WO2015037236A1 - 吸着器 - Google Patents
吸着器 Download PDFInfo
- Publication number
- WO2015037236A1 WO2015037236A1 PCT/JP2014/004669 JP2014004669W WO2015037236A1 WO 2015037236 A1 WO2015037236 A1 WO 2015037236A1 JP 2014004669 W JP2014004669 W JP 2014004669W WO 2015037236 A1 WO2015037236 A1 WO 2015037236A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat medium
- tube
- medium pipe
- heat
- groove
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B35/00—Boiler-absorbers, i.e. boilers usable for absorption or adsorption
- F25B35/04—Boiler-absorbers, i.e. boilers usable for absorption or adsorption using a solid as sorbent
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
- F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/08—Tubular elements crimped or corrugated in longitudinal section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
- F28F2255/18—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes sintered
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
Definitions
- This disclosure relates to an adsorber.
- This adsorber includes a heat medium tube through which a heat medium flows, a porous sintered body joined to the outer surface of the heat medium tube, and an adsorbent held by the sintered body.
- a heat medium tube a smooth tube having no grooves on the inner surface and the outer surface is used.
- the sintered body is obtained by sintering metal powder so that the metal powder is bonded together and the metal powder and the heat medium tube are bonded while forming a gap between the metal powders.
- the heat transfer between the adsorbent and the heat medium tube is improved by holding the adsorbent in the sintered body.
- the heat transfer between the adsorbent and the heat medium flowing in the heat medium pipe greatly contributes to the adsorption capacity of the adsorber when the adsorbent adsorbs or desorbs the gas phase refrigerant. For this reason, it is required to improve heat transfer between the adsorbent and the heat medium.
- the outer surface of the heat medium tube is smooth, so that the metal powder shrinks greatly during sintering.
- the metal powder largely moves on the interface with the heat medium tube, so that the bonding between the metal powder and the outer surface of the heat medium tube is hindered, and the bonding area between the metal powder and the heat medium tube is reduced.
- the inventors of the present application have found that there is a problem that the thermal resistance between the metal powder and the heat medium pipe is increased. Further, since the inner surface of the heat medium pipe is smooth, there is a problem that the heat transfer coefficient between the heat medium and the heat medium pipe is low.
- an object of the present disclosure is to provide an adsorber capable of improving heat transfer on both the inner side and the outer side of the heat medium pipe as compared with the conventional adsorber described above.
- the adsorber of the present disclosure includes: A heat medium pipe through which the heat medium flows, A porous sintered body joined to the outer surface of the heat medium tube and sintered with metal powder; With an adsorbent held in a sintered body, The heat medium tube has a groove on the outer surface and a groove on the inner surface.
- the groove is provided on the outer surface of the heat medium tube, the shrinkage of the metal powder during sintering can be suppressed as compared with the case where the outer surface is smooth. For this reason, the joining area of a metal powder and a heat medium pipe
- the groove is provided on the inner surface of the heat medium pipe, the heat transfer area can be increased compared to the case where the inner surface is smooth, and the heat transfer coefficient between the heat medium flowing in the heat medium pipe and the heat medium pipe is increased. Can be improved. Therefore, according to the present disclosure, it is possible to improve heat transfer on both the inside and outside of the heat medium pipe.
- FIG. 1 is a front view of an adsorber according to the first embodiment of the present disclosure.
- FIG. 2 is a cross-sectional view taken along line II-II in FIG. 3 is a cross-sectional view taken along the line III-III in FIG.
- FIG. 4 is an external view of the heat medium pipe in the first embodiment.
- FIG. 5 is a schematic view of a sintered body and an adsorbent on the outer surface of the heat medium pipe in the first embodiment.
- FIG. 6 is a flowchart showing manufacturing steps of the adsorber according to the first embodiment.
- FIG. 7 is a schematic view of a sintered body and an adsorbent on the outer surface of the heat medium pipe in Comparative Example 1.
- FIG. 1 is a front view of an adsorber according to the first embodiment of the present disclosure.
- FIG. 2 is a cross-sectional view taken along line II-II in FIG. 3 is a cross-sectional view taken along the line III-III in FIG.
- FIG. 8 is an SEM photograph showing the joint location between the heat medium tube and the sintered body in the first embodiment.
- FIG. 9 is an SEM photograph showing the joint location between the heat medium tube and the sintered body in Comparative Example 1.
- FIG. 10 is a diagram showing the relationship between the ratio of the groove depth (hi / di) of the inner surface to the inner diameter of the heat medium tube and the heat transfer coefficient ratio to the heat transfer coefficient of the smooth tube in the first embodiment.
- FIG. 11 is a diagram illustrating the relationship between the ratio of the groove depth (hi / di) of the inner surface to the inner diameter of the heat medium tube and the heat transfer coefficient ratio to the heat transfer coefficient of the smooth tube in the first embodiment.
- FIG. 12 is a diagram showing the relationship between the ratio of the groove depth (hi / di) of the inner surface to the inner diameter of the heat medium tube and the adsorption capacity ratio to the adsorption capacity of the smooth tube in the first embodiment.
- FIG. 13 is a graph showing the relationship between the ratio of the groove depth (hi / di) of the inner surface to the inner diameter of the heat medium tube in Comparative Example 2 and the adsorption capability ratio to the adsorption capability of the smooth tube.
- FIG. 14 is a diagram showing a relationship between the ratio of the groove depth (hi / di) of the inner surface to the inner diameter of the heat medium tube and the COP ratio of the smooth tube to the COP in the first embodiment.
- FIG. 15 is a diagram showing the relationship between the ratio (hi / di) of the groove depth of the inner surface to the inner diameter of the heat medium tube in the first embodiment and the plate thickness ratio of the heat medium tube before grooving.
- FIG. 16 is an external view of a heat medium tube according to the second embodiment of the present disclosure.
- the adsorber of the present embodiment is applied to an air conditioner for vehicles and the like.
- the adsorber 1 includes an adsorption heat exchange unit 2, a casing 3, first and second plates 4 and 5, and first and second tanks 6 and 7. Yes.
- the adsorption heat exchange unit 2 includes a plurality of heat medium tubes 21 through which a heat medium such as water, an antifreeze liquid, and a refrigerant flows, a porous sintered body 22 joined to an outer surface 21a of the heat medium pipe 21, and a sintered body 22 And the adsorbent 23 held in the tank.
- a heat medium such as water, an antifreeze liquid, and a refrigerant flows
- a porous sintered body 22 joined to an outer surface 21a of the heat medium pipe 21, and a sintered body 22 And the adsorbent 23 held in the tank.
- the heat medium tubes 21 are cylindrical tubes having a circular cross section, and are arranged in parallel with each other at a predetermined interval.
- tube 21 is comprised with the metal excellent in heat conductivity, for example, copper, copper alloy.
- the sintered body 22 is disposed around each of the plurality of heat medium tubes 21 and covers the entire outer circumferential direction of each heat medium tube 21.
- each heat medium tube 21 has grooves 211 and 212 on both the outer surface 21a and the inner surface 21b.
- the groove 211 on the outer surface 21 a and the groove 212 on the inner surface 21 b are both spiral grooves and extend in a direction intersecting the longitudinal direction (axial direction) of the heat medium pipe 21.
- the groove 211 on the outer surface 21a and the groove 212 on the inner surface 21b have the same shape, and the widths wo and wi and the depths ho and hi are the same.
- channel 211 of the outer surface 21a is for suppressing shrinkage
- the sintered body 22 is formed so that the metal powders 22 a are bonded to each other while a gap is formed between the metal powders 22 a, and the metal powder 22 a and the heat medium pipe 21 are bonded to each other.
- the powder 22a is sintered.
- the sintered body 22 has a three-dimensional network structure.
- a metal that is more excellent in thermal conductivity than the adsorbent 23, such as copper or copper alloy, and that has a fibrous shape is used.
- the adsorbent 23 is a solid material that adsorbs water vapor as a gas phase refrigerant. As shown in FIG. 5, the adsorbent 23 is disposed in the voids of the sintered body 22, and is in the form of particles having a smaller particle diameter than the voids of the sintered body 22. As the adsorbent 23, silica gel, zeolite, or the like is used.
- the casing 3 accommodates the adsorption heat exchange part 2 inside.
- the casing 3 has a cylindrical shape having a lower end side opening and an upper end side opening.
- the lower end opening and the upper end opening of the casing 3 are sealed with first and second plates 4 and 5.
- the first and second plates 4 and 5 are formed with a plurality of through holes through which the heat medium pipe 21 can pass. End portions of the heat medium pipe 21 are inserted into the through holes of the first and second plates 4 and 5.
- the heat medium pipe 21 and the first and second plates 4 and 5 are joined in an airtight manner. In this way, the casing 3 and the first and second plates 4 and 5 make the outside of the heat medium pipe 21 a sealed space, thereby forming a vacuum container.
- the inside of this vacuum vessel is configured so that no other gas exists other than water vapor.
- the first and second tanks 6 and 7 are tanks for distributing the heat medium to the plurality of heat medium tubes 21 and merging the heat medium from the plurality of heat medium tubes 21.
- a heat medium inflow pipe 10 is provided in the lower first tank 6.
- the upper second tank 7 is provided with a heat medium outlet pipe 11. For this reason, the heat medium flowing into the first tank 6 flows out of the second tank 7 through the plurality of heat medium tubes 21.
- the upper part of the casing 3 is provided with a steam inflow pipe 8 and an outflow pipe 9. For this reason, at the time of adsorption of water vapor, the water vapor flows into the casing 3 through the inflow pipe 8 from the evaporator side. At the time of desorption of water vapor, the water vapor desorbed from the adsorbent 23 flows out from the outflow pipe 9 to the condenser side.
- the adsorber 1 configured as described above, when water vapor is adsorbed, water vapor generated by the evaporation of water in the evaporator flows into the adsorber 1 and is adsorbed by the adsorbent 23. Since the adsorbent 23 adsorbs water vapor, the vacuum state inside the evaporator is maintained, and water can continue to evaporate inside the evaporator. At this time, when the adsorbent 23 reaches a high temperature, the water vapor is no longer adsorbed by the adsorbent 23, so that the adsorbent 23 is cooled by the cooling heat medium flowing through the heat medium pipe 21.
- the heating medium pipe 21 is switched so that the heating medium flows.
- the adsorbent 23 is heated by the heating heat medium flowing through the heat medium pipe 21, and the water vapor adsorbed on the adsorbent 23 is desorbed.
- the desorbed water vapor is condensed into water by the condenser, and the condensed water is returned to the evaporator.
- the adsorber 1 is manufactured by sequentially performing the first assembly step S100, the filling step S110, the second assembly step S120, and the heating step S130.
- the first assembly step S100 a part of each component of the adsorber 1 is assembled.
- at least the components of the adsorption heat exchange unit 2 excluding one of the first and second plates 4 and 5 and the casing 3 are assembled so that the metal powder 22a can be filled in the next filling step S110.
- the heat medium pipe 21 having spiral grooves 211 and 212 formed on both the outer surface 21a and the inner surface 21b is used.
- a method of forming the spiral grooves 211 and 212 a general processing method can be adopted.
- a method is adopted in which a mechanical force is applied to the outer surface of the smooth tube to deform both the outer surface and the inner surface at the same time, thereby forming an uneven shape on the outer surface and the inner surface.
- the spiral grooves 211 and 212 can be easily formed.
- spiral grooves 211 and 212 having the same shape are formed on both the outer surface 21a and the inner surface 21b of the heat medium pipe 21.
- the mixed powder of the metal powder 22a and the adsorbent 23 is filled inside the casing 3 and outside each heat medium pipe 21.
- the component parts of the adsorber 1 other than the component parts assembled in the first assembly step are assembled.
- the components of the adsorber 1 are brazed to each other and the metal powder 22a is sintered.
- maintains the adsorption agent 23 inside is formed by the metal powder 22a and the heat-medium pipe
- the manufacturing method of the adsorption device 1 is not limited to the above-described manufacturing method, and the above-described manufacturing method may be changed.
- the above-described manufacturing method may be changed.
- the adsorbent 23 is held by the sintered body 22 by performing a step of filling the casing 3 with a solution containing the adsorbent 23 and a drying step after the heating step S130.
- other steps may be added.
- a spiral groove 211 is provided on the outer surface 21 a of the heat medium pipe 21.
- the spiral groove 211 is a groove that is provided on the outer surface 21 a of the heat medium pipe 21 and extends in a direction intersecting the axial direction of the heat medium pipe 21 (a direction not parallel to the axial direction). In other words, the spiral groove 211 extends in a spiral shape around the central axis of the heat medium pipe 21.
- a plurality of irregularities (valleys and peaks) are formed in the axial direction of the heat medium pipe 21 by the spiral grooves 211.
- the number of spiral grooves 211 provided on the outer surface 21a of the heat medium pipe 21 is one, but the number of spiral grooves 211 is not limited to one. That is, a plurality of spiral grooves 211 may be provided on the outer surface 21 a of the heat medium pipe 21.
- a plurality of spiral grooves 211 extending spirally around the central axis of the heat medium pipe 21 may be provided side by side in the axial direction on the outer surface 21 a of the heat medium pipe 21.
- another spiral groove spaced from the spiral groove 211 may be provided on the right or left side of the spiral groove 211 shown in FIG.
- the spiral groove 212 is also provided on the inner surface 21b of the heat medium pipe 21 in the same manner as the outer surface 21a. Accordingly, the heat transfer area can be increased and the stirring action by the swirling flow can be generated as compared with Comparative Example 1 in which the inner surface 21b of the heat medium pipe 21 shown in FIG. 7 is smooth. The heat transfer coefficient between the heat medium flowing through the heat medium 21 and the heat medium pipe 21 can be improved. As described above with respect to the spiral groove 211 on the outer surface 21a of the heat medium pipe 21, a plurality of spiral grooves may be provided also on the inner surface 21b of the heat medium pipe 21.
- spiral groove tube (hereinafter also referred to simply as a spiral groove tube) and a smooth tube with spiral grooves on both the inner and outer surfaces as heat medium tubes, and adsorb metal powder.
- the mixed powder of the agent was placed on the outer surface of the heat medium tube and sintered.
- the spiral groove tube used has the same groove shape on the outer surface and the inner surface.
- the spiral groove tube and the smooth tube are copper tubes, and the metal powder is copper powder.
- the Reynolds number (Re) was set to 500 and 1500.
- the measurement conditions are cold water 30 ° C. and hot water 40 ° C.
- the smooth tube and the spiral groove tube used are in a state in which a sintered body and an adsorbent are not provided on the outside.
- the vertical axis represents the ratio of the heat transfer coefficient of the spiral groove tube to the heat transfer coefficient of the smooth tube.
- the heat transfer coefficient ratio exceeds 1, and it can be seen that the heat transfer coefficient of the spiral groove tube is improved as compared with the smooth tube.
- Fig. 12 shows the calculation results.
- the adsorption capacity ratio exceeded 1 when hi / di> 0.058, and the adsorption capacity ratio exceeded 1.2 when hi / di ⁇ 0.099.
- the pipe inner diameter di and the inner groove depth hi of the spiral groove pipe preferably satisfy the relationship of hi / di> 0.058, and more preferably satisfy the relationship of hi / di ⁇ 0.099.
- an adsorber in which a porous sintered body is bonded to the outer surface of the tube has a low thermal resistance on the outside of the tube, and therefore the adsorption capacity is greatly improved by promoting heat transfer on the inside of the tube. Therefore, the adsorption capability is dramatically improved by the heat transfer enhancement by the spiral groove 212 on the tube inner surface 21b.
- the porous sintered body 22 is joined to the tube outer surface 21a, and is adsorbed inside the sintered body 22. This is a characteristic effect of the adsorber 1 in which the agent 23 is held.
- the calculation result of the adsorption capacity ratio shown in FIG. 12 uses the thermal resistance value when a smooth tube is used as the thermal resistance value outside the pipe.
- the thermal resistance on the outside of the tube is lower than when a smooth tube is used. Therefore, when hi / di ⁇ 0.099, adsorption is performed. It is easily estimated that the capability is further improved than the result shown in FIG.
- the COP is calculated based on the adsorption capacity as an output and the amount of cold as input heat necessary for it. It can be said that the smaller the amount of heat necessary to exhibit the same adsorption capacity, the higher the energy saving effect.
- the amount of cold is the amount of cold necessary to switch the adsorbent from the desorbed state (heated state) to the adsorbed state (cooled state), and is necessary to cool the heat generated by the adsorbent itself during adsorption. And the amount of cooling required to cool the heat capacity of the entire adsorber so that it is cooled from the heated state. For this reason, COP is calculated by the adsorption capacity, the calorific value of the adsorbent itself during adsorption, and the heat capacity of the entire adsorber. The calorific value is obtained by multiplying the adsorption capacity by a predetermined coefficient, and is obtained from the adsorption capacity. The heat capacity is determined from the weight of the heat medium tube.
- FIG. 14 shows the result of calculating the COP ratio of the spiral groove tube (that is, the spiral groove tube having spiral grooves on both the inner surface and the outer surface) relative to the COP of the smooth tube, using the adsorption capacity ratio shown in FIG.
- the plate thickness of the spiral groove tube after grooving was calculated as the same regardless of the groove depth. Specifically, as shown in FIG. 15, as the groove is deepened, the plate thickness of the smooth tube before grooving is increased so as to compensate for the thinning due to grooving.
- the thickness ratio on the vertical axis in FIG. 15 is the ratio between the thickness of the smooth tube and the thickness of the smooth tube before grooving in the spiral groove tube.
- the helical groove tube of this embodiment increases the weight of the heat medium tube and increases the heat capacity as the groove is deepened. As can be seen from the above formula, COP deteriorates as the heat capacity increases.
- the range of hi / di there are a range in which the COP ratio exceeds 1 and a range in which the COP ratio is lower than 1.
- the COP ratio exceeds 1 when 0.070 ⁇ hi / di ⁇ 0.250. Therefore, in order to obtain an energy saving effect, the relationship of 0.070 ⁇ hi / di ⁇ 0.250 is established for the pipe inner diameter di and the inner groove depth hi of the spiral groove pipe having spiral grooves on both the inner surface and the outer surface. It is preferable to set so as to satisfy.
- the heat medium pipe 21 is formed with bellows-shaped grooves 213 and 214 formed on both the outer surface 21a and the inner surface 21b.
- the grooves 213 and 214 extend in a direction intersecting the axial direction of the heat medium pipe 21, more specifically, in a direction orthogonal to the axial direction of the heat medium pipe 21, and a plurality of grooves 213 and 214 are provided in the axial direction of the heat medium pipe 21. Is provided.
- a plurality of grooves 213 extending in the circumferential direction of the heat medium pipe 21 are provided in the outer surface 21 a of the heat medium pipe 21 in the axial direction, and the heat medium pipe 21 is provided on the inner surface 21 b of the heat medium pipe 21.
- a plurality of grooves 214 extending in the circumferential direction are provided side by side in the axial direction. Therefore, these grooves 213 and 214 also extend in a direction intersecting the axial direction of the heat medium pipe 21 (more specifically, a direction orthogonal to the axial direction). For this reason, also by this embodiment, the same effect as a 1st embodiment is acquired.
- the grooves provided in the outer surface 21 a and the inner surface 21 b of the heat medium tube 21 may extend in a direction parallel to the axial direction of the heat medium tube 21.
- shrinkage of the metal powder 22a in the outer peripheral direction of the heat medium tube 21 during sintering can be suppressed.
- tube 21 can be increased, and the thermal resistance of the outer side of the heat-medium pipe
- the heat transfer area of the inner surface 21b of the heat medium pipe 21 can be increased as compared with the case where the inner surface 21b of the heat medium pipe 21 is smooth. The heat transfer coefficient with the medium pipe 21 can be improved.
- the groove of the outer surface 21a and the groove of the inner surface 21b of the heat medium pipe 21 may not be the same shape, but both are arranged in the axial direction of the heat medium pipe 21 as in the first and second embodiments. It is preferable to extend in the intersecting direction.
- the shrinkage of the metal powder 22 a in the axial direction of the heat medium pipe 21 is larger than the shrinkage of the metal powder 22 a in the outer peripheral direction of the heat medium pipe 21.
- the outer surface 21a of the heat medium pipe 21 is provided with a groove extending in the direction intersecting the axial direction, and the shrinkage of the metal powder 22a in the axial direction is suppressed, thereby reducing the heat resistance outside the heat medium pipe 21. The effect of lowering becomes greater.
- the shape of the metal powder 22a is not limited to a fiber shape, and may be other shapes such as a spherical shape as long as a porous sintered body can be formed.
- the gas phase refrigerant is not limited to water vapor, and other gas phase refrigerants may be employed.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Sorption Type Refrigeration Machines (AREA)
- Rigid Pipes And Flexible Pipes (AREA)
Abstract
Description
内部を熱媒体が流れる熱媒体管と、
熱媒体管の外面に接合され、金属粉が焼結してなる多孔質の焼結体と、
焼結体に保持された吸着剤とを備え、
熱媒体管は、外面に溝が設けられているとともに、内面に溝が設けられている。
本実施形態の吸着器は、車両用などの空調装置に適用されるものである。図1~3に示すように、この吸着器1は、吸着熱交換部2と、ケーシング3と、第1、第2プレート4、5と、第1、第2タンク6、7とを備えている。
熱媒体管として内面と外面の両方にらせん溝を備えたらせん溝管(以下、単にらせん溝管とも称する)と平滑管の両方を用意し、金属粉と吸着剤の混合粉末を熱媒体管の外面に配置して焼結させた。このとき、使用したらせん溝管は、外面と内面の溝形状が同じものである。らせん溝管と平滑管は銅管であり、金属粉は銅粉である。
熱媒体管として内面と外面の両方にらせん溝を備えたらせん溝管と平滑管とを用意し、熱媒体管と熱媒体との間の熱伝達率をウィルソンプロット法により測定した。用いた平滑管およびらせん溝管の管内径di、らせん溝管のらせん溝条数および内面の溝深さhiを表1に示す。らせん溝管は、外面と内面の溝形状が同じものである。
図10、11に示すRe=500、1500のときの熱伝達率比を用いて、吸着シミュレータにて、平滑管の吸着能力に対するらせん溝管の吸着能力比を算出した。hi/di>0.15の範囲の熱伝達率比については、図10、11に示す熱伝達率比を一次近似した推定値を用いた。この算出結果は、管外面に多孔質の焼結体が接合され、この焼結体の内部に吸着剤が保持された状態のものである。ただし、管外側の熱抵抗値として、内面と外面の両方にらせん溝を備えたらせん溝管においても、平滑管と同じものを用いた。このとき用いた管外側の熱抵抗値は、予め実験から求めたものである。
吸着器の性能を表す指標として、省エネ効果を示すCoefficient of Performance(COP)がある。このCOPは、次式により算出される。
COPは、出力としての吸着能力と、それに必要な入熱としての冷熱量によって算出される。同じ吸着能力を発揮するために必要な冷熱量が少ないほど、省エネ効果が高いと言える。
本実施形態は、第1実施形態に対して、熱媒体管21の溝211、212の向きを変更したものである。他の構成については、第1実施形態と同じである。
本開示は上記した実施形態に限定されるものではなく、下記のように、本開示の範囲内において適宜変更が可能である。
Claims (7)
- 内部を熱媒体が流れる熱媒体管(21)と、
前記熱媒体管(21)の外面(21a)に接合され、金属粉が焼結してなる多孔質の焼結体(22)と、
前記焼結体(22)に保持された吸着剤(23)とを備え、
前記熱媒体管(21)は、前記外面(21a)に溝(211、213)が設けられているとともに、内面(21b)に溝(212、214)が設けられている吸着器。 - 前記外面(21a)の前記溝(211、213)と前記内面(21b)の前記溝(212、214)は、前記熱媒体管(21)の軸方向に交差する方向に延びており、
前記外面(21a)の前記溝(211、213)は、前記外面(21a)に設けられた複数の溝(211、213)のうちの1つであり、
前記内面(21b)の前記溝(212、214)は、前記内面(21b)に設けられた複数の溝(212、214)のうちの1つである請求項1に記載の吸着器。 - 前記外面(21a)の前記溝(211)と前記内面(21b)の前記溝(212)は、前記熱媒体管(21)の軸方向に交差する方向に延びるらせん溝である請求項1または2に記載の吸着器。
- 前記内面(21b)の前記溝(212)は、該溝(212)の深さをhiとし、前記熱媒体管(21)の内径をdiとしたとき、hi/di>0.058の関係を満たす請求項3に記載の吸着器。
- 前記内面(21b)の前記溝(212)は、hi/di>0.070の関係を満たす請求項4に記載の吸着器。
- 前記内面(21b)の前記溝(212)は、hi/di≧0.099の関係を満たす請求項5に記載の吸着器。
- 前記内面(21b)の前記溝(212)は、hi/di<0.250の関係を満たす請求項4ないし6のいずれか1つに記載の吸着器。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112014004185.8T DE112014004185T5 (de) | 2013-09-13 | 2014-09-10 | Adsorber |
US15/021,058 US10408509B2 (en) | 2013-09-13 | 2014-09-10 | Adsorber |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013-190643 | 2013-09-13 | ||
JP2013190643A JP6011499B2 (ja) | 2013-09-13 | 2013-09-13 | 吸着器 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015037236A1 true WO2015037236A1 (ja) | 2015-03-19 |
Family
ID=52665367
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/004669 WO2015037236A1 (ja) | 2013-09-13 | 2014-09-10 | 吸着器 |
Country Status (4)
Country | Link |
---|---|
US (1) | US10408509B2 (ja) |
JP (1) | JP6011499B2 (ja) |
DE (1) | DE112014004185T5 (ja) |
WO (1) | WO2015037236A1 (ja) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2017172831A (ja) * | 2016-03-22 | 2017-09-28 | 株式会社デンソー | 吸着器 |
CN111771090A (zh) * | 2018-02-26 | 2020-10-13 | 国立大学法人东海国立大学机构 | 热交换器、制冷机和烧结体 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60200063A (ja) * | 1984-03-23 | 1985-10-09 | 松下冷機株式会社 | 冷房システムの乾燥装置 |
JPH04148194A (ja) * | 1990-10-08 | 1992-05-21 | Daikin Ind Ltd | 吸着剤付き熱交換器 |
JPH0444602B2 (ja) * | 1986-02-24 | 1992-07-22 | Kogyo Gijutsu Incho | |
JPH10185353A (ja) * | 1996-12-25 | 1998-07-14 | Chubu Electric Power Co Inc | 吸着式冷凍装置 |
JP2008107075A (ja) * | 2006-09-29 | 2008-05-08 | Denso Corp | 吸着モジュールおよび吸着モジュールの製造方法 |
WO2013001390A1 (en) * | 2011-06-30 | 2013-01-03 | International Business Machines Corporation | Adsorption heat exchanger devices |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1135535B (de) * | 1958-01-11 | 1962-08-30 | Willi Krebs | Gas- und fluessigkeitsdichter Akkumulator |
JPS5852993A (ja) * | 1981-09-25 | 1983-03-29 | Hitachi Ltd | 多孔質伝熱面 |
DE3735915A1 (de) | 1987-10-23 | 1989-05-03 | Wieland Werke Ag | Waermeaustauscher |
JPH04197441A (ja) * | 1990-11-28 | 1992-07-17 | Osaka Gas Co Ltd | 吸着体 |
JPH09178382A (ja) | 1995-12-25 | 1997-07-11 | Mitsubishi Shindoh Co Ltd | 溝付き伝熱管およびその製造方法 |
JP4088945B2 (ja) * | 1998-07-03 | 2008-05-21 | 株式会社Ihi | 燃料電池用蒸発器 |
CN2556587Y (zh) | 2002-08-08 | 2003-06-18 | 上海电力学院 | 花瓣形螺旋纵槽管 |
US20060175044A1 (en) * | 2005-02-10 | 2006-08-10 | Chin-Wei Lee | Heat dissipating tube sintered with copper powders |
JP2007100673A (ja) * | 2005-10-07 | 2007-04-19 | Hino Motors Ltd | Egrクーラ |
JP4380620B2 (ja) * | 2005-11-01 | 2009-12-09 | 株式会社デンソー | 吸着コア、吸着コアの製造方法および吸着式冷凍機 |
DE102006008786B4 (de) * | 2006-02-24 | 2008-01-17 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | Adsorptions-Wärmepumpe, Adsorptions-Kältemaschine und darin enthaltene Adsorberelemente auf Basis eines offenporigen wärmeleitenden Festkörpers |
JP2009198146A (ja) * | 2008-02-25 | 2009-09-03 | Denso Corp | 吸着モジュールおよび吸着熱交換器 |
TWI381144B (zh) * | 2009-07-31 | 2013-01-01 | 燒結式熱管、其製造方法以及其溝槽導管的製造方法 | |
CN102469744A (zh) * | 2010-11-09 | 2012-05-23 | 富准精密工业(深圳)有限公司 | 平板式热管 |
CN202403597U (zh) | 2012-01-16 | 2012-08-29 | 安吉恒盛热能机械有限公司 | 一种螺旋槽换热管 |
-
2013
- 2013-09-13 JP JP2013190643A patent/JP6011499B2/ja not_active Expired - Fee Related
-
2014
- 2014-09-10 US US15/021,058 patent/US10408509B2/en not_active Expired - Fee Related
- 2014-09-10 WO PCT/JP2014/004669 patent/WO2015037236A1/ja active Application Filing
- 2014-09-10 DE DE112014004185.8T patent/DE112014004185T5/de not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60200063A (ja) * | 1984-03-23 | 1985-10-09 | 松下冷機株式会社 | 冷房システムの乾燥装置 |
JPH0444602B2 (ja) * | 1986-02-24 | 1992-07-22 | Kogyo Gijutsu Incho | |
JPH04148194A (ja) * | 1990-10-08 | 1992-05-21 | Daikin Ind Ltd | 吸着剤付き熱交換器 |
JPH10185353A (ja) * | 1996-12-25 | 1998-07-14 | Chubu Electric Power Co Inc | 吸着式冷凍装置 |
JP2008107075A (ja) * | 2006-09-29 | 2008-05-08 | Denso Corp | 吸着モジュールおよび吸着モジュールの製造方法 |
WO2013001390A1 (en) * | 2011-06-30 | 2013-01-03 | International Business Machines Corporation | Adsorption heat exchanger devices |
Also Published As
Publication number | Publication date |
---|---|
JP6011499B2 (ja) | 2016-10-19 |
JP2015055453A (ja) | 2015-03-23 |
DE112014004185T5 (de) | 2016-06-02 |
US10408509B2 (en) | 2019-09-10 |
US20160223229A1 (en) | 2016-08-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
TWI633266B (zh) | Heat pipe | |
WO2015093051A1 (ja) | 吸着器および吸着式冷凍機 | |
JP6827117B2 (ja) | ヒートパイプ | |
US20100263835A1 (en) | Heat pipe | |
TWI633269B (zh) | Heat pipe | |
US20120227934A1 (en) | Heat pipe having a composite wick structure and method for making the same | |
TW201303250A (zh) | 熱管 | |
JP2020076554A (ja) | ヒートパイプ | |
TW201408978A (zh) | 熱管及其製造方法 | |
JP6429297B1 (ja) | ベイパーチャンバー複合体 | |
WO2015037236A1 (ja) | 吸着器 | |
CN205488104U (zh) | 一种超薄导热元件和一种弯折的超薄导热元件 | |
TWI457528B (zh) | 扁平熱管 | |
TWI438043B (zh) | 熱管的製造方法、以及製造熱管的治具 | |
JP2009115346A (ja) | ヒートパイプ | |
TWI661171B (zh) | Heat pipe | |
CN105992919A (zh) | 吸附芯及其制造方法 | |
JP2021055914A (ja) | ヒートパイプ | |
TWI494531B (zh) | 扁平熱導管及其製造方法 | |
JP6605918B2 (ja) | ヒートパイプ | |
US20120037344A1 (en) | Flat heat pipe having swirl core | |
JP4830799B2 (ja) | 吸着モジュール | |
TWI541486B (zh) | 熱管結構及其製造方法 | |
TW201028635A (en) | Evaporator and loop type heat pipe employing it | |
TWI497026B (zh) | 扁平熱導管及其製造方法 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14844760 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15021058 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120140041858 Country of ref document: DE Ref document number: 112014004185 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 14844760 Country of ref document: EP Kind code of ref document: A1 |