and auxiliary regenerator GX, and 1 mouth of triple valve VB is connected with solution stream 4, and this solution stream 4 will assist regenerator GX to be connected with low-temperature side heat exchanger XL.

In the present embodiment, when the refrigerant vapour amount by auxilliary absorber AX absorption that will assist regenerator GX to be produced reduced, the auxiliary needed thermal source heat of regenerator GX was less, and the temperature that needs also reduces.On the other hand, the heat source temperature of regenerator G needs remains high.Best, earlier heat source fluid is imported to regenerator G, then import to auxiliary regenerator GX.That is since with high heat source temperature utilization in regenerator G one side, thereby efficient is improved.

When the refrigerant vapour amount by auxilliary absorber AX absorption that is produced by auxiliary regenerator GX increased, the thermal source heat increased, and the thermal source outlet temperature reduces.On the other hand, when this refrigerant vapour amount reduced, the thermal source heat reduced, and the thermal source outlet temperature rises.Therefore, preferably in above-mentioned adjustable side, with the mode of heat source temperature (thermal source outlet temperature) as desired value, the control of the refrigerant vapour amount that is absorbed by auxilliary absorber AX that auxiliary regenerator GX is produced is regulated.

Because under the situation that thermal source circulates at absorption refrigerating machine and heat generation source place, when the thermal source outlet temperature reduces, the thermal source inlet temperature also reduces, thus not heat-obtaining source outlet temperature but with the thermal source inlet temperature as desired value, the detection position of thermal source can not specify.Generally be heat-obtaining source outlet temperature or thermal source inlet temperature.

Figure 12 is the summary construction diagram of the absorption refrigerating machine of expression the present invention the 6th embodiment.It is the modified example of the 4th embodiment that present embodiment can be called.

As shown in figure 12, with the 2nd embodiment similarly, in order to utilize the gateway temperature difference of cold water, further raise the efficiency, the absorber A of above-mentioned absorption refrigerating machine is distinguished into low-pressure absorber AL and high pressure absorber AH, evaporimeter E is distinguished into low pressure evaporator EL and high pressure evaporator EH, cold water at first is directed to high pressure evaporator EH, then, chilled cold water is imported to low pressure evaporator EL, and will import to low-pressure absorber AL earlier from the concentrated solution of auxiliary regenerator GX, absorption is from the refrigerant vapour of low pressure evaporator EL, to import to high pressure absorber AH by the solution that low-pressure absorber AL has absorbed refrigerant vapour, absorb refrigerant vapour from high pressure evaporator EH.

Figure 13 is that the saturation temperature of high pressure evaporator EH uprises with respect to the time-continuing process curve map of the solution cycle period of Figure 12, the weak solution concentration step-down of high pressure absorber AH output.Thus, can reduce by auxilliary absorber AX making the concentration necessary amount that further descends, with occasion shown in Figure 9 mutually specific energy efficient is improved.

Although cooling-water flow is to carry out branch at the cooling water introducing port, the mobile of a side is condenser → absorption refrigerating machine, and the opposing party flow into auxilliary absorber, and is best, and the warm water temperature that needs is reduced.

As mentioned above, the absorption refrigerating machine of embodiments of the present invention is provided with: regenerator, condenser, absorber, evaporimeter, auxiliary regenerator and auxilliary absorber, wherein, to produce refrigerant vapour and further concentrated from the concentrated solution heating of above-mentioned regenerator by above-mentioned auxiliary regenerator, to cool off from the weak solution of above-mentioned absorber by above-mentioned auxilliary absorber, and absorb refrigerant vapour from above-mentioned auxiliary regenerator output, and, be provided for importing to the concentrated solution of above-mentioned absorber from above-mentioned auxiliary regenerator and being transported to the low-temperature side heat exchanger that carries out heat exchange between the weak solution of regenerator from above-mentioned auxilliary absorber, further, the high-pressure side heat exchanger is set, and the concentrated solution that is used for by importing to auxiliary regenerator from above-mentioned regenerator heats the weak solution of the regenerator that is transferred of emitting from above-mentioned low-temperature side heat exchanger.

In addition, above-mentioned absorption refrigerating machine can be able to be constituted, absorber zone is divided into low-pressure absorber and high pressure absorber; Above-mentioned evaporator region is divided into low pressure evaporator and high pressure evaporator, cold water at first is directed to high pressure evaporator, then, the cold water that has been cooled is imported to low pressure evaporator, and at first be directed to low-pressure absorber from the concentrated solution of above-mentioned auxiliary regenerator, absorption is from the refrigerant vapour of low pressure evaporator, to import to high pressure absorber by the solution that low-pressure absorber has absorbed refrigerant vapour, absorption imports to above-mentioned auxilliary absorber from the refrigerant vapour of high pressure evaporator with this weak solution.

The absorption refrigerating machine of another embodiment of the present invention is provided with: regenerator, condenser, absorber, evaporimeter, auxiliary regenerator and auxilliary absorber, wherein, will make it produce refrigerant vapour cooling and further concentrated from the concentrated solution heating of above-mentioned regenerator by above-mentioned auxiliary regenerator; By above-mentioned auxilliary absorber the weak solution from above-mentioned absorber is cooled off, and absorb refrigerant vapour from above-mentioned auxiliary regenerator, and, the heat transfer area of above-mentioned auxiliary regenerator is set at below 1/3 of heat transfer area of above-mentioned regenerator, the heat transfer area of above-mentioned auxilliary absorber is set at heat transfer area 2/3 better when following of above-mentioned absorber.

In these absorption refrigerating machines, can constitute, heat source fluid at first is directed to regenerator, then imports to auxiliary regenerator.

The absorption refrigerating machine of another embodiment of the invention is provided with: regenerator, condenser, absorber, evaporimeter, auxiliary regenerator and auxilliary absorber also have absorbent solution arrives absorber through auxilliary absorber → regenerator → auxiliary regenerator from absorber circulating path; The mechanism that the heat-transfer capability of above-mentioned auxiliary regenerator is adjusted is set and/or the mechanism that the heat-transfer capability of above-mentioned auxilliary absorber is adjusted also is fine.

And, in above-mentioned absorption refrigerating machine, can constitute, above-mentioned absorber zone is divided into low-pressure absorber and high pressure absorber, above-mentioned evaporator region is divided into low pressure evaporator and high pressure evaporator, cold water at first is directed to high pressure evaporator, then, the cold water that has been cooled is imported to low pressure evaporator, and will import to low-pressure absorber earlier from the concentrated solution of regenerator and auxiliary regenerator, and absorb refrigerant vapour from low pressure evaporator, will import to high pressure absorber by the solution that low-pressure absorber has absorbed refrigerant vapour, absorption imports to above-mentioned auxiliary regenerator from the refrigerant vapour of high pressure evaporator with this weak solution.When forming such structure, the efficient of above-mentioned absorption refrigerating machine is further improved.

The mechanism that the heat-transfer capability of above-mentioned auxiliary regenerator is adjusted can be with this auxiliary regenerator bypass and/or stream of warm water adjustable valve that the warm water flow that passes through is regulated, or with the heat transfer part bypass of above-mentioned auxiliary regenerator and/or the liquid inventory control valve that the liquid inventory that passes through is regulated.

And, the mechanism that the heat-transfer capability of above-mentioned auxilliary absorber is adjusted can be with this auxilliary absorber bypass and/or cooling water flow adjustable valve that the cooling water flow that passes through is regulated, or with the heat transfer part bypass of above-mentioned auxilliary absorber and/or the liquid inventory control valve that the liquid inventory that passes through is regulated.

Further, the mechanism that the heat-transfer capability of above-mentioned auxiliary regenerator is adjusted and/or can have controlling organization to the mechanism that the heat-transfer capability of auxilliary absorber is adjusted, this controlling organization is regulated according to warm water temperature or regenerator solution temperature as thermal source.

The absorption refrigerating machine of another embodiment of the present invention is provided with: regenerator, condenser, absorber, evaporimeter, auxiliary regenerator and auxilliary absorber, wherein, by above-mentioned auxiliary regenerator the concentrated solution from above-mentioned regenerator is heated generation refrigerant vapour and further concentrated, by above-mentioned auxilliary absorber, utilize the part of the mixing weak solution of above-mentioned absorber outlet weak solution and auxilliary absorber outlet weak solution that the refrigerant vapour of above-mentioned generation is cooled off, and absorb, and, has the path that the remainder of above-mentioned mixing weak solution is transported to above-mentioned regenerator, on this path, in turn be provided with: by the low-temperature side heat exchanger that the concentrated solution that imports to above-mentioned absorber from above-mentioned auxiliary regenerator heats this mixing weak solution, the h that the mixing weak solution of this low-temperature side heat exchanger being exported by the concentrated solution that imports to above-mentioned auxiliary regenerator from above-mentioned regenerator that is transported to regenerator heats.

And.In above-mentioned absorption refrigerating machine, for the gateway temperature difference of utilizing cold water is further raised the efficiency, can also constitute, the absorber zone of above-mentioned absorption refrigerating machine is divided into low-pressure absorber and high pressure absorber, evaporator region is divided into low pressure evaporator and high pressure evaporator, cold water is at first imported to high pressure evaporator, the cold water that then will be cooled imports to low pressure evaporator, and will import to low-pressure absorber from the concentrated solution of regenerator earlier, absorption is from the refrigerant vapour of low pressure evaporator, to import to high pressure absorber by the solution that low-pressure absorber has absorbed refrigerant vapour, absorption is from the refrigerant vapour of high pressure evaporator, to absorb the weak solution of refrigerant vapour and mixed by high pressure absorber from the weak solution of auxilliary absorber, form and mix weak solution, the part of this mixing weak solution is imported to auxilliary absorber, remainder is imported to regenerator.

The present invention's possibility of utilizing industrially is, if adopt the present invention, by as above Described structure can form absorption freezing as thermal source of the warm water of 60～70 ℃ of C degree Machine, although use absorption refrigerating machine poor than single-action, it is more absorption than secondary concentrated type to form efficient The absorption refrigerating machine that refrigerator is high, and can effectively utilize relation because of the ambient atmosphere condition And cooling water temperature is reduced, that is, along with coolant water temperature reduces, efficient is risen, according to Temperature conditions can be to turn round with identical efficient with single-action.

Claims

1. absorption refrigerating machine is characterized in that, has:

Produce refrigerant vapour and make the regenerator of solution concentration;

The condenser that the refrigerant vapour of above-mentioned generation is condensed;

Make the evaporimeter of above-mentioned cold-producing medium evaporation of condensing;

With the absorber of solution with the refrigerant vapour absorption of above-mentioned evaporation;

To heat from the concentrated solution of above-mentioned regenerator and the generation refrigerant vapour, carry out the auxiliary regenerator that further concentrates;

To cool off from the weak solution of above-mentioned absorber, and make by the absorbed auxilliary absorber of the refrigerant vapour that above-mentioned auxiliary regenerator produced;

In the concentrated solution that imports to above-mentioned absorber from above-mentioned auxiliary regenerator be transported to the low-temperature side heat exchanger that carries out heat exchange between the weak solution of above-mentioned regenerator from above-mentioned auxilliary absorber; And

With the concentrated solution that is directed to above-mentioned auxiliary regenerator from above-mentioned regenerator, to from the output of above-mentioned low-temperature side heat exchanger and be transported to the h that the weak solution of above-mentioned regenerator heats.

2. absorption refrigerating machine is characterized in that, has:

Produce refrigerant vapour and make the regenerator of solution concentration;

To cool off from the weak solution of above-mentioned absorber, and make by the absorbed auxilliary absorber of the refrigerant vapour that above-mentioned auxiliary regenerator produced; And

The heat transfer area of above-mentioned auxiliary regenerator is below 1/3 of heat transfer area of above-mentioned regenerator, and the heat transfer area of above-mentioned auxilliary absorber is below 2/3 of heat transfer area of above-mentioned absorber.

3. absorption refrigerating machine is characterized in that, has:

Produce refrigerant vapour and make the regenerator of solution concentration;

Above-mentioned solution is from above-mentioned absorber, arrives the circulating path of above-mentioned absorber through above-mentioned auxilliary absorber, above-mentioned regenerator, above-mentioned auxiliary regenerator according to mentioned order; And

At least one mechanism in mechanism that the heat-transfer capability of above-mentioned auxiliary regenerator is adjusted and the mechanism that the heat-transfer capability of above-mentioned auxilliary absorber is adjusted.

4. absorption refrigerating machine as claimed in claim 3, it is characterized in that, the mechanism that the heat-transfer capability of above-mentioned auxiliary regenerator is adjusted is with this auxiliary regenerator bypass and/or stream of warm water adjustable valve that the warm water flow that passes through is regulated, or with the heat transfer part bypass of above-mentioned auxiliary regenerator and/or the liquid inventory control valve that the liquid inventory that passes through is regulated.

5. as claim 3 or 4 described absorption refrigerating machines, it is characterized in that, the mechanism that the heat-transfer capability of above-mentioned auxilliary absorber is adjusted is with this auxilliary absorber bypass and/or cooling water flow adjustable valve that the cooling water flow that passes through is regulated, or with the heat transfer part bypass of above-mentioned auxilliary absorber and/or the liquid inventory control valve that the liquid inventory that passes through is regulated.

6. as any described absorption refrigerating machine in the claim 3～5, it is characterized in that, in mechanism that the heat-transfer capability of above-mentioned auxiliary regenerator is adjusted and the mechanism that the heat-transfer capability of auxilliary absorber is adjusted at least one has controlling organization, and this controlling organization is regulated according to warm water temperature or regenerator solution temperature as thermal source.

7. as any described absorption refrigerating machine in the claim 1～6, it is characterized in that, above-mentioned absorber zone is divided into low-pressure absorber and high pressure absorber, above-mentioned evaporator region is divided into low pressure evaporator and high pressure evaporator, cold water is imported to above-mentioned high pressure evaporator earlier, then, the cold water that has been cooled is imported to above-mentioned low pressure evaporator, and, to import to above-mentioned low-pressure absorber earlier from the concentrated solution of above-mentioned auxiliary regenerator, refrigerant vapour from above-mentioned low pressure evaporator is absorbed, to import to above-mentioned high pressure absorber by the solution that above-mentioned low-pressure absorber has absorbed refrigerant vapour, refrigerant vapour from above-mentioned high pressure evaporator is absorbed, the weak solution that has absorbed this refrigerant vapour is imported to above-mentioned auxilliary absorber.

8. absorption refrigerating machine is characterized in that, has:

Produce refrigerant vapour and make the regenerator of solution concentration;

Weak solution is cooled off, and make that by the absorbed auxilliary absorber of the refrigerant vapour that above-mentioned auxiliary regenerator produced this auxilliary absorber is constituted as the part of the mixing weak solution of utilizing above-mentioned absorber outlet weak solution and this auxilliary absorber outlet weak solution as above-mentioned weak solution;

The remainder of above-mentioned mixing weak solution is transported to the path of above-mentioned regenerator;

In above-mentioned path, in turn use from above-mentioned auxiliary regenerator and import to the low-temperature side heat exchanger that the concentrated solution of above-mentioned absorber heats above-mentioned mixing weak solution; And

With the concentrated solution that imports to above-mentioned auxiliary regenerator from above-mentioned regenerator to the output of above-mentioned low-temperature side heat exchanger and be transported to the h that the mixing weak solution of above-mentioned regenerator heats.

9. absorption refrigerating machine as claimed in claim 8, it is characterized in that, above-mentioned absorber zone is divided into low-pressure absorber and high pressure absorber, above-mentioned evaporator region is divided into low pressure evaporator and high pressure evaporator, cold water is imported to above-mentioned high pressure evaporator earlier, then, the cold water that has been cooled is imported to above-mentioned low pressure evaporator, and will import to above-mentioned low-pressure absorber earlier from the concentrated solution of above-mentioned regenerator, refrigerant vapour from above-mentioned low pressure evaporator is absorbed, to import to above-mentioned high pressure absorber by the solution that above-mentioned low-pressure absorber has absorbed refrigerant vapour, refrigerant vapour from above-mentioned high pressure evaporator is absorbed, a part that the above-mentioned high pressure absorber that has absorbed this refrigerant vapour is exported the mixing weak solution of weak solution and above-mentioned auxilliary absorber outlet weak solution imports to above-mentioned auxilliary absorber, and remainder is transported to above-mentioned regenerator.

10. as any described absorption refrigerating machine in the claim 1～9, it is characterized in that the thermal source liquid that above-mentioned solution is heated imports to above-mentioned regenerator earlier, then, import to above-mentioned auxiliary regenerator.