CN1172128C

CN1172128C - Heat pump and dehumidifier

Info

Publication number: CN1172128C
Application number: CNB018031846A
Authority: CN
Inventors: 前田健作
Original assignee: Ebara Corp
Current assignee: Ebara Corp
Priority date: 2001-03-07
Filing date: 2001-03-07
Publication date: 2004-10-20
Anticipated expiration: 2021-03-07
Also published as: DE60117000D1; EP1367333A4; EP1367333A1; EP1367333B1; CN1416519A; WO2002070960A1; DE60117000T2

Abstract

The present invention provides a heat pump with high COP and a dehumidifier constructed with a compact dimension. The heat pump is provided with a supercharger (260), an evaporator (210), a condenser (220) and a first heat exchanger (300a), wherein the supercharger (260) is used for increasing the pressure of refrigerants; the evaporator (210) uses the evaporation heat of refrigerants to be supercharged for cooling low temperature heat source fluid (A); the condenser (220) uses the condensation heat of the supercharged refrigerants for heating high temperature heat source fluid (B); the first heat exchanger (300a) is used for the heat exchange between the low temperature heat source fluid at the upper stream of the evaporator (210) and cooling fluid; the first heat exchanger (300a) is provided with a first containing chamber (310), a second containing chamber (320) and refrigerant channels (251A1-A9, 252A1-A9), wherein the first containing chamber (310) is used for the low temperature heat source fluid (A) to flow over, the second containing chamber (320) is used for the cooling fluid (B) to flow over, and the refrigerant channels extend and pass through the first containing chamber and the second containing chamber; the refrigerant channels (251A1-A9, 252A1-A9) are connected with the condenser (220) through a first restrictor (330), repeatedly alternate to extend and pass through the first containing chamber and the second containing chamber, and then are connected to the evaporator (210) through a second restrictor (250). Since flowing across the first containing chamber and the second chamber for many times, the refrigerants can not completely dry out when extend and pass through the refrigerant channel of the first containing chamber.

Description

Heat pump and dehydrating unit

Technical field

The present invention relates to heat pump and dehydrating unit, particularly a kind of dehydrating unit that has the heat pump of high COP (coefficient of performance) and this heat pump is housed.

Background technology

As shown in figure 17, there is shown a kind of drier formula aircondition in the past, it is used as thermal source with a heat pump.Adopted a compression heat pump HP in the aircondition shown in Figure 17, it comprises a heat pump compressor 260.This aircondition has a path that is used to handle air A, be dried in this path agent runner 103 of moisture absorbs, and path that is used to reclaim air B, it is heated by a thermal source, extend through the desiccant wheel 3 that has absorbed moisture again, so that moisture is drawn, thereby make the drier reduction from drier.Aircondition has an air-conditioner, it comprises a sensible heat exchanger 104, be used for making the processing air that has dehumidified and be in will the drier reduction of desiccant wheel 3 before and by heat-shift between the regeneration air before the thermal source heating, aircondition also has compression heat pump HP.Be used for reducing the air-conditioner regeneration air of drier as the high temperature heat source of compression heat pump HP, and heated by heater 220.The air-conditioner regeneration air is as the low-temperature heat source among the compression heat pump HP, and device 210 coolings that are cooled.

The operation of compression heat pump HP shown in Figure 17 is described below with reference to the mollier diagram shown in Figure 18.Curve map among Figure 18 is as the mollier diagram of making under the situation of cold-producing medium at HFC134a.Point a represents cold-producing medium device 210 evaporation and the cold-producing medium state when being rendered as saturated vapor that is cooled.This moment, the pressure of cold-producing medium was 4.2kg/cm ², temperature is 10 ℃, enthalpy is 148.83kcal/kg.Point b represent steam sucked by compressor 260 and compress after state, i.e. the state in compressor 260 exits.Under this state, the pressure of cold-producing medium is 19.3kg/cm ², temperature is 78 ℃, and is rendered as the form of superheated vapor.Refrigerant vapour is cooled heater (seeing it is cooling device or condenser from the angle of cold-producing medium) 220, and arrives the state to represent among the c in the mollier diagram.At a c place, cold-producing medium is rendered as the saturated vapor state, and pressure is 19.3kg/cm ², temperature is 65 ℃.Under this pressure, cold-producing medium is further cooled and condensation, the state of representing with point of arrival d.At a d place, cold-producing medium is rendered as the form of saturated liquid, and has the identical temperature with some c place.The enthalpy of saturated liquid is 122.97kcal/kg.This refrigerant liquid reduces pressure in expansion valve 250, thereby is issued to saturation pressure 4.2kg/cm 10 ℃ of temperature ²Under 10 ℃ temperature, cold-producing medium is transported to cooling device (seeing it is evaporimeter from the angle of cold-producing medium) 210 with the state of the mixture of refrigerant liquid and steam, at this, mixture draw to be handled airborne heat, and is evaporated and arrives the saturated vapor state of representing with an a in mollier diagram.Saturated vapor is inhaled in the compressor 260 again, to carry out above-mentioned cycle period repeatedly.

Because the refrigerant cools efficient in the cold-producing medium cycle period not necessarily can be very high, therefore used heat pump does not have excellent COP in above-mentioned traditional aircondition.In this traditional aircondition, be used for before the processing air is cooled device 210 coolings, having played the part of the key player to handling the preliminary sensible heat exchanger 104 that cools off of air work.Yet,, therefore be difficult to tectonic system, and the size of system can be bigger inevitably because sensible heat exchanger will occupy very big space usually in system.

Therefore, an object of the present invention is to provide a kind of heat pump and a kind of dehydrating unit with high COP and cramped construction with high COP.

Summary of the invention

According to an aspect of the present invention, a kind of heat pump is provided, its interior booster, a condenser and an evaporimeter are interconnecting by refrigerant path, heat pump comprises: be arranged in being used in the refrigerant path links to each other condenser with evaporimeter utensil, it is used under middle pressure alternatively vaporised and condensating refrigerant repeatedly, and described middle pressure is at the pressure that will be pressurized the device supercharging and between the pressure after being pressurized the device supercharging.

Heat pump can be settled like this, promptly when cold-producing medium by alternately the evaporation and condensation after, condensed cold-producing medium will be depressurized to second middle pressure that is lower than last middle pressure, and then be evaporated.Heat pump can have two and be used for the utensil of alternatively vaporised and condensating refrigerant repeatedly, and heat pump can be settled like this, be that evaporating pressure in one of them utensil or condensing pressure are lower than evaporating pressure or the condensing pressure in another utensil, and when cold-producing medium was alternately evaporated with condensation by corresponding utensil, condensed cold-producing medium was depressurized to evaporating pressure simultaneously in evaporimeter.

According to an aspect of the present invention, provide a kind of dehumidification air conditioner device, it comprises: a moisture absorbing device, and it is used for remove handling airborne moisture, and is reproduced air and therefrom siphons away moisture and obtain reduction; And a heat pump, it has a condenser, evaporimeter and a tubule group that condenser is linked to each other with evaporimeter; Wherein the tubule group is settled like this, promptly the chilled cold-producing medium of the device that is condensed can be introduced in the evaporimeter, and cold-producing medium is alternately contacted with regeneration air with the processing air.

Two above-mentioned tubule groups can be arranged, and be used for from the refrigerant path that condenser is introduced cold-producing medium to the tubule group branching into two paths, they are connecting two tubule groups respectively, and the refrigerant lines that extends out from corresponding tubule group can converge each other at evaporator inlet, perhaps converges in the evaporimeter indirect.

According to another aspect of the present invention, provide a kind of heat pump, it comprises: a booster, the pressure of its cold-producing medium that is used to raise; An evaporimeter, its utilization will be pressurized the heat of evaporation cooling low-temperature heat source fluid of the cold-producing medium of device supercharging; A condenser, its utilization are pressurized the condensation heat heating high temperature heat source fluid of the cold-producing medium after the device supercharging; And first heat exchanger, it is used to make the low-temperature heat source fluid and the above-mentioned high temperature heat source fluid that are positioned at vaporizer upstream to carry out heat exchange; Wherein first heat exchanger has first room that is used for being flow through by the low-temperature heat source fluid, is used for second room that is flow through by the high temperature heat source fluid and extends through first room and the coolant channel of second room, coolant channel is connecting condenser by the first throttle device, and alternately extend through first room and second room repeatedly, be connected to evaporimeter by second flow controller again.Say especially, be used for the high temperature heat source fluid that the low-temperature heat source fluid that is positioned at vaporizer upstream with first heat exchanger carries out heat exchange and preferably include the high temperature heat source fluid that is positioned at the condenser upstream.

In coolant channel, cold-producing medium flows along a direction usually on the whole.This refers to, and sees on the whole, and cold-producing medium flows through coolant channel along same direction basically, but cold-producing medium may be because of the turbulent flow local return in the part, perhaps can cause that flow direction oscillation changes because of bubble or pressure oscillation that instantaneous interruption produced.Coolant channel comprises for example heat-exchange tube, and alternately extends through first room and second room.Therefore, the cold-producing medium that flows along a direction on the whole can be repeatedly by alternatively vaporised and condensation.Term " coolant channel alternately extends through first room and second room " refers to coolant channel and not only extends through first room and second room once, but coolant channel extends through first room and second room earlier once, extends through second room or first room more at least once.In first room, low-temperature heat source fluid and cold-producing medium heat-shift, in second room, high temperature heat source fluid and cold-producing medium heat-shift.Usually, cold-producing medium is evaporation at least in part in the coolant channel that extends through first room, will condensation at least in part in the coolant channel that extends through second room and be in the cold-producing medium of steam attitude.

By said structure, because cold-producing medium is flowed through first and second rooms repeatedly, therefore, though cold-producing medium is evaporated in the coolant channel that extends through first room, it can not parch fully yet.

In heat pump, first room and second room can be settled like this, and promptly low-temperature heat source fluid and high temperature heat source fluid flow in the mode of adverse current; Coolant channel in first room and second room can have: be arranged at least one pair of the first room extension and the second room extension on first plane, this first plane is substantially perpendicular to the flow direction of low-temperature heat source fluid and high temperature heat source fluid; Be arranged at least one pair of the first room extension and the second room extension on second plane, this second plane is different with first plane and be substantially perpendicular to the flow direction of low-temperature heat source fluid and high temperature heat source fluid; And locational middle flow controller that is arranged in first plane to the second plane transition.

In extending through the coolant channel part of first room, there is at least a portion cold-producing medium to be evaporated usually.Therefore this coolant channel part can be called evaporator section.In extending through the coolant channel part of second room, there is at least a portion cold-producing medium to be condensed usually.Therefore this coolant channel part can be called condensation segment.Therefore aforementioned each to part refer to evaporator section and condensation segment (or condensation segment and evaporator section) to group.Because heat pump has middle flow controller, so the pressure in the coolant channel in the pressure in the coolant channel in first plane and second plane can have different values.Because low-temperature heat source fluid and high temperature heat source fluid flow with the form of adverse current, therefore the described pressure that differs from one another can reduce gradually along the downstream direction of low-temperature heat source fluid or the updrift side of high temperature heat source fluid.Like this, between low-temperature heat source fluid and the high temperature heat source fluid countercurrent heat exchange can take place, thereby obtain high heat exchanger effectiveness.

In above-mentioned heat pump, middle flow controller can be placed on the position of coolant channel when extending through second room, and middle flow controller can be placed on the position of coolant channel when extending through first room.

Heat pump can also comprise second heat exchanger, and it is used to make the low-temperature heat source fluid and the high temperature heat source fluid that are positioned at vaporizer upstream to carry out heat exchange; Wherein second heat exchanger has the 3rd room that is used for being flow through by the low-temperature heat source fluid, is used for the 4th room and a coolant channel that extends through the 3rd room and the 4th room of being flow through by the high temperature heat source fluid, this coolant channel is connecting condenser by the 3rd flow controller, and alternately extend through the 3rd room and the 4th room repeatedly, be connected to evaporimeter by the 4th flow controller again; The 3rd room with respect to the low-temperature heat source fluid placement in the first room downstream, the 4th room with respect to the high temperature heat source fluid placement in the second room upstream.Say especially, be used for the high temperature heat source fluid that the low-temperature heat source fluid that is positioned at vaporizer upstream with second heat exchanger carries out heat exchange and preferably include the high temperature heat source fluid that is positioned at the condenser upstream.

By said structure, because heat pump has second heat exchanger, so heat pump can operate under the pressure different with the pressure of first heat exchanger, thereby can improve the overall thermal exchange efficiency.

Heat pump can also comprise the 3rd heat exchanger, and it is used to make the low-temperature heat source fluid and the high temperature heat source fluid that are positioned at vaporizer upstream to carry out heat exchange; Wherein the 3rd heat exchanger has the 5th room that is used for being flow through by the low-temperature heat source fluid, is used for the 6th room and a coolant channel that extends through the 5th room and the 6th room of being flow through by the high temperature heat source fluid, this coolant channel is connecting the coolant channel of first heat exchanger by the 5th flow controller, and alternately extend through the 5th room and the 6th room repeatedly, be connected to evaporimeter by second flow controller again; The 5th room with respect to the low-temperature heat source fluid placement in the first room downstream, the 6th room with respect to the high temperature heat source fluid placement in the second room upstream.Say especially, be used for the high temperature heat source fluid that the low-temperature heat source fluid that is positioned at vaporizer upstream with the 3rd heat exchanger carries out heat exchange and preferably include the high temperature heat source fluid that is positioned at the condenser upstream.

According to another aspect of the present invention, a kind of dehydrating unit is provided, it comprises foregoing heat pump and a moisture absorbing device, this moisture absorbing device is with respect to the upstream of low-temperature heat source fluid placement at first heat exchanger, and has the drier that is used for from low-temperature heat source absorption of fluids moisture.

The low-temperature heat source fluid is the processing air of aircondition normally.Owing to have a moisture absorbing device in the aircondition, so the humidity of low-temperature heat source fluid can reduce.The low-temperature heat source fluid normally is used as the outside air of regeneration air.

The preferred structure like this of dehydrating unit of the present invention promptly utilizes the moisture in the warmed-up high temperature heat source fluid absorption of the device that the is condensed drier.

Purpose of the present invention can also realize that to the method for high temperature heat source fluid transmission heat this method comprises from the low-temperature heat source fluid by a kind of: the first step, and at predetermined low pressure 4.2kg/cm ²Following vaporized refrigerant is with the cooling low-temperature heat source; In second step, will in the first step, be increased to predetermined high pressure 19.3kg/cm by the pressure of vaporized cold-producing medium ²The 3rd one, will be in second step under predetermined high pressure supercharging condensation of refrigerant, to utilize condensation heat heating high temperature heat source; In the 4th step, chilled cold-producing medium in the 3rd one is decompressed to first middle pressure between predetermined high pressure and predetermined low pressure; In the 5th step, the cold-producing medium that has reduced pressure is promptly evaporated in evaporation and condensation repeatedly in the 4th step, with the cooling low-temperature heat source, and condensating refrigerant, with the heating high temperature heat source; In the 6th step, chilled cold-producing medium in the 5th one is supplied as the cold-producing medium that will evaporate in the first step.Heat conduction normally mode by this draw heat realizes.

Evaporation repeatedly and condensation operation in the 5th one are so to realize: vaporized refrigerant, and with cooling low-temperature heat source fluid, and condensating refrigerant, with heating high temperature heat source fluid.The 6th step was the step of supply cold-producing medium, and promptly the cold-producing medium that has heated the high temperature heat source fluid by condensation is provided as the cold-producing medium that will evaporate in the first step.

For the dehumanization method that comprises above-mentioned draw heat method, can be provided with for the 11 step, before the low-temperature heat source fluid was cooled by vaporized refrigerant in the 5th step, utilize drier to absorb the moisture that contains in the low-temperature heat source fluid; And the 12 step, utilize the high temperature heat source fluid that has been heated by condensating refrigerant in the 3rd step from the drier that during the 11 step, has absorbed moisture, to absorb water.

The present invention is based on the Japanese Patent Application Publication document No.11-245022 that submitted on August 31st, 1999, the document is incorporated herein by the part of the application's disclosure.

Can understand the present invention more fully according to following detailed.Other application modes of the present invention can more clearly display from following detailed.Yet, the preferred embodiment that following detailed and specific example are just described for explaining purpose of the present invention, obviously, under the premise without departing from the spirit and scope of the present invention, those of ordinary skill in the art can make change miscellaneous and modification to the embodiment that describes in detail below.

The applicant does not think the arbitrary embodiment that describes for the public below should being confined to, and does not think that any modification that disclosure is done and substituting is not included in the scope according to claims of a doctrine of equivalents formation part of the present invention.

Description of drawings

Fig. 1 is according to the heat pump of first embodiment of the invention and flow circuit diagram that the dehumidification air conditioner device of this heat pump is housed;

Fig. 2 (a) and 2 (b) are respectively a kind of schematic side elevation and transverse cross sectional vertical views that is suitable for being used in the heat exchanger in the heat pump shown in Figure 1;

Fig. 3 is the mollier diagram of heat pump shown in Figure 1;

Fig. 4 is the psychrometric chart that is used to explain the operation of dehumidification air conditioner device shown in Figure 1;

Fig. 5 is the schematic transverse cross sectional front view that is equipped with according to a practical structures example of the dehumidification air conditioner device of the heat pump of first embodiment of the invention;

Fig. 6 is according to the heat pump of second embodiment of the invention and flow circuit diagram that the dehumidification air conditioner device of this heat pump is housed;

Fig. 7 is the mollier diagram of heat pump shown in Figure 6;

Fig. 8 is the schematic transverse cross sectional front view that is equipped with according to a practical structures example of the dehumidification air conditioner device of the heat pump of second embodiment of the invention;

Fig. 9 is according to the heat pump of third embodiment of the invention and flow circuit diagram that the dehumidification air conditioner device of this heat pump is housed;

Figure 10 is the mollier diagram of heat pump shown in Figure 9;

Figure 11 is the schematic transverse cross sectional front view that is equipped with according to a practical structures example of the dehumidification air conditioner device of the heat pump of third embodiment of the invention;

Figure 12 is according to the heat pump of four embodiment of the invention and flow circuit diagram that the dehumidification air conditioner device of this heat pump is housed;

Figure 13 is the mollier diagram of heat pump shown in Figure 12;

Figure 14 is the schematic transverse cross sectional front view that is equipped with according to a practical structures example of the dehumidification air conditioner device of the heat pump of four embodiment of the invention;

Figure 15 (a) and 15 (b) are respectively a kind of schematic plan and side views that is suitable for being used in according to the heat exchanger in the heat pump of the embodiment of the invention;

Figure 16 is the curve map that concerns between heat-exchange tube progression and the temperature efficiency;

Figure 17 is the flow circuit diagram of a kind of conventional heat pump and a kind of traditional dehumidification air conditioner device;

Figure 18 is the mollier diagram of conventional heat pump shown in Figure 17.

The specific embodiment

A preferred embodiment of the present invention is described with reference to the accompanying drawings.In each figure, identical or similar elements is represented with identical or similar Reference numeral, and no longer is repeated in this description.

Fig. 1 is according to the heat pump HP1 of first embodiment of the invention and the flow circuit diagram that the dehumidification air conditioner device of heat pump HP1 is housed.Dehumidification air conditioner device is the aircondition that adopts drier.Fig. 2 (a) and 2 (b) are respectively schematic side elevation and the transverse cross sectional vertical views that is suitable for being used in the structure example of first heat exchanger in the heat pump shown in Figure 1.Fig. 3 is included in the mollier diagram of the heat pump in the aircondition shown in Figure 1.Fig. 4 is the psychrometric chart of dehumidification air conditioner device shown in Figure 1.

Describe according to the heat pump of first embodiment and the CONSTRUCTED SPECIFICATION that the dehumidification air conditioner device of this heat pump is housed below with reference to Fig. 1.This aircondition utilizes drier to reduce the humidity of handling air, so that keep comfortable air ambient in having supplied the air conditioning space 101 of handling air.In Fig. 1, the device relevant with handling air will be described along the path from the processing air A in air conditioning space 101.First room 310, path 110, refrigerant evaporator (seeing it is cooling device from the angle of handling air) 210 and the path 111 that are connecting the path 107 in air conditioning space 101, the hair-dryer that is used for the circular treatment air 102 that links to each other with path 107, path 108, the desiccant wheel 103 of filling drier, path 109, be positioned at according to the first heat exchanger 300a of the present invention with above-mentioned arranged in order, return in the air conditioning space 101 so that handle air.

Path 124, the hair-dryer 140 that is used for the circular regeneration air, path 125, be used to make the heat exchanger 300a of generation heat exchange between regeneration air that flows into desiccant wheel 103 and the processing air that flows out desiccant wheel second room 320, path 126, refrigerant condenser (seeing it is heater) 220, path 127, desiccant wheel 103 and path 128 from the angle of regeneration air with above-mentioned order successively along the paths arrangement of the regeneration air B of the space OA that comes from the outside, with regeneration air as being discharged in the extraneous space.

Each device the heat pump HP1 is described from refrigerant evaporator 210 beginnings along refrigerant path below.In Fig. 1, refrigerant evaporator 210, path 207, be used to compress compressor 260, path 210, refrigerant condenser 220, path 202, flow controller 330, heat exchanger 330a, path 204, flow controller 250 and the path 206 that cooled dose evaporimeter 210 flashes to the cold-producing medium of steam and, so that cold-producing medium turns back in the refrigerant evaporator 210 with above-mentioned arranged in order.So just constituted heat pump HP1.

Desiccant wheel 103 comprise one can be around the thick disk shape runner of rotation AX rotation, drier is filled in the runner and leaves and is used to gap that air is flow through.As example, desiccant wheel 103 comprises the dry element of a plurality of tubuloses, and they combine togather, and extend so that their central axis is parallel to rotation AX.Runner be placed along a direction around rotation AX rotation, and make that handling air A and regeneration air B can flow into and flow out and be parallel to the desiccant wheel 103 that rotation AX is arranging.Each dry element be placed along with the rotation of runner 103 alternately contact handle air A and regeneration air B.Usually, desiccant wheel 103 is settled like this, promptly handles air A and regeneration air B flow through circular desiccant wheel 103 with the adverse current form that is parallel to rotation AX corresponding half zone.

Because aircondition is settled like this, be compression heat pump HP1 processing air and its regeneration air of heating of cool drying agent formula air-conditioner simultaneously, therefore compression heat pump HP1 can utilize the driving energy of the drive source supply outside the compression heat pump HP1 and produce cooling effect to handling air, and to be used to reduce the heat of drier be from the summation of the driving energy of the heat of handling air drawn and compression heat pump HP1 by the heat pump running.Like this, the driving energy that applies from extraneous drive source can use by multiple approach, to realize high energy-saving effect.Utilization can further improve energy-saving effect at the heat exchanger 300a that handles heat-shift between air and the regeneration air.

Below with reference to Fig. 2 (a) and 2 (b) CONSTRUCTED SPECIFICATION that is suitable for being used in the heat exchanger 300a among the heat pump HP1 is described.The side view that Fig. 2 (a) is plate wing one tubing heat exchanger from as vertically the seeing of the pipe of refrigerant flow path the time, some of them plate wing is disconnected demonstration.Symbol " * " the expression cold-producing medium at the circular cross sections center of pipe is in the paper of observer's flow graph 2 (a), and the symbol " ● " at the circular cross sections center of pipe expression cold-producing medium flows to the observer from the paper of Fig. 2 (a).Fig. 2 (b) is the cross-sectional view that the hatching line X-X in Fig. 2 (a) is done.In Fig. 2 (b), heat exchanger 300a has second room 320 that the outside air that is used for first room 310 that processed air A flows through and is used to be used as regeneration air is flowed through, first and second rooms 310,320 adjoin arrangement each other, and single partition 301 is clipped between them.

In Fig. 2 (a), handle air A and be fed to first room 310 from upside, and discharge from the downside of first room 310 by path 110 by path 109.Regeneration air B is fed to second room 320 from downside by path 125, discharges from the upside of second room 320 by path 126 again.Shown in Fig. 2 (a), heat exchanger 300a has the heat-exchange tube as refrigerant flow path of a plurality of almost parallels, and they are positioned at (promptly perpendicular to Fig. 2 (a) paper) Different Plane PA, PB, the PC of a plurality of approximate horizontal ... in.

Shown in Fig. 2 (b), the partition 301 that a plurality of heat-exchange tubes extend through first room 310, second room 320 and described room is separated each other.As example, be arranged in that the heat-exchange tube among the plane P A has the part that extends through first room 310 shown in Fig. 2 (a), shown in Fig. 2 (b), these parts are called evaporator section 251, with as first coolant channel.A plurality of evaporator sections with corresponding Reference numeral 251A1,251A2,251A3 ... 251A9 (in illustrated example, having nine heat-exchange tubes to be arranged among the single plane PA) expression.Below discuss under the situation of described a plurality of evaporator sections separately not needing, these evaporator sections are with 251 expressions of single Reference numeral.The heat-exchange tube that is arranged among the plane P A also has the part that extends through second room 320, and these parts are called condensation segment 252, to be used as second coolant channel.A plurality of condensation segments with corresponding Reference numeral 252A1,252A2,252A3 ... 252A9 represents.Below discuss under the situation of described a plurality of condensation segments separately not needing, these condensation segments are with 252 expressions of single Reference numeral.Evaporator section 251A1 and condensation segment 252A1,251A2 and 252A2,251A3 and 252A3 ... 251A9 and 252A9 constitute the first room extension and the second room extension respectively to group, and have constituted each coolant channel.

In addition, shown in Fig. 2 (b), the heat-exchange tube that is arranged among the single plane PB has a plurality of parts that extend through first room 310, these parts be called evaporator section 251B1,251B2,251B3 ... 251B8 (in illustrated example, having eight heat-exchange tubes to be arranged among the plane P B).The heat-exchange tube that is arranged among the plane P B also has the part that extends through second room 320, these parts and above-mentioned evaporator section are formed coolant channel to group, and be called condensation segment 252B1,252B2,252B3 ... 252B8 is to be used as second coolant channel.Also be provided with among the plane P C with plane P B in the same coolant channel, they are not shown.

In the heat exchanger shown in Fig. 2 (a) and 2 (b), evaporator section 251A1 and condensation segment 252A1 become a partner each other, and are made of the single pipe that forms integral passage.Evaporator section 251A2,251A3 ... with condensation segment 252A2,252A3 ... and evaporator section 251B1,251B2,251B3 ... with condensation segment 252B1,252B2,252B3 ... also construct similarly.This feature is added first room 310 and second room 320 and is adjoined each other and settle and have single partition 301 to be clipped between them, can make heat exchanger 300a less on the whole effectively and compact.

In the heat exchanger shown in Fig. 2 (a) and 2 (b), evaporator section 251A, 251B, 251C begin to arrange successively downwards with the upside of above-mentioned order from Fig. 2 (a), and condensation segment 252A, 252B, 252C also begin to arrange successively downwards with the upside of above-mentioned order from Fig. 2 (a).In plane P A, each evaporator section begins to arrange successively that condensation segment also begins to arrange successively with the left side of order from Fig. 2 (a) of 252A1-252A9 to the right to the right with the left side of order from Fig. 2 (a) of 251A1-251A9.

Shown in Fig. 2 (b), the end (away from partition 301) of the end of condensation segment 252A1 (away from partition 301) and condensation segment 252A2 is joined to one another by a U-shaped pipe.The end of the end of evaporator section 251A2 and evaporator section 251A3 also is joined to one another by a U-shaped pipe similarly.

Like this, along being introduced the condensation segment 252A2 by the U-shaped pipe to the cold-producing medium of the direction overall flow of condensation segment 252A1 from evaporator section 251A1, flow among the evaporator section 251A2, cold-producing medium flows among the evaporator section 251A3 by the U-shaped pipe from here again.In this way, the coolant channel that is made of evaporator section and condensation segment will replace, extend through repeatedly first room 310 and second room 320.In other words, coolant channel is provided with in the mode of suite folding tubule.This suite folding tubule extends through first room 310 and second room 320, and keeps alternately contact to handle air and regeneration air.

In Fig. 2 (a), the right-hand end of the coolant channel among the plane P A is that the right-hand end of the end of condensation segment 252A9 and the coolant channel among the plane P B is that the end of condensation segment 252B8 is connected to each other by an eyelet 331 as flow controller.The left-hand end of the coolant channel among the plane P B is that the left-hand end of the end of condensation segment 252B1 and the coolant channel among the plane P C is that the end of condensation segment 252C1 (not shown) is connected to each other by an eyelet 332 as flow controller.

In Fig. 2 (a), handle air A and flow in first room 310 downwards by conduit 109, flow out first room 310 downwards.In Fig. 2 (a), the outside air that is used as regeneration air B upwards flows in second room 320 by conduit 125, upwards flows out second room 320 again.

Utilize so heat exchanger of structure, the cold-producing medium of introducing among the evaporator section 251A1 is partly evaporated in evaporator section 251A1, flows among the condensation segment 252A1 with hygrometric state again.Cold-producing medium is turned to by the U-shaped pipe, flows among the condensation segment 252A2 and at this to be condensed again.Condensed cold-producing medium will flow among the evaporator section 251A2, partly be evaporated at this cold-producing medium, be turned to and will flow among the evaporator section 251A3 by the U-shaped pipe again.Cold-producing medium is so repeatedly by alternatively vaporised and condensation, last column condensation segment 252A9 in arriving plane P A.Afterwards, cold-producing medium is reduced pressure by flow controller 331, and among the condensation segment 252B8 among the inflow plane P B.

Next, cold-producing medium alternating current is similarly crossed condensation segment and evaporator section among the plane P B, and by condensation and evaporation repeatedly, arrives last column condensation segment 252B1 among the plane P B until cold-producing medium.Cold-producing medium is reduced pressure by flow controller 332 again, and among the condensation segment 252C1 among the inflow plane P C.

Condensing pressure among evaporating pressure among the evaporator section 251A and the condensation segment 252A, first middle pressure just, perhaps evaporating pressure among the evaporator section 251B and the condensing pressure among the condensation segment 252B, second middle pressure just is according to handling air A and determining as the temperature of the outside air of regeneration air B.Because the heat exchanger 300a shown in Fig. 2 (a) and 2 (b) implements the heat conduction by evaporation and condensation, so heat exchanger has excellent pyroconductivity.In addition, owing to heat exchange is implemented according to countercurrent action, so heat exchanger has very high rate of heat exchange.Since cold-producing medium be compelled to from evaporator section 251 to condensation segment 252 or from condensation segment 252 to evaporator section 251 the coolant channel along same direction overall flow roughly, therefore the heat exchanger effectiveness of handling between air and the regeneration air (outside air) is very high.Term " cold-producing medium in coolant channel along roughly same direction overall flow " refers to, see on the whole, cold-producing medium flows along same direction in coolant channel basically, but cold-producing medium may be because of the turbulent flow local return in the part, perhaps can cause that flow direction oscillation changes because of bubble or pressure oscillation that instantaneous interruption produced.In the present embodiment, being forced to property ground flows along a direction under the pressurization of cold-producing medium in compressor 260.

When high temperature fluid was cooled, promptly when heat exchanger was used for the cooling down high-temperature fluid, heat exchanger effectiveness φ was defined as:

φ＝(TP1-TP2)/(TP1-TC1)

Wherein the high temperature fluid temperature at heat exchanger entrance place is represented with TP1, and the high temperature fluid temperature at heat exchanger outlet place represents that with TP2 the cryogen temperature at heat exchanger entrance place represents that with TC1 the cryogen temperature at heat exchanger outlet place is represented with TC2.When heat exchanger was used to heat cryogen, heat exchanger effectiveness φ was defined as:

φ＝(TC2-TC1)/(TP1-TC1)

Be used in the inner surface of the heat-exchange tube in evaporator section 251 and the condensation segment 252 and be preferably formed helicla flute, the sort of wire casing in the rifle gun barrel inner surface for example, thus obtain a high-performance heat transfer surface.The refrigerant liquid of heat-exchange tube of flowing through can drench its inner surface usually.Helicla flute can disturb the boundary layer of refrigerant liquid stream usually, thereby increases pyroconductivity.

Handle air first room 310 of flowing through.In first room 310, be installed in fin on the heat-exchange tube outer surface preferably with the arranged in form of fin, with flow through the flowing of fluid of first room 310 of interference.Similarly, the fin in second room 320 is also preferred so to be arranged, with flow through the flowing of fluid of second room 320 of interference.Fin is preferably made by aluminium or copper or their alloy.

At first describe cold-producing medium stream flowing in each device below, refer again to the operation that Fig. 3 describes heat pump HP1 with reference to Fig. 1.

In Fig. 1, the refrigerant vapour after cooled dose of compressor 260 compresses is introduced in the regeneration air heater (refrigerant condenser) 220 by the refrigerant vapour pipeline 201 that is connecting compressor row mouth.Refrigerant vapour after cooled dose of compressor 260 compresses can be compressed the effect of heat and heat up, and the heat in the refrigerant vapour can the thermal regeneration air.Heat is drawn from refrigerant vapour self, and refrigerant vapour is condensed.

Refrigerant condenser 220 has a refrigerant outlet, and it is connected to the inlet of the evaporator section 251A1 among the heat exchanger 300a by refrigerant path 202.Flow controller 330 is adjacent to evaporator section 251A1 and is arranged in the refrigerant path 202.

In Fig. 1, the condensation segment 252A1 that only shows evaporator section 251A1 and become a partner with it, they are placed between the flow controller 331 of flow controller 330 and heat exchanger 330a.Evaporator section 251A1 and condensation segment 252A1 are the minimalist configuration requirements, for example will settle a plurality of evaporator sections and condensation segment usually among the plane P A on a plane, such as the front with reference to Fig. 2 (a) and 2 (b) description.

The refrigerant liquid that flows out from refrigerant condenser (seeing it is heater from the angle of regeneration air) 220 is reduced pressure by flow controller 330, and the partly evaporation (flash distillation) by expanding.The refrigerant mixture of being made up of liquid and steam arrives evaporator section 251A1, flows and drenches inside pipe wall surface among the evaporator section 251A1 at this refrigerant liquid, and be evaporated, with the processing air cooling of first room 310 of will flowing through.

Evaporator section 251A1 and condensation segment 252A1 are configured to a pipe continuously.Specifically, because evaporator section 251A1 and condensation segment 252A1 be with the form setting of integral passage, therefore vaporized refrigerant vapour (and unevaporated refrigerant liquid) will flow among the condensation segment 252A2.At this moment, the flowed through outside air of second room 320 of the heat in the refrigerant vapour is drawn, and cold-producing medium is condensed.

As previously mentioned, heat exchanger 300a has the evaporator section that is made of the coolant channel that extends through first room 310 in the first plane P A and the condensation segment that is made of the coolant channel that extends through second room 320 (is a pair of at least, a pair of with 251A9 and 252A9 representative for example), also in the second plane P B, have condensation segment that constitutes by the coolant channel that extends through second room 320 and the evaporator section that constitutes by the coolant channel that extends through first room 310 (be a pair of at least, for example a pair of with 252B8 and 251B8 representative).Heat exchanger 300a has middle flow controller 331, its be arranged in cold-producing medium from the condensation segment 252A9 of plane P A flow to plane P B condensation segment 252B8 on the crossover position of process.Specifically, middle flow controller 331 is placed on the position of coolant channel when extending through second room 320.

In first embodiment, heat pump HP1 has and is used for the middle flow controller 331,332,333 that the condensation segment of Different Plane is linked to each other and is arranged in the many to condensation segment and evaporator section of flow controller 333 downstreams.Therefore the layout of heat pump HP1 makes the liquid refrigerant that flows out from the heat exchanger 300a condensation segment of finally can flowing through.

The outlet of the final condensation segment among the heat exchanger 300a is connecting an expansion valve 250 as second flow controller by refrigerant liquid line 204.Expansion valve 250 is connecting refrigerant evaporator (seeing it is cooling device from the angle of handling air) 210 by refrigerant lines 206.

Flow controller 250 can be placed in from condensation segment to refrigerant evaporator on any position between 210 the inlet, but preferably is placed in inlet next-door neighbour the place ahead of refrigerant evaporator 210.This is because be starkly lower than atmospheric temperature owing to flow out the temperature of the cold-producing medium of flow controller 250, so the heat-insulating material of refrigerant lines needs very thick.Condensed refrigerant liquid is reduced pressure by flow controller 250 in condensation segment, and occurs expanding and cooling.Afterwards, cold-producing medium is introduced in the refrigerant evaporator 210, is evaporated at this cold-producing medium, thereby utilizes heat of evaporation cooling processing air.Flow controller 330,250 can comprise eyelet, capillary, expansion valve or analog.Middle flow controller 331,332,333 is made of eyelet usually.

The cold-producing medium that flashes to steam in refrigerant evaporator 210 is introduced in the suction side of coolant compressor 260, and therefore carries out above-mentioned cycle period repeatedly.

Below with reference to Fig. 2 (b) evaporator section of heat exchanger 300a and the change procedure of the cold-producing medium in the condensation segment are described.Cold-producing medium flows among the evaporator section 251A1 with liquid state.Cold-producing medium can be the vaporized refrigerant liquid of part, thereby contains some steam attitude cold-producing mediums slightly.Refrigerant liquid is when flowing through evaporator section 251A1 processed air heat, and enters among the condensation segment 252A1 with the steam attitude that has increased.In condensation segment 252A1, cold-producing medium is with the thermal regeneration air.At this moment, heat is drawn from cold-producing medium self, and the cold-producing medium that is in the steam attitude is condensed, and cold-producing medium flows among next condensation segment 252A2 then.When cold-producing medium was flowed through condensation segment 252A2, heat continues to be reproduced air to be drawn from cold-producing medium, and was in the further condensation of cold-producing medium quilt of steam attitude.After this, cold-producing medium flows among next evaporator section 251A2.In this way, cold-producing medium flows through coolant channel, and changes phase simultaneously between steam attitude and liquid state.Like this, exchange between the processing air of the low-temperature heat source fluid of heat in being used as heat pump HP1 and the regeneration air as the high temperature heat source fluid among the heat pump HP1.

Next the operation of heat pump HP1 is described with reference to Fig. 3.Fig. 3 is as the mollier diagram under the situation of cold-producing medium at HFC134a.In this mollier diagram, transverse axis is represented enthalpy, and the longitudinal axis is represented pressure.

For illustrative purposes, suppose that coolant channel is made of the condensation segment 252C1 among the condensation segment 252B2 among a pair of evaporator section 251A1 among the plane P A and condensation segment 252A1, flow controller 331, the plane P B and evaporator section 251B2 and evaporator section 251B1 and condensation segment 252B1, flow controller 332, the plane P C and evaporator section 251C1 and evaporator section 251C2 and condensation segment 252C2, flow controller 333, the condensation segment 252D2 that is arranged in plane P D and evaporator section 251D2 and evaporator section 251D1 and condensation segment 252D1, finally arrives flow controller 250.

Represent the refrigerant condition in the exit of refrigerant evaporator 210 at Fig. 3 mid point a, this moment, cold-producing medium was rendered as the form of saturated vapor.The pressure of cold-producing medium is 4.2kg/cm ², temperature is 10 ℃, enthalpy is 148.83kcal/kg.Point b represent steam sucked by compressor 260 and compress after state, i.e. the state in compressor 260 exits.At a b place, the pressure of cold-producing medium is 19.3kg/cm ², temperature is 78 ℃, and is rendered as the form of superheated vapor.

Refrigerant vapour is cooled in refrigerant condenser 220, and arrives the state of representing with a c in mollier diagram.At a c place, cold-producing medium is rendered as the form of saturated vapor, and pressure is 19.3kg/cm ², temperature is 65 ℃.Under this pressure, cold-producing medium is further cooled and condensation, the state of representing with point of arrival d.At a d place, cold-producing medium is rendered as the form of saturated liquid, and has the identical temperature with some c place.The enthalpy of saturated liquid is 122.97kcal/kg.

Cold-producing medium is reduced pressure by flow controller 330, and among the evaporator section 251A1 among the inflow heat exchanger 330a.The state of this moment is represented with an e in mollier diagram.The temperature of refrigerant liquid is a little more than the temperature of outside air at this moment.The pressure of refrigerant liquid is according to first middle pressure of the present invention, promptly is 4.2kg/cm in the present embodiment ²With 19.3kg/cm ²Between median.Because liquid is partly evaporated, therefore this moment, refrigerant liquid was the mixture of liquid and steam.

In evaporator section 251A1, refrigerant liquid is evaporated under first middle pressure, and arrives the state of representing with a f1, and this point and is under the middle pressure between saturated liquid curve and saturated vapor curve.At a f1 place, though partially liq is evaporated, refrigerant liquid keeps sizable amount.

The cold-producing medium that is under the state of representing with a f1 flows among the condensation segment 252A1.In condensation segment 252A1, the flowed through outside air of second room 320 of heat is drawn from cold-producing medium, and cold-producing medium arrives the state of representing with a g1a.

The cold-producing medium that is under the g1a state is reduced pressure by flow controller 331, and arrives the state of representing with a g1b.At a g1b place, cold-producing medium has second middle pressure, and it is lower than a pressure at g1a place.Afterwards, heat is drawn from cold-producing medium in second room 320, and cold-producing medium arrives the state of representing with a h1 with the liquid ratio that has increased.Afterwards, cold-producing medium flows among the evaporator section 251B2, in the steam attitude ratio increase of this cold-producing medium, and arrives the state of representing with a f2.After this, cold-producing medium flows among the condensation segment 252B1.In condensation segment 252B1, the flowed through outside air of second room 320 of the heat in the cold-producing medium is drawn, and arrives the state of representing with a g1a.

Be in a cold-producing medium of g2a state and reduced pressure, and arrive the state of representing with a g2b by flow controller 332.At a g2b place, cold-producing medium has the 3rd middle pressure, and it is lower than a pressure at g2a place.Afterwards, draw in the cold-producing medium of heat from condensation segment 252C2, and cold-producing medium arrives the state of representing with a h2 with the liquid ratio that has increased.Afterwards, cold-producing medium flows among the evaporator section 251C2.

Cold-producing medium is by 333 decompressions of intermediate relief device, the coolant channel in flow through successively again evaporator section, condensation segment, condensation segment and the evaporator section, thereby the state that arrival is represented with a h4 in mollier diagram.In mollier diagram, some h4 is positioned on the saturated liquid curve.At this some place, the temperature of cold-producing medium is 30 ℃, and enthalpy is 109.99kcal/kg.

The refrigerant liquid at some h4 place is by flow controller 250 4.2kg/cm that reduces pressure ², this pressure is 10 ℃ of saturation pressures under the temperature.Cold-producing medium flows in the refrigerant evaporator 210 with the form of refrigerant liquid and steam mixture under 10 ℃ of temperature, from handling the air drawn heat, and is evaporated to saturated vapor at this cold-producing medium, to arrive the state of representing with an a in mollier diagram.The steam that is evaporated is sucked by compressor 260 again, thereby carries out above-mentioned cycle period repeatedly.

In heat exchanger 300a, as previously mentioned, cold-producing medium experiences in evaporator section 251 from an e to putting f1 or change from a h1 to the evaporating state of putting f2, and in condensation segment 252 experience from a f1 to putting g1a or changing from a g1b to the condensing state of putting h1.Because cold-producing medium transmits heat by evaporation and condensation, so pyroconductivity is very high.

Include compressor 260, refrigerant condenser (regeneration air heater) 220,

flow controller

330 and 250 and the compression heat pump HP1 of refrigerant evaporator 210 in, under the situation that is not provided with heat exchanger 300a, the cold-producing medium that is under the state of representing with a d in the refrigerant condenser 220 will return refrigerant evaporator 210 by flow controller.Therefore, refrigerant evaporator 210 utilizable enthalpy differences have only 148.83-122.97=25.86kcal/kg.Yet, to utilize according to the heat pump HP1 that includes heat exchanger 300a of the present invention, refrigerant evaporator 210 utilizable enthalpy differences are 148.83-109.84=38.84kcal/kg.Like this, under identical cooling load and power demand, the vapor volume that is recycled in the compressor can reduce by 33%.Therefore, the heat pump HP1 according to present embodiment can implement and well-known sub-cooled cycle identical operations.

The operation of the dehumidification air conditioner device that heat pump HP1 is housed is described below with reference to Fig. 4.The CONSTRUCTED SPECIFICATION aspect is please referring to Fig. 1.In Fig. 4, tactic alphabetical K-N and Q-U represent the state of air in each zone, and corresponding with the zone circle letter in the flow circuit diagram shown in Figure 1.Psychrometric chart among Fig. 4 also can be applied in as described later the dehumidification air conditioner device according to another embodiment of the present invention.

At first describe below and handle flowing of air A.In Fig. 4, suck in the hair-dryers 102 by handling air path 107 from the processing air (being in state K) in air conditioning space 101, and be transported in the desiccant wheel 103 by handling air path 108.Handling the drier that airborne moisture is dried in the dry element of agent runner 103 absorbs.Handle airborne absolute humidity and reduce, and its dry-bulb temperature can raise because of the effect of the absorption heat of drier, arrive state L so that handle air.Handle air by in first room 310 of handling air path 109 inflow heat exchanger 300a, managing air herein can be in the refrigerant cools of quilt evaporation in evaporator section 251 (Fig. 2) under the constant absolute humidity.Afterwards, handle air and arrive state M, and flow in the cooling device 210 by path 110.In cooling device 210, handling air can be further cooled under constant absolute humidity, and arrives N state.The processing air of this moment is dried and cooled off, thereby turns back in the air conditioning space 101 by conduit 111 with the form of processing air SA with suitable humidity and preference temperature.

Flowing of regeneration air B is described below.The regeneration air B (being in state Q) of space OA of coming from the outside is inhaled into by regeneration air path 124, and by in second room 320 of path 125 inflow heat exchanger 300a.In second room 320, by making cold-producing medium flow through evaporator section 25 1 and condensation segment 252 as coolant channel among the heat exchanger 300a, the processing air (being in state L) of regeneration air and first room 310 of flowing through is heat-shift indirectly.The result of heat exchange is that the dry-bulb temperature of regeneration air raises, and the state of arrival R.Afterwards, regeneration air is transported to refrigerant condenser (seeing it is heater from the angle of regeneration air) 220 by path 126, at this regeneration air dry-bulb temperature that is heated and raises, thus the state of arrival T.Afterwards, regeneration air is transported in the desiccant wheel 103 by path 127, draws (releases) at this in the drier of moisture from dry element and comes out, so that drier reduces.The absolute humidity of regeneration air has increased, and owing to consumed heat when drier absorbs moisture, so dry-bulb temperature reduced, thus the state of arrival U.As previously mentioned, regeneration air emits by path 128 with the form of exhaust EX subsequently.

From psychrometric chart shown in Figure 4 as can be seen, in front in the aircondition of Miao Shuing, be applied in the regeneration air so that required heat H, the heat q that draws from handle air of drier reduction and the driving energy h of compressor have such relation: H=q+h each other.

A kind of frame for movement of above-mentioned dehumidification air conditioner device is described below with reference to Fig. 5.In Fig. 5, dehumidification air conditioner device is contained in the rack 700.Rack 700 comprises a rectangle housing of for example being made by sheet metal, and have one be open in its vertical top top board central authorities be used to suck the inlet of handling air RA.A filter 501 is located in the inlet, is used for preventing that the dust in air conditioning space 101 from entering in the dehumidification air conditioner device.Hair-dryer 102 is arranged in rack 700 on the interior side direction of filter 501, and its inlet is communicated with the processing air intake of rack by filter 501.

Hair-dryer 102 has one and points to the vertically outlet of below, and desiccant wheel 103 is arranged in hair-dryer 102 belows, and rotation AX is vertically-oriented.Desiccant wheel 103 is connecting one as driver and the motor 105 that rotation is vertically-oriented by belt, chain or analog in the mode that can turn round, and the low speed rotation that can turn around with a few minutes.Since desiccant wheel 103 can be in generally horizontal plane around vertical-rotation-axis AX rotation, so the height of dehumidification air conditioner device can reduce, thereby can be compact.

The outlet of hair-dryer 102 is connecting desiccant wheel by path 10 8.Path 10 8 is separated with miscellaneous part by sheet metal, and this sheet metal can be similar in the rack 700 for example.Handle air flow through circular desiccant wheel 103 roughly half (semicircular area).

First room 310 of heat exchanger 300a is that evaporator section 251 is arranged in the below of half (semicircular area) of desiccant wheel 103, is used for processed air and flows through.The desiccant wheel 103 and first room 310 are connected to each other by path 109, and this path is made of the space between horizontally disposed the pipe (and fin mounted thereto) of the evaporator section that is arranged in horizontally disposed desiccant wheel 103 and Fig. 1.

The refrigerant evaporator 210 that has level cooling pipeline is arranged in first room, 310 belows.In Fig. 1, path 110 is made of the space between first room 310 and refrigerant evaporator 210.Since first room 310 and refrigerant evaporator 210 be each other entire combination together, so the space between them merges in heat exchanger 300a and the refrigerant evaporator 210.Below refrigerant evaporator 210, arranging that horizontal-extending on the path 111 is at the start-up portion of rack 700 bottoms.Path 111 changes direction and points upwards subsequently, and separates with path 109,108 by partition, and the top board that finally arrives rack 700 is the supply opening place of air SA, and this air supply opening opens wide stem for stem with the inlet of handling air RA.

The inlet that is used for introducing outside air OA is open in the bottom side plate of rack 700, and a filter 502 is located in this inlet, to stop the dust that contains in the outside air.A space that is formed on the filter 502 interior side directions is used as path 124, and compressor 260 is installed in this path.Though hair-dryer 140 is arranged between desiccant wheel 103 and the heat exchanger 300a in Fig. 1, hair-dryer 140 is to be arranged between desiccant wheel 103 and the regeneration air outlet, as described later in Fig. 5.Hair-dryer 140 can be placed in the described position any one, as long as can cause the regeneration air circulation.

Second room 320 of heat exchanger 300a vertically is arranged in the top of compressor 260.Condenser 220 is arranged in the top of second room 320 of heat exchanger 300a.In this example, have public fin on second room 320 of heat exchanger 300a and the condenser 220, and be configured to one.Middle flow controller 331,332,333 is installed on the end of the condensation segment that extends through second room 320, and arranges along rack 700.

Only about half of (semicircular area) of circular desiccant wheel 103 vertically is arranged in condenser 220 tops, is used to flow through regeneration air.

This later half zone that is positioned at desiccant wheel 103 vertically is used as path 128 in the space of top, is settling hair-dryer 140 in this path.Hair-dryer 140 has one and adjoins the outlet of handling in the top board that air intake is arranged in rack 700.The outlet of hair-dryer 140 is to be used for and will to be discharged into the mouth in extraneous space with the regeneration air of crossing.

Because heat exchanger 300a carries out heat conduction by the evaporation and the mode of condensation, and basically according to the heat exchange between countercurrent action realization processing air and the regeneration air, so heat pump HP1 and dehumidification air conditioner device can be with the size configurations of compactness.

Below with reference to the heat pump HP2 and CONSTRUCTED SPECIFICATION that the dehumidification air conditioner device of this heat pump be housed of Fig. 6 description according to second embodiment.Heat exchanger 300b is identical with heat exchanger according to first embodiment, just in the middle of flow controller 331,332,333 be arranged in the evaporator section.

Specifically, heat exchanger 300b has as coolant channel in the first plane P A and extends through the condensation segment of second room 320 and be used as coolant channel and extend through evaporator section (at least one pair of of first room 310, for example with 252A1 and 251A1 represent a pair of), also in the second plane P B, have as coolant channel and extend through the evaporator section of first room 310 and be used as coolant channel and extend through second room 320 condensation segment (at least one pair of, for example with 251B1 and 252B1 represent a pair of).Flow controller 331 in the middle of the crossover position of heat exchanger 300a in the evaporator section 251B1 of the evaporator section 251A1 of cold-producing medium from plane P A in plane P B flows is provided with.Specifically, middle flow controller 331 is placed on the position of coolant channel when extending through first room 310.

300a is the same with heat exchanger, in heat exchanger 300b, utilized in heat pump the periodically cold-producing medium of circulation, normally uses with their total amount, with alternately evaporator section by series connection and condensation segment heat-shift to group and repeatedly.Like this, as long as have sub-fraction to be evaporated and condensation in the cold-producing medium that flows, just can handle heat-shift between air and the regeneration air fully.Usually, in evaporator section, the sizable part in the refrigerant liquid keeps not evaporating.Therefore, even middle flow controller 331,332,333 is arranged in evaporator section, also can be at each plane (PA, PB, PC ...) in coolant channel in produce required pressure reduction.

Below with reference to the operation of Fig. 7 description according to the heat pump HP2 of second embodiment.In Fig. 7, to the conversion of an e identical with shown in Fig. 3, and no longer describe from an a.The cold-producing medium that is under the state of representing with an e among the heat exchanger 300b is the mixture of liquid and steam, and wherein a part of liquid evaporates under first middle pressure, describes with reference to Fig. 3 as the front.

Cold-producing medium continues evaporation in evaporator section, and point of arrival f1, and this is near the saturated vapor curve in the wet district in the mollier diagram.Cold-producing medium under this state flows in the condensation segment, and cold-producing medium is condensed at this.Afterwards, cold-producing medium point of arrival g1 is though this point also in wet district, approaches the saturated liquid curve.Afterwards, cold-producing medium flows in the evaporator section, shifts to saturated vapor curve in the wet district and point of arrival h1a.Before this point, cold-producing medium changes under first middle pressure basically.

The cold-producing medium that is under the state of representing with a h1a is reduced pressure by flow controller 331, and under second middle pressure point of arrival h1b.Specifically, the cold-producing medium of the evaporator section outflow that is used as coolant channel from plane P A will flow into being used as in the evaporator section of coolant channel among the plane P B.Cold-producing medium evaporates in evaporator section under second middle pressure, and point of arrival f2.Afterwards, cold-producing medium is alternatively vaporised and condensation repeatedly in a similar fashion, and by middle flow controller 333 decompressions.After this, cold-producing medium flow through evaporator section and condensation segment and arrive some g4 in the mollier diagram, this is corresponding to the some h4 among Fig. 3.In mollier diagram, some g4 is positioned on the saturated liquid curve.At that point, the temperature of cold-producing medium is 30 ℃, and enthalpy is 109.99kcal/kg.

The same with the situation among Fig. 3, the refrigerant liquid at some g4 place is by flow controller 250 4.2kg/cm that reduces pressure ², this pressure is 10 ℃ of saturation pressures under the temperature.Cold-producing medium flows in the refrigerant evaporator 210 with the form of refrigerant liquid and steam mixture under 10 ℃ of temperature, from handling the air drawn heat, and is evaporated to saturated vapor at this cold-producing medium, to arrive the state of representing with an a in mollier diagram.The steam that is evaporated is sucked by compressor 260 again, thereby carries out above-mentioned cycle period repeatedly.

In heat exchanger 300b, as previously mentioned, cold-producing medium hockets repeatedly, and the steam attitude changes and liquid the variation.Because cold-producing medium transmits heat by evaporation and condensation, therefore the same with heat exchanger 300a, pyroconductivity is very high.

Refrigerant evaporator 210 utilizable enthalpy differences are significantly greater than conventional heat pump.Therefore, under identical cooling load and power demand, the vapor volume that is recycled in the compressor can reduce by 33%, and is the same with situation among Fig. 3.

The operating in nature of dehumidification air conditioner device that heat pump HP2 is housed described identically with the front with reference to the psychrometric chart among Fig. 4, thereby no longer describe.

Heat pump HP2 and the frame for movement that the dehumidification air conditioner device of heat pump HP2 is housed according to second embodiment of the invention have been shown among Fig. 8.In the present embodiment, middle flow controller 331,332,333 is installed on the end of the evaporator section that extends through first room 310, and arranges along a partition, and this partition defines the part straight up of handling air path 111.Other mechanical details of present embodiment identical with shown in Fig. 5.

Below with reference to the heat pump HP3 and dehumidification air conditioner device that hot HP3 be housed of Fig. 9 description according to third embodiment of the invention.In the present embodiment, heat exchanger 300c who is used for heat-shift between the processing air that flows out desiccant wheel 103 and the regeneration air that flows into condenser 220 is separated into respect to the mobile heat exchanger 300c1 that is positioned at the upstream that handles air with respect to the mobile heat exchanger 300c2 that is positioned at the downstream of processing air.Heat exchanger 300c1 is corresponding to first heat exchanger according to the present invention, and heat exchanger 300c2 is corresponding to the 3rd heat exchanger according to the present invention.

With the same among first or second embodiment, heat exchanger 300c1 can be the heat exchanger of flow controller 331,332,333 in the middle of having.Yet in example shown in Figure 9, heat exchanger 300c1 does not have middle flow controller.In the present embodiment, coolant channel that alternately extends through first room 310 and second room 320 repeatedly comprises second condensation segment, second evaporator section, the 3rd condensation segment of bending, the 3rd evaporator section of first evaporator section, first condensation segment, bending.Heat exchanger 300c2 can be the heat exchanger of flow controller 331,332,333 in the middle of having.Among heat exchanger 300c1 and the heat exchanger 300c2 any one can be the heat exchanger of flow controller in the middle of having.

Heat pump HP3 is settling like this, and promptly the cold-producing medium that flows out from the 3rd condensation segment of heat exchanger 300c1 is introduced among the heat exchanger 300c2 by a pipeline of walking around heat exchanger 300c1.In the embodiment shown in fig. 9, the structure of heat exchanger 300c2 and heat exchanger 300c1 are identical.

From the pipeline that the 3rd condensation segment of heat exchanger 300c1 extends out, have a flow controller 340 as the 5th flow controller.Specifically, heat exchanger 300c1 is one another in series along the flow of refrigerant direction by flow controller 340 with heat exchanger 300c2 and is in the same place.The 5th flow controller 340 is connecting first evaporator section of heat exchanger 300c2.The 3rd evaporator section of heat exchanger 300c2 is connecting flow controller 250.

Be used for room that processed air flows through as the 5th room among the heat exchanger 300c2, being used among the heat exchanger 300c2 is reproduced room that air flows through as the 6th room.The processing air that flows out from desiccant wheel will flow into the 5th room from first room.The regeneration air of introducing from outside air will flow into second room from the 6th room, flow in the condenser 220 again.

The operation of heat pump HP3 is described below with reference to Figure 10.Before an e, identical among the operation of heat pump HP3 and first and second embodiment.The cold-producing medium at some e place evaporates on ground, the first middle pressure lower part in first evaporator section, and arrives the some f1 in the wet district.The cold-producing medium at some f1 place will be by the first and second condensation segment condensations, and arrival is positioned on the saturated liquid curve or near some g1.The partly evaporation in the second and the 3rd evaporator section of the cold-producing medium at some g1 place, and point of arrival f2.Cold-producing medium condensation in the 3rd condensation segment, and arrival is positioned on the saturated liquid curve or near some g2.

The cold-producing medium at some g2 place is reduced pressure by flow controller 340, and under second middle pressure point of arrival E.Afterwards, in first evaporator section of cold-producing medium inflow heat exchanger 300c2.After this, cold-producing medium changes state in the mode identical with cold-producing medium among the heat exchanger 300c1, and point of arrival G2, and this is corresponding to the some g4 among Fig. 3.Cold-producing medium is reduced pressure by flow controller 250, and the state at point of arrival j place.Next, heat pump HP3 with first and second embodiment in identical mode operate.

Heat pump HP3 and the frame for movement that the dehumidification air conditioner device of heat pump HP3 is housed according to third embodiment of the invention have been shown among Figure 11.In the present embodiment, flow controller 331,332,333 in the middle of heat pump is not with, but flow controller 340 is arranged between heat exchanger 300c1 and the heat exchanger 300c2.Other mechanical details in the present embodiment identical with shown in Fig. 5 and 8.

Below with reference to the heat pump HP4 and dehumidification air conditioner device that heat pump HP4 be housed of Figure 12 description according to four embodiment of the invention.In the present embodiment, heat exchanger 300d who is used for heat-shift between the processing air that flows out desiccant wheel 103 and the regeneration air that flows into condenser 220 is separated into respect to the mobile heat exchanger 300d1 that is positioned at the upstream that handles air with respect to the mobile heat exchanger 300d2 that is positioned at the downstream of processing air.Heat exchanger 300d1 is corresponding to first heat exchanger according to the present invention, and heat exchanger 300d2 is corresponding to second heat exchanger according to the present invention.

With the same among first or second embodiment, heat exchanger 300d1 can be the heat exchanger of flow controller 331,332,333 in the middle of having.Yet in example shown in Figure 12, heat exchanger 300d1 does not have middle flow controller.Heat exchanger 300d1 and heat exchanger 300d2 are substantially the same with the structure of heat exchanger 300c1 and heat exchanger 300c2.

According to the 3rd embodiment, heat exchanger 300c1 and heat exchanger 300c2 are together in series by flow controller 340.Yet according to present embodiment, heat exchanger 300d1 has corresponding flow controller 330A, the 330B of the inlet that is being connected them and corresponding flow controller 340A, the 340B of the outlet that is being connected them with heat exchanger 300d2, and is connected in parallel to each other and is arranging.Specifically, a refrigerant path 202 that extends out from condenser 220 branches into two paths that connecting

flow controller

330A, 330B

respectively.Flow controller

340A, 340B are connecting the refrigerant outlet of heat exchanger 300d1 and heat exchanger 300d2, and merge in the path 204 that is connecting flow controller 250.Among flow controller 250, the 340B any one can dispense.

The operation of heat pump HP4 is described below with reference to Figure 13.In Figure 13, identical in the conversion of a d and first, second and the 3rd embodiment.The cold-producing medium at some d place is diverted in two paths by path 202, with will be roughly half cold-producing medium be transferred among the flow controller 330A, the cold-producing medium that is left is transferred among the flow controller 330B.

Be transferred to cold-producing medium among the flow controller 330A by flow controller 330A reduce pressure first middle pressure and point of arrival e.The cold-producing medium at some e place evaporates on ground, the first middle pressure lower part in first evaporator section of heat exchanger 300d1, and arrives the some f1 in the wet district.The cold-producing medium at some f1 place will be by the first and second condensation segment condensations, and arrival is positioned on the saturated liquid curve or near some g1.The partly evaporation in the second and the 3rd evaporator section of the cold-producing medium at some g1 place, and point of arrival f2.Cold-producing medium condensation in the 3rd condensation segment, and arrival is positioned on the saturated liquid curve or near some g2.The cold-producing medium at some g2 place is by flow controller 340A and flow controller 250 decompressions, and point of arrival j1.The pressure at some j1 place equates with the evaporating pressure in the evaporimeter 210.

In a cold-producing medium at d place, be transferred to cold-producing medium among the flow controller 330B by flow controller 330B reduce pressure middle pressure lower and point of arrival E than first middle pressure.This be because, be used for the 3rd room that processed air flows through with respect to the mobile first room downstream that is placed in heat exchanger 300d1 of handling air among the heat exchanger 300d2, being used among the heat exchanger 300d2 is reproduced the 4th room that air the flows through mobile second room upstream that is placed in heat exchanger 300d1 with respect to regeneration air, so evaporating temperature and condensation temperature are lower.

The cold-producing medium that is under the E state changes state in the mode identical with cold-producing medium among the heat exchanger 300d1, and final arrival is positioned on the saturated liquid curve or near some G2.The cold-producing medium at some G2 place is by flow controller 340B and flow controller 250 decompressions, and point of arrival j.The pressure at some j place equates with the evaporating pressure in the evaporimeter 210.The cold-producing medium that mixes with the state at a j1, j place will evaporate in evaporimeter 210.

Heat pump HP4 and the frame for movement that the dehumidification air conditioner device of heat pump HP4 is housed according to four embodiment of the invention have been shown among Figure 14.In the present embodiment, flow controller 331,332,333 in the middle of heat pump HP4 is not with, but flow

controller

330A, 330B are being connected the corresponding inlet of heat exchanger 300d1 and heat exchanger 300d2, flow

controller

340A, 340B are connecting the corresponding outlet of heat exchanger 300d1 and heat exchanger 300d2.Other mechanical details in the present embodiment identical with according to first, second and the 3rd embodiment.

Below with reference to Figure 15 (a) and 15 (b) a kind of structure among the present invention first, second and the 3rd embodiment is described, institute do description mainly be at Fig. 2 (a) and 2 (b) in difference.Figure 15 (a) is the vertical view of the heat exchanger done along the flow direction of handling air and regeneration air, and Figure 15 (b) is perpendicular to the side view of the heat exchanger that the flow direction of handling air and regeneration air does.In Figure 15 (a), to handle air and flow to paper from the observer, regeneration air flows to the observer from paper.In this heat exchanger, heat-exchange tube is arranged as eight row respectively in each plane P A, PB, PC, PD, and described plane is perpendicular to the flow direction of handling air and regeneration air.Like this, described pipe is arranged as four row, eight row along the flow direction of handling air and regeneration air.

Flow controller 331 is arranged in from the first plane P A on the position of next plane P B transition in the middle of one.Flow controller 332 (not shown) are arranged in from plane P B on the position of plane P C transition in the middle of one.Flow controller 333 is arranged in from plane P C on the position of plane P D transition in the middle of one.A flow controller is being located at a plane under the locational situation of next plane transition, and the pipe among the plane P A is capable can be arranged in the multilayer.In this structure, arranging a flow controller under every course on the position of one deck transition respectively.Before the middle flow controller and plane afterwards is called first and second planes respectively.

The heat exchanger that has four layers of (row) pipe of eight row shown in Figure 15 (a) and 15 (b) respectively can be connected in parallel to each other or arranged in series with respect to the flow direction of handling air and regeneration air, and this depends on the amount of handling air and regeneration air.

As example, in mollier diagram shown in Figure 3, even cold-producing medium evaporation and condensation and enter in the sub-cooled district that exceeds the saturated liquid curve repeatedly, cycle period also can carry out.Yet, consider the heat exchange of handling between air stream and the regeneration airflow, cold-producing medium is preferably in wet district and changes phase.Therefore, for Fig. 2 or heat exchanger shown in Figure 15, with heat transfer area in first evaporator section that flow controller 330 the links to each other heat transfer area in next evaporator section.In addition and since flow into cold-producing medium in the flow controller 250 be preferably placed at saturated or the sub-cooled district in, the therefore heat transfer area of the heat transfer area of the condensation segment that links to each other with flow controller 250 in the last condensation segment.

Below with reference to Figure 16 relation between the progression that total moisture content efficient (rate of heat exchange) and heat-exchange tube separated by middle flow controller along the flow direction of handling air or regeneration air is described, described progression can refer to the number of plies or line number, and corresponding to the number of planes among Figure 15.As example, if every grade temperature efficiency is 0.400, then three grades total moisture content efficient is about 0.67, and level Four is about 0.72, and it is about 0.80 that Pyatyi is about 0.77, six grade.Further increasing of progression can not cause total moisture content efficient obviously to improve.Therefore, from cost-efficient viewpoint, preferably use about level Four.

Among superincumbent each embodiment, compressor is as booster.Yet, booster can comprise the following element that is used in the absorption type freezer unit: an absorber, it is used for by adsorbent solution absorption refrigeration agent, a pump, it is used for having absorbed the adsorbent solution pressurization of cold-producing medium, and a generator, it is used for producing cold-producing medium from pressurized adsorbent solution.

Industrial applicability

As previously mentioned, according to the present invention since cold-producing medium repeatedly alternating current cross and extend in Coolant channel in first and second rooms, the system of therefore flow through evaporimeter or condenser Cryogen is Multiple through then out first and second rooms, and repeatedly utilized, so that Low Temperature Thermal Heat-shift between source fluid and the high temperature heat source fluid. Like this, although cold-producing medium extending Be evaporated in the coolant channel by first room, it can not parch fully yet.

Claims

1. heat pump, its interior booster, a condenser and an evaporimeter are interconnecting by a refrigerant path, and above-mentioned heat pump comprises:

Be arranged in being used in the refrigerant path links to each other above-mentioned condenser with above-mentioned evaporimeter utensil, it is used under middle pressure alternatively vaporised and condensating refrigerant repeatedly, and above-mentioned middle pressure is will be by the pressure of above-mentioned booster supercharging and between by the pressure after the above-mentioned booster supercharging.

2. dehumidification air conditioner device, it comprises:

A moisture absorbing device, it is used for remove handling airborne moisture, and is reproduced air and therefrom siphons away moisture and obtain reduction; And

A heat pump, it has a condenser, evaporimeter and a tubule group that above-mentioned condenser is linked to each other with above-mentioned evaporimeter;

Wherein above-mentioned tubule group is settled like this, promptly can with by above-mentioned condenser condenses cold-producing medium introduce in the above-mentioned evaporimeter, and cold-producing medium is alternately contacted with above-mentioned regeneration air with above-mentioned processing air.

3. heat pump, it comprises:

A booster, the pressure of its cold-producing medium that is used to raise;

An evaporimeter, its utilization will be by the heat of evaporation of the cold-producing medium of above-mentioned booster supercharging cooling low-temperature heat source fluid;

A condenser, it utilizes by the condensation heat of the cold-producing medium after above-mentioned booster supercharging heating high temperature heat source fluid; And

First heat exchanger, it is used to make the above-mentioned low-temperature heat source fluid and the above-mentioned high temperature heat source fluid that are positioned at above-mentioned vaporizer upstream to carry out heat exchange;

Wherein above-mentioned first heat exchanger has first room that is used for being flow through by above-mentioned low-temperature heat source fluid, be used for second room and a coolant channel that extends through above-mentioned first room and above-mentioned second room of being flow through by above-mentioned high temperature heat source fluid, above-mentioned coolant channel is connecting above-mentioned condenser by the first throttle device, and alternately extend through above-mentioned first room and above-mentioned second room repeatedly, be connected to above-mentioned evaporimeter by second flow controller again.

4. heat pump according to claim 3 is characterized in that, above-mentioned first room and above-mentioned second room are settled like this, and promptly above-mentioned low-temperature heat source fluid and above-mentioned high temperature heat source fluid flow in the mode of adverse current;

Above-mentioned coolant channel in above-mentioned first room and above-mentioned second room has: be arranged at least one pair of the first room extension and the second room extension on first plane, above-mentioned first plane is approximately perpendicular to the flow direction of above-mentioned low-temperature heat source fluid and above-mentioned high temperature heat source fluid; Be arranged at least one pair of the first room extension and the second room extension on second plane, above-mentioned second plane is different with above-mentioned first plane and be approximately perpendicular to the flow direction of above-mentioned low-temperature heat source fluid and above-mentioned high temperature heat source fluid; And locational middle flow controller that is arranged in above-mentioned first plane to the above-mentioned second plane transition.

5. according to claim 3 or 4 described heat pumps, also comprise second heat exchanger, it is used to make the above-mentioned low-temperature heat source fluid and the above-mentioned high temperature heat source fluid that are positioned at above-mentioned vaporizer upstream to carry out heat exchange;

Wherein above-mentioned second heat exchanger has the 3rd room that is used for being flow through by above-mentioned low-temperature heat source fluid, be used for the 4th room and a coolant channel that extends through above-mentioned the 3rd room and above-mentioned the 4th room of being flow through by above-mentioned high temperature heat source fluid, above-mentioned coolant channel is connecting above-mentioned condenser by the 3rd flow controller, and alternately extend through above-mentioned the 3rd room and above-mentioned the 4th room repeatedly, be connected to above-mentioned evaporimeter by the 4th flow controller again;

Above-mentioned the 3rd room with respect to above-mentioned low-temperature heat source fluid placement in the above-mentioned first room downstream, above-mentioned the 4th room with respect to above-mentioned high temperature heat source fluid placement in the above-mentioned second room upstream.

6. according to claim 3 or 4 described heat pumps, also comprise the 3rd heat exchanger, it is used to make the above-mentioned low-temperature heat source fluid and the above-mentioned high temperature heat source fluid that are positioned at above-mentioned vaporizer upstream to carry out heat exchange;

Wherein above-mentioned the 3rd heat exchanger has the 5th room that is used for being flow through by above-mentioned low-temperature heat source fluid, be used for the 6th room and a coolant channel that extends through above-mentioned the 5th room and above-mentioned the 6th room of being flow through by above-mentioned high temperature heat source fluid, above-mentioned coolant channel is connecting the coolant channel of above-mentioned first heat exchanger by the 5th flow controller, and alternately extend through above-mentioned the 5th room and above-mentioned the 6th room repeatedly, be connected to above-mentioned evaporimeter by above-mentioned second flow controller again;

Above-mentioned the 5th room with respect to above-mentioned low-temperature heat source fluid placement in the above-mentioned first room downstream, above-mentioned the 6th room with respect to above-mentioned high temperature heat source fluid placement in the above-mentioned second room upstream.

7. dehydrating unit, it comprises:

One according to arbitrary described heat pump in the claim 3 to 6; And

A moisture absorbing device, it in the upstream of above-mentioned first heat exchanger, and has the drier that is used for from above-mentioned low-temperature heat source absorption of fluids moisture with respect to above-mentioned low-temperature heat source fluid placement.