JP2015001334A

JP2015001334A - Air conditioner and operation method thereof

Info

Publication number: JP2015001334A
Application number: JP2013125766A
Authority: JP
Inventors: 岸本　章; Akira Kishimoto; 章岸本; 喜徳久角; Yoshinori Hisakado; 後藤　稔; Minoru Goto; 稔後藤; 司堀; Tsukasa Hori
Original assignee: Osaka Gas Co Ltd; Osaka University NUC
Current assignee: Osaka Gas Co Ltd; University of Osaka NUC
Priority date: 2013-06-14
Filing date: 2013-06-14
Publication date: 2015-01-05
Anticipated expiration: 2033-06-14
Also published as: JP6188438B2

Abstract

【課題】冬季で熱不足が発生する状況であっても、エクセルギー損失の低減を図ることができながら、実用に耐え得る加湿暖房運転を実行する。
【解決手段】ロータ部１０の吸湿部１０ｂを通過した後の空気を、第１加熱器２５を通過した後の熱媒により加熱する第２加熱器２２と、空気をロータ部１０の吸湿部１０ｂと第２加熱器２２と熱交換器２３とに記載順に通過させる第１空調流路Ｒ１と、空気を第１加湿器２４と熱交換器２３と第１加熱器２５とロータ部１０の再生部１０ａとに記載順に通過させる第２空調流路Ｒ２とを備え、第２空調流路Ｒ２を通流した空気を空調用空気ＳＡとして供給すると共に第１空調流路Ｒ１を通流した空気を排気ＶＡとして排出する加湿暖房運転を実行可能に構成されている。
【選択図】図１The present invention performs a humidifying heating operation that can withstand practical use while reducing exergy loss even in a situation where heat shortage occurs in winter.
SOLUTION: A second heater 22 that heats air after passing through a hygroscopic portion 10b of a rotor section 10 by a heat medium after passing through a first heater 25, and air is absorbed by a moisture absorbing section 10b of the rotor section 10. 1st air-conditioning flow path R1 which lets it pass in order of description to the 2nd heater 22 and the heat exchanger 23, the 1st humidifier 24, the heat exchanger 23, the 1st heater 25, and the reproduction | regeneration part of the rotor part 10 10a and a second air conditioning channel R2 that is passed in the order of description, and the air that has passed through the second air conditioning channel R2 is supplied as air conditioning air SA and the air that has passed through the first air conditioning channel R1 is exhausted. It is comprised so that the humidification heating operation discharged | emitted as VA is executable.
[Selection] Figure 1

Description

本発明は、空気が通流する吸湿部と再生部との間で通気性吸湿体からなるデシカントロータを回転駆動させて当該空気の除湿及び加湿を行うロータ部と、前記ロータ部の前記再生部を通過する前の空気を外部から導かれる熱媒により加熱する第１加熱器とを備え、空気を、前記ロータ部の前記吸湿部を通過した後の空気と熱交換させる熱交換器と、前記第１加熱器と、前記ロータ部の前記再生部とに通過させ空調用空気として供給する加湿暖房運転を実行可能な空調装置に関する。 The present invention relates to a rotor unit that rotationally drives a desiccant rotor made of a breathable hygroscopic body between a hygroscopic unit through which air flows and a regenerating unit to dehumidify and humidify the air, and the regenerating unit of the rotor unit A first heater that heats the air before passing through a heat medium guided from the outside, and a heat exchanger that exchanges heat between the air after passing through the moisture absorbing portion of the rotor portion, and The present invention relates to an air conditioner capable of performing a humidifying and heating operation that passes through a first heater and the regeneration unit of the rotor unit and supplies the air as air for air conditioning.

今日、震災以降の慢性的な電力不足から節電技術に対する要望が高まっている。特に、空調装置の消費電力は、夏季及び冬季において電力需要のピークを押し上げる主要因となっているため、その消費電力を低減する技術の開発が強く望まれている。
この現状に対し、住宅建築においては高気密高断熱仕様とすることで、空調負荷低減を図っており、このような住宅は建築基準法により２４時間換気できる仕様が義務付けられている。このような２４時間換気において、空調負荷低減を図る目的で、従来の換気扇に代わり、室外空気と室内空気とを熱交換させる熱交換器を設けると共に、熱交換後の室外空気を空調用空気として室内へ供給する換気空調装置がある。
当該換気空調装置の一例として、図８に示すように、空気が通流する吸湿部１０ｂと再生部１０ａとの間で通気性吸湿体からなるデシカントロータ１１を回転駆動させて当該空気の吸湿及び加湿を行うロータ部１０と、当該ロータ部１０の再生部１０ａを通過する前の空気を外部から導かれる熱媒により加熱する加熱器２５と、空気を加湿する加湿器２４と、室外空気と室内空気とを熱交換させる熱交換器２３と、これらの各空調機器に対する空気の流れを加湿暖房運転時と除湿冷房運転時とで切り換える四方切替弁３１、３２とを備えたものが知られている（特許文献１を参照）。
当該特許文献１に開示の空調装置は、その加熱器２５にガスエンジンや燃料電池等のコジェネレーションシステムの排熱を回収した熱媒が導かれ、当該熱媒と空気との熱交換器により、空気を加熱するように構成され、加熱された空気が、ロータ部１０の再生部１０ａに導かれデシカントロータ１１を再生する。 Today, demand for power-saving technology is increasing due to chronic power shortage after the earthquake. In particular, the power consumption of an air conditioner is a main factor that pushes up the peak of power demand in summer and winter, and therefore development of a technology for reducing the power consumption is strongly desired.
In contrast to this situation, in residential construction, air-conditioning load is reduced by adopting high airtight and high thermal insulation specifications, and such houses are required to be able to ventilate for 24 hours according to the Building Standard Law. In such 24-hour ventilation, for the purpose of reducing the air conditioning load, a heat exchanger for exchanging heat between outdoor air and indoor air is provided instead of the conventional ventilation fan, and the outdoor air after heat exchange is used as air conditioning air There is a ventilation air conditioner that supplies indoors.
As an example of the ventilation air conditioner, as shown in FIG. 8, the desiccant rotor 11 made of a breathable hygroscopic material is driven to rotate between the moisture absorbing portion 10 b through which air flows and the regenerating portion 10 a, The rotor unit 10 that performs humidification, the heater 25 that heats the air before passing through the regeneration unit 10a of the rotor unit 10 with a heat medium guided from the outside, the humidifier 24 that humidifies the air, the outdoor air and the room There is known a heat exchanger 23 that exchanges heat with air, and four-way switching valves 31 and 32 that switch the flow of air to each of these air-conditioning devices between a humidifying heating operation and a dehumidifying and cooling operation. (See Patent Document 1).
In the air conditioner disclosed in Patent Document 1, a heat medium that recovers exhaust heat of a cogeneration system such as a gas engine or a fuel cell is guided to the heater 25, and a heat exchanger between the heat medium and air The air is configured to be heated, and the heated air is guided to the regeneration unit 10 a of the rotor unit 10 to regenerate the desiccant rotor 11.

特開２０１２−１８９３０１号公報JP 2012-189301 A

上記特許文献１に開示の空調装置にあっては、特に、冬季において、コジェネレーションシステムの熱が給湯や床暖房等に利用されることが多くなり、加熱器２３に導かれる熱媒の保有する熱が不足するという課題がある。
尚、加熱器２３で熱不足が生じる他の要因としては、加熱器２３での熱媒と空気との温端温度差に起因するエクセルギーの損失が大きいことが挙げられる。
ここで、エクセルギーとは、ある系から仕事として取り出せるエネルギーのことであり、エクセルギー損失とは、当該仕事を取り出す際に、エントロピーの増大により伝熱や燃焼などの過程において必ず発生する有効仕事に変換できないエネルギーのことをいう。 In the air conditioner disclosed in Patent Document 1, the heat of the cogeneration system is often used for hot water supply, floor heating, etc., particularly in winter, and the heat medium guided to the heater 23 is retained. There is a problem of lack of heat.
In addition, as another factor which heat shortage produces in the heater 23, the loss of exergy resulting from the warm end temperature difference of the heating medium and air in the heater 23 is large.
Here, exergy is energy that can be extracted as work from a certain system, and exergy loss is effective work that is always generated in the process of heat transfer and combustion due to increased entropy when the work is extracted. The energy that cannot be converted into.

本発明は、上述の課題に鑑みてなされたものであり、その目的は、従来にない空調回路構成を採用することにより、特に、冬季で熱不足が発生する状況（冬季に空調に使用できる熱が限定される状況）であっても、エクセルギー損失の低減を図ることができながら、実用に耐え得る加湿暖房運転を実行可能な空調装置を提供する点にある。 The present invention has been made in view of the above-described problems, and its purpose is to employ an unprecedented air conditioning circuit configuration, particularly in a situation where heat shortage occurs in winter (heat that can be used for air conditioning in winter). However, the present invention is to provide an air conditioner capable of performing a humidifying and heating operation that can withstand practical use while reducing the exergy loss.

上記目的を達成するための空調装置は、
空気が通流する吸湿部と再生部との間で通気性吸湿体からなるデシカントロータを回転駆動させて当該空気の除湿及び加湿を行うロータ部と、
前記ロータ部の前記再生部を通過する前の空気を外部から導かれる熱媒により加熱する第１加熱器とを備え、
空気を、前記ロータ部の前記吸湿部を通過した後の空気と熱交換させる熱交換器と、前記第１加熱器と、前記ロータ部の前記再生部とに通過させ空調用空気として供給する加湿暖房運転を実行可能な空調装置であって、その特徴構成は、
空気を加湿する第１加湿器と、
前記ロータ部の前記吸湿部を通過した後の空気を、前記第１加熱器を通過した後の熱媒により加熱する第２加熱器と、
空気を前記ロータ部の前記吸湿部と前記第２加熱器と前記熱交換器とに記載順に通過させる第１空調流路と、空気を前記第１加湿器と前記熱交換器と前記第１加熱器と前記ロータ部の前記再生部とに記載順に通過させる第２空調流路とを備え、
前記第２空調流路を通流した空気を空調用空気として供給すると共に前記第１空調流路を通流した空気を排気として排出する加湿暖房運転を実行可能に構成されている点にある。 The air conditioner for achieving the above object is
A rotor unit for dehumidifying and humidifying the air by rotating and driving a desiccant rotor made of a breathable hygroscopic material between a hygroscopic unit through which air flows and a regeneration unit;
A first heater that heats the air before passing through the regeneration portion of the rotor portion with a heat medium guided from the outside;
Humidification supplied to the heat exchanger for exchanging heat with the air after passing through the moisture absorption part of the rotor part, the first heater, and the regeneration part of the rotor part and supplied as air for air conditioning An air conditioner that can perform heating operation, and its characteristic configuration is:
A first humidifier for humidifying the air;
A second heater that heats the air after passing through the hygroscopic part of the rotor part with a heat medium after passing through the first heater;
A first air-conditioning flow path for allowing air to pass through the hygroscopic portion of the rotor portion, the second heater, and the heat exchanger in the order described; and air for the first humidifier, the heat exchanger, and the first heating. And a second air-conditioning channel that passes through the regenerator and the regenerating unit of the rotor unit in the order described,
The humidification heating operation which supplies the air which flowed through the 2nd air-conditioning channel as air-conditioning air, and exhausts the air which flowed through the 1st air-conditioning channel as exhaust air is executable.

上記特徴構成によれば、第１加熱器に加えて、第１空調流路を通流する空気を、第１加熱器を通過した後の熱媒により加熱する第２加熱器を備えているから、第２加熱器では、第１空調流路を通流する空気が熱媒の保有する熱を回収することにより、当該熱は、その下流側の熱交換器にて第２空調流路を通流する空気に伝熱される。そして、このように加熱された当該第２空調流路を通流する空気が、さらに第１加熱器にてさらに加熱されて、当該第２空調流路を流れる空気が保有する熱が、ロータ部の再生部の再生の用に供されることとなる。つまり、熱媒（外部から空調装置内に導入され、系外から熱を供給する熱媒）の側からみると、その保有する熱が、第１加熱器に加えて、第２加熱器でも回収（利用）されることとなり、当該回収（利用）された熱が、第２空調流路を通流する空気に伝達され、デシカントロータの再生の用に供される。結果、熱媒が系外に捨てる熱、即ち、利用されることなく系の外部へ放熱される熱の量を低減でき、エクセルギー損失の低減を図ることができる。
一方、第１加熱器での空気と熱媒との熱交換に着目すると、第１加熱器における熱媒と空調用空気との温端温度差を低減して、エクセルギー損失を低減することができる。結果、冬季で熱媒の保有する熱が不足する場合であっても、適切に加湿暖房運転を実行することができる。
尚、熱媒の保有する熱不足が生じていない状況にあっては、熱媒の流量を低減することができ、この場合でも、エクセルギー損失の低減を図ることができる。
以上より、デシカントロータを用いた空調装置において、新たな回路構成を採用することにより、エクセルギー損失を低減できると共に、特に、冬季で熱不足が発生する状況であっても、実用に耐える加熱暖房運転を実行可能な空調装置を実現できる。 According to the above characteristic configuration, in addition to the first heater, the second heater for heating the air flowing through the first air-conditioning flow path with the heat medium after passing through the first heater is provided. In the second heater, the air flowing through the first air conditioning channel recovers the heat held by the heat medium, so that the heat passes through the second air conditioning channel in the heat exchanger on the downstream side. Heat is transferred to the flowing air. And the air which flows through the said 2nd air conditioning flow path heated in this way is further heated by the 1st heater, and the heat which the air which flows through the said 2nd air conditioning flow path holds is a rotor part. It will be used for the reproduction of the reproduction unit. In other words, when viewed from the side of the heat medium (a heat medium that is introduced from the outside into the air conditioner and supplies heat from outside the system), the heat held by the heat medium is also recovered by the second heater in addition to the first heater. The recovered (utilized) heat is transmitted to the air flowing through the second air conditioning channel, and is used for regeneration of the desiccant rotor. As a result, the amount of heat that the heat medium throws out of the system, that is, the amount of heat radiated to the outside of the system without being used, can be reduced, and the exergy loss can be reduced.
On the other hand, paying attention to the heat exchange between the air and the heat medium in the first heater, the exothermic loss can be reduced by reducing the temperature difference between the heat medium and the air-conditioning air in the first heater. it can. As a result, even when the heat held by the heat medium is insufficient in winter, the humidifying and heating operation can be appropriately executed.
In addition, in the situation where the heat shortage possessed by the heat medium does not occur, the flow rate of the heat medium can be reduced, and even in this case, the exergy loss can be reduced.
As described above, in the air conditioner using a desiccant rotor, by adopting a new circuit configuration, exergy loss can be reduced, and heating and heating that can withstand practical use even in situations where heat shortage occurs in winter. An air conditioner that can be operated can be realized.

本発明の空調装置の更なる特徴構成は、
前記第１空調流路を通過した空気を空調用空気として供給すると共に前記第２空調流路を通過した空気を排気として排出する除湿冷房運転と、前記加湿暖房運転とを択一的に切り換える運転切替手段を備える点にある。 A further characteristic configuration of the air conditioner of the present invention is as follows:
An operation for selectively switching between the dehumidifying and cooling operation for supplying the air that has passed through the first air-conditioning channel as air-conditioning air and exhausting the air that has passed through the second air-conditioning channel as an exhaust, and the humidifying and heating operation. It is in the point provided with the switching means.

上記特徴構成によれば、除湿冷房運転をも実行することができ、運転切替手段により、除湿冷房運転と加湿暖房運転とを択一的に切り換えて、年間を通じて適切な空調を実行可能な空調装置を実現できる。 According to the above-described characteristic configuration, the dehumidifying and cooling operation can also be executed, and the operation switching unit can selectively switch between the dehumidifying and cooling operation and the humidifying and heating operation, and can perform appropriate air conditioning throughout the year. Can be realized.

本発明の空調装置の更なる特徴構成は、
前記第１空調流路は、前記第２加熱器をバイパスするバイパス路を備え、
前記第２加熱器をバイパスするバイパス路に空気を通流させるバイパス状態と、前記第２加熱器を通過する非バイパス状態とを択一的に切り換える通流状態切替手段を備え、
前記通流状態切替手段は、前記除湿冷房運転時に前記バイパス状態に切り換え、前記加湿暖房運転時に前記非バイパス状態に切り換える点にある。 A further characteristic configuration of the air conditioner of the present invention is as follows:
The first air conditioning flow path includes a bypass path that bypasses the second heater,
A flow state switching means that selectively switches between a bypass state in which air is passed through a bypass passage that bypasses the second heater and a non-bypass state that passes through the second heater;
The flow state switching means switches to the bypass state during the dehumidifying and cooling operation and switches to the non-bypass state during the humidifying and heating operation.

上述した空調装置にあっては、除湿冷房運転時において、第１空調流路を通流する空気（空調用空気として供給される空気）が、ロータ部の除湿部を通過して除湿され、第２加熱器にて加熱され、熱交換器における熱交換により降温した後、空調対象空間に供給される。
即ち、除湿冷房運転で、第１空調流路を通流する空気（空調用空気として供給される空気）の除湿よりも降温を優先させる場合には、第２加熱器での加熱を行わないことが好ましい。
上記特徴構成によれば、通流状態切替手段により、除湿冷房運転時には、第１空調流路を通流する空気（空調用空気として供給される空気）を、第２加熱器をバイパスするバイパス状態にできるから、空調用空気としての空気の温度を、不要に昇温させることなく低温の状態を保った状態で、空調対象空間へ供給できる。
尚、除湿冷房運転時であっても、降温よりも除湿を優先させる場合には、ロータ部の再生部へなるべく高温の空気を通過させることが好ましいため、第１空調流路を通流する空気（空調用空気として供給される空気）が第２加熱器を通過させる非バイパス状態として、当該第２加熱器にて第１空調流路を通流する空気が回収した熱を、熱交換器にて、ロータ部の再生部へ導かれる第２空調流路を通流する空気に伝熱させる構成を採用することもできる。 In the air conditioner described above, during the dehumidifying and cooling operation, the air flowing through the first air conditioning channel (air supplied as air for air conditioning) passes through the dehumidifying portion of the rotor portion and is dehumidified. After being heated by the two heaters and cooled by heat exchange in the heat exchanger, it is supplied to the air-conditioning target space.
That is, in the dehumidifying and cooling operation, when priority is given to temperature reduction over dehumidification of air flowing through the first air conditioning channel (air supplied as air conditioning air), heating with the second heater is not performed. Is preferred.
According to the above characteristic configuration, in the dehumidifying and cooling operation, the flow state switching means bypasses the air flowing through the first air conditioning channel (air supplied as air conditioning air) to the second heater. Therefore, the temperature of the air as the air for air conditioning can be supplied to the air conditioning target space in a state where the temperature is kept low without being unnecessarily increased.
Even in the dehumidifying and cooling operation, when priority is given to dehumidifying over lowering the temperature, it is preferable to pass hot air as much as possible to the regenerating part of the rotor part, so the air flowing through the first air conditioning channel As a non-bypass state in which (air supplied as air-conditioning air) passes through the second heater, the heat recovered by the air flowing through the first air-conditioning channel in the second heater is transferred to the heat exchanger. Thus, it is also possible to adopt a configuration in which heat is transferred to the air flowing through the second air conditioning channel guided to the regeneration unit of the rotor unit.

本発明の空調装置の更なる特徴構成は、
前記第１加湿器とは別に空気を加湿する第２加湿器を備え、
前記除湿冷房運転時に、前記第１空調流路を通過した後の空気を前記第２加湿器にて加湿冷却する点にある。 A further characteristic configuration of the air conditioner of the present invention is as follows:
A second humidifier that humidifies air separately from the first humidifier;
In the dehumidifying and cooling operation, the air after passing through the first air conditioning channel is humidified and cooled by the second humidifier.

上記特徴構成によれば、除湿冷房運転時に、除湿よりも降温を優先させる場合には、第１空調流路を通過した後の空気（空調用空気としての空気）を、第２加湿器にて加湿冷却することができ、十分に降温された空気を、空調用空気として空調対象空間へ供給することができる。 According to the above characteristic configuration, in the dehumidifying and cooling operation, when priority is given to lowering the temperature over dehumidifying, the air after passing through the first air conditioning channel (air as air for air conditioning) is sent by the second humidifier. Humidification and cooling can be performed, and sufficiently cooled air can be supplied to the air-conditioning target space as air-conditioning air.

本発明の空調装置の更なる特徴構成は、
前記熱交換器が、前記第１空調流路を通流する空気と前記第２空調流路を通流する空気とを対向流で熱交換させる対向流型熱交換器である点にある。 A further characteristic configuration of the air conditioner of the present invention is as follows:
The heat exchanger is a counterflow type heat exchanger that exchanges heat between the air flowing through the first air-conditioning channel and the air flowing through the second air-conditioning channel in a counterflow.

通常、ロータ部を備える空調装置にあっては、設置スペースの制約等の関係で、第１空調流路を通過する空気と第２空調流路を通過する空気との熱交換器に、クロスフィン型の熱交換器が採用される。しかしながら、当該クロスフィン型の熱交換器では、温端温度差が大きくなるため、エクセルギー損失が大きくなるという問題があった。
上記特徴構成によれば、熱交換器として比較的大きい伝熱係数を有する対向流型熱交換器を採用することで、温端温度差を減少させ、エクセルギー損失を低減することができる。尚、ここで、対向流型熱交換器とは、例えば、二重管式熱交換器で内管の内部と内管と外管との間とに対向流で空気を通流させ熱交換する熱交換器を意味することとする。 In general, in an air conditioner including a rotor unit, a cross fin is used in a heat exchanger between air passing through the first air conditioning channel and air passing through the second air conditioning channel due to restrictions on installation space. A mold heat exchanger is adopted. However, the cross-fin type heat exchanger has a problem that exergy loss increases because the temperature difference at the warm end becomes large.
According to the above characteristic configuration, by adopting a counter flow heat exchanger having a relatively large heat transfer coefficient as a heat exchanger, it is possible to reduce the hot end temperature difference and reduce exergy loss. Here, the counter flow type heat exchanger is, for example, a double pipe heat exchanger that exchanges heat by passing air in the counter flow between the inside of the inner tube and between the inner tube and the outer tube. It shall mean a heat exchanger.

本発明の空調装置の運転方法は、
前記第１加熱器に導かれる熱媒の温度を、前記第２空調流路で前記第１加熱器を通過する空気の温度よりも高く設定すると共に、前記第２加熱器に導かれる熱媒の温度を、前記第１空調流路で前記第２加熱器を通過する空気の温度よりも高く設定する点を特徴とする。 The operation method of the air conditioner of the present invention is as follows:
The temperature of the heat medium guided to the first heater is set higher than the temperature of the air passing through the first heater in the second air conditioning channel, and the heat medium guided to the second heater is The temperature is set higher than the temperature of the air passing through the second heater in the first air conditioning channel.

上記特徴構成の如く、熱媒の温度を設定することにより、第１加熱器において熱媒の保有する熱を第２空調流路を通流する空気へ適切に伝熱させることができると共に、第２加熱器において熱媒の保有する熱を第１空調流路を通流する空気へ適切に伝熱させることができ、空調装置を適切に働かせることができる。
尚、上記温度設定に係る制御に関しては、実体上は、第１加熱器及び第２加熱器を通過する熱媒の流量を調整することとなる。 As in the above characteristic configuration, by setting the temperature of the heat medium, the heat held by the heat medium in the first heater can be appropriately transferred to the air flowing through the second air conditioning channel, In the two heaters, the heat held by the heat medium can be appropriately transferred to the air flowing through the first air conditioning flow path, and the air conditioning apparatus can be operated appropriately.
Note that, regarding the control related to the temperature setting, the flow rate of the heat medium passing through the first heater and the second heater is actually adjusted.

第１実施形態での除湿冷房運転における回路状態を示す図The figure which shows the circuit state in the dehumidification air_conditionaing | cooling operation in 1st Embodiment. 図１に示す回路の各部位での空気の状態を示す空気線図Air line diagram showing the state of air in each part of the circuit shown in FIG. 第１実施形態での加湿暖房運転における回路状態を示す図The figure which shows the circuit state in the humidification heating operation in 1st Embodiment. 図３に示す回路の各部位での空気の状態を示す空気線図Air line diagram showing the state of air in each part of the circuit shown in FIG. 本発明と図８に示す従来技術とでの加湿暖房運転時におけるエクセルギーサンキーダイアグラムを示す図The figure which shows the exergy Sankey diagram at the time of humidification heating operation by this invention and the prior art shown in FIG. 第２加熱器をバイパスするバイパス路を備えた第２実施形態を示す回路図The circuit diagram which shows 2nd Embodiment provided with the bypass path which bypasses a 2nd heater. 本発明に係る加湿暖房運転を専用で実施する別実施形態を示す図The figure which shows another embodiment which implements humidification heating operation concerning this invention exclusively. 加湿暖房運転における回路状態を示す従来技術の図Prior art diagram showing circuit state in humidification heating operation

本発明の空調装置１００は、従来にない回路構成を採用することにより、特に、冬季で熱不足が発生する状況でも、エクセルギー損失を低減して、実用に耐え得る加熱暖房運転を実行可能なものであり、以下その実施形態を図面に基づいて説明する。
〔第１実施形態〕
本発明の空調装置１００は、空気の通流状態を切り換え可能な第１四方切替弁３１及び第２四方切替弁３２を備えており、当該第１四方切替弁３１と第２四方切替弁３２とを対応して切り換えることにより、図１に示す除湿冷房運転時の回路状態と、図３に示す加湿暖房運転時の回路状態とを切り換え可能に構成されている。当該第１四方切替弁３１及び第２四方切替弁３２が、運転切替手段として働く。
以下、本発明の空調装置１００の基本的な構成、第１空調流路Ｒ１、第２空調流路Ｒ２の構成及び働きについて順に説明し、その後、除湿冷房運転及び加湿暖房運転について説明する。
本発明の空調装置１００は、基本的な構成として、空気に直接水を噴霧して加湿可能な第１加湿器２４、第２加湿器４１、空気が通流する吸湿部１０ｂと再生部１０ａとの間で通気性吸湿体からなるデシカントロータ１１を回転駆動させて当該空気の除湿及び加湿を行うロータ部１０と、熱媒の熱により空気を加熱する第１加熱器２５及び第２加熱器２２と、室外空気ＯＡ又は室内空気ＲＡを吸入すると共に空調用空気ＳＡ又は排気ＶＡとして吹出する第１ファン２１及び第２ファン２６と、室外空気ＯＡと室内空気ＲＡとを熱交換させる対向流型熱交換器２３とを備えて構成されている。 The air conditioner 100 of the present invention employs an unprecedented circuit configuration, and can perform a heating and heating operation that can withstand practical use by reducing exergy loss even in a situation where heat shortage occurs particularly in winter. The embodiment will be described below with reference to the drawings.
[First Embodiment]
The air conditioner 100 of the present invention includes a first four-way switching valve 31 and a second four-way switching valve 32 that are capable of switching the air flow state, and the first four-way switching valve 31 and the second four-way switching valve 32 are provided. By switching correspondingly, the circuit state during the dehumidifying and cooling operation shown in FIG. 1 and the circuit state during the humidifying and heating operation shown in FIG. 3 can be switched. The first four-way switching valve 31 and the second four-way switching valve 32 serve as operation switching means.
Hereinafter, the basic configuration of the air conditioner 100 of the present invention, the configurations and functions of the first air conditioning channel R1 and the second air conditioning channel R2 will be described in order, and then the dehumidifying and cooling operation and the humidifying and heating operation will be described.
The air conditioner 100 according to the present invention includes, as a basic configuration, a first humidifier 24 and a second humidifier 41 that can be humidified by directly spraying water on the air, a moisture absorption unit 10b through which air flows, and a regeneration unit 10a. A rotor 10 that dehumidifies and humidifies the air by rotating a desiccant rotor 11 made of a breathable hygroscopic material, and a first heater 25 and a second heater 22 that heat the air by the heat of the heat medium. And the first fan 21 and the second fan 26 that suck in the outdoor air OA or the indoor air RA and blow out as the air-conditioning air SA or the exhaust VA, and the counter flow heat that exchanges heat between the outdoor air OA and the indoor air RA. And an exchanger 23.

尚、第１加熱器２５及び第２加熱器２２には、エンジンや燃料電池等のコージェネレーションシステム（図示せず）の排熱を回収した熱媒を通流する熱媒流路Ｒ３が、記載の順に熱媒を循環させるように配設されている。 The first heater 25 and the second heater 22 have a heat medium flow path R3 through which a heat medium that recovers exhaust heat from a cogeneration system (not shown) such as an engine or a fuel cell is passed. It arrange | positions so that a heat medium may be circulated in order.

ロータ部１０に設けられるデシカントロータ１１は、モータ等の回転駆動部１２により、回転される回転駆動軸に中心部が固定されて比較的ゆっくりした所定の回転速度で回転駆動し、後述する第１空調流路Ｒ１及び第２空調流路Ｒ２に配設される吸湿部１０ｂ及び再生部１０ａを横断する姿勢で配設された円盤状又は円柱状の部材として構成されている。当該デシカントロータ１１は、回転駆動軸に沿う方向に貫通する多数の通路が形成されたハニカム状に形成されており、吸湿部１０ｂ及び再生部１０ａにおいて、空気がデシカントロータ１１を貫通して通過する。当該デシカントロータ１１は、ゼオライト、シリカゲル、及び活性炭等の公知の吸着材を担持して、通気性吸着体とされている。
このようなデシカントロータ１１を備えたロータ部１０は、吸湿部１０ｂに、比較的低温の空気が通過することにより、当該空気がデシカントロータ１１の吸湿時の放熱作用による温度上昇を伴って除湿され、それによりデシカントロータ１１は空気の水分を吸着した状態（吸湿状態）となる。その水分を吸着したデシカントロータ１１の部分が、上記回転駆動により再生部１０ａに移動することになる。
一方、当該再生部１０ａに比較的高温の空気が通過することで、その空気はデシカントロータ１１の放湿時の吸湿作用による温度低下を伴って加湿され、それによりデシカントロータ１１は、上記吸着した水分を脱着させた状態（乾燥状態）となり、再生されることとなる。当該再生されたデシカントロータ１１の部分が、上記回転駆動により吸湿部１０ｂに移動することになる。
このようにして、ロータ部１０は、吸湿部１０ｂ及び再生部１０ａを通過する夫々の空気の除湿と加湿とを行うことができるように構成されている。 A desiccant rotor 11 provided in the rotor unit 10 is rotationally driven at a relatively slow predetermined rotational speed with a central part fixed to a rotating rotational drive shaft by a rotational drive unit 12 such as a motor. It is configured as a disk-shaped or columnar member disposed in a posture that traverses the hygroscopic portion 10b and the regenerating portion 10a disposed in the air conditioning channel R1 and the second air conditioning channel R2. The desiccant rotor 11 is formed in a honeycomb shape having a large number of passages penetrating in the direction along the rotation drive shaft, and air passes through the desiccant rotor 11 in the moisture absorption part 10b and the regeneration part 10a. . The desiccant rotor 11 carries a known adsorbent such as zeolite, silica gel, and activated carbon, and is a breathable adsorbent.
The rotor portion 10 having such a desiccant rotor 11 is dehumidified with an increase in temperature due to a heat dissipation action when the desiccant rotor 11 absorbs moisture when relatively low-temperature air passes through the moisture absorption portion 10b. As a result, the desiccant rotor 11 is in a state where moisture in the air is absorbed (moisture absorption state). The portion of the desiccant rotor 11 that has adsorbed the moisture moves to the reproducing unit 10a by the rotational drive.
On the other hand, the relatively high-temperature air passes through the regeneration unit 10a, so that the air is humidified with a decrease in temperature due to moisture absorption when the desiccant rotor 11 is dehumidified, whereby the desiccant rotor 11 is adsorbed. The moisture is desorbed (dried state) and regenerated. The regenerated portion of the desiccant rotor 11 is moved to the moisture absorbing portion 10b by the rotational drive.
In this way, the rotor unit 10 is configured to be able to dehumidify and humidify each of the air passing through the moisture absorption unit 10b and the regeneration unit 10a.

第１空調流路Ｒ１は、第１ファン２１から送り出された空気を、ロータ部１０の吸湿部１０ｂ、第２加熱器２２及び対向流型熱交換器２３に通過させる状態で構成されている。そして、この第１空調流路Ｒ１を通過した後に、第２加湿器４１を通過する。ここで、第１空調流路Ｒ１は、図１、３に示される回路図において、第１四方切替弁３１と第２四方切替弁３２との間に設けられる。
一方、第２空調流路Ｒ２は、第２ファン２６にて吸入される空気を、第１加湿器２４、対向流型熱交換器２３、第１加熱器２５、及びロータ部１０の再生部１０ａに順に通過させる状態で設けられる。ここで、第２空調流路Ｒ２は、図１、３に示される回路図において、第１四方切替弁３１と第２四方切替弁３２との間に設けられる。 The first air conditioning channel R <b> 1 is configured in a state in which the air sent from the first fan 21 is allowed to pass through the moisture absorption unit 10 b, the second heater 22, and the counterflow type heat exchanger 23 of the rotor unit 10. Then, after passing through the first air conditioning channel R1, the second humidifier 41 is passed. Here, the first air conditioning flow path R1 is provided between the first four-way switching valve 31 and the second four-way switching valve 32 in the circuit diagrams shown in FIGS.
On the other hand, the second air conditioning channel R2 converts the air sucked by the second fan 26 into the first humidifier 24, the counterflow heat exchanger 23, the first heater 25, and the regeneration unit 10a of the rotor unit 10. Are provided in such a state that they are sequentially passed through. Here, the second air conditioning channel R2 is provided between the first four-way switching valve 31 and the second four-way switching valve 32 in the circuit diagrams shown in FIGS.

熱媒流路Ｒ３では、第１加熱器２５に導かれる熱媒の温度が、第２空調流路Ｒ２で第１加熱器２５に導かれる空気の温度よりも高く、第２加熱器２２に導かれる熱媒の温度が、第１空調流路Ｒ１で第２加熱器２２に導かれる空気の温度よりも高くなるように、図示しない制御装置により制御されている。
説明を追加すると、制御装置は、実質的には、熱媒流路Ｒ３を通流する熱媒の流量を制御することで、第１加熱器２５、及び第２加熱器２２での熱媒の温度を上述の温度に設定する。
これにより、第２加熱器２２では、第１空調流路Ｒ１を通流する空気が常に熱媒の保有する熱を回収する（加熱される）ことにより、当該熱は、対向流型熱交換器２３にて第２空調流路Ｒ２を通流する空気に伝熱され、当該第２空調流路Ｒ２を通流する空気が、さらに第１加熱器２５にて加熱されて、当該第２空調流路Ｒ２の保有する熱が、ロータ部１０の再生部１０ａでのデシカントロータ１１の再生の用に供されることとなる。つまり、熱媒の側からみると、その保有する熱が、空調装置１００の第１加熱器２５に加えて、第２加熱器２２でも回収されることとなり、当該回収された熱が、第２空調流路Ｒ２を通流する空気に伝達され、デシカントロータ１１の再生の用に供されるから、利用されることなく系の外部へ排熱される熱の量を低減でき、エクセルギー損失の低減を図ることが可能な構成となっている。 In the heat medium flow path R3, the temperature of the heat medium guided to the first heater 25 is higher than the temperature of the air guided to the first heater 25 in the second air conditioning flow path R2, and is guided to the second heater 22. The temperature of the heating medium to be applied is controlled by a control device (not shown) so as to be higher than the temperature of the air guided to the second heater 22 in the first air conditioning channel R1.
When the description is added, the control device substantially controls the flow rate of the heat medium that flows through the heat medium flow path R3, so that the heat medium in the first heater 25 and the second heater 22 is controlled. Set the temperature to the above-mentioned temperature.
Thereby, in the 2nd heater 22, when the air which flows through 1st air-conditioning flow path R1 always collect | recovers the heat which a heat carrier holds (it heats), the said heat is counterflow type heat exchanger 23, heat is transferred to the air flowing through the second air conditioning channel R2, and the air flowing through the second air conditioning channel R2 is further heated by the first heater 25, so that the second air conditioning channel The heat possessed by the path R <b> 2 is used for the regeneration of the desiccant rotor 11 in the regeneration unit 10 a of the rotor unit 10. That is, when viewed from the side of the heat medium, the retained heat is also recovered by the second heater 22 in addition to the first heater 25 of the air conditioner 100, and the recovered heat is the second heat. Since it is transmitted to the air flowing through the air conditioning channel R2 and used for regeneration of the desiccant rotor 11, the amount of heat exhausted to the outside of the system without being used can be reduced, and the exergy loss can be reduced. It is the structure which can aim at.

〔除湿冷房運転〕
除湿冷房運転では、図示しない制御装置による制御により、第１四方切替弁３１と第２四方切替弁３２とを、図１に示す回路状態へと切り替えられる。これにより、室外空気ＯＡは、第１空調流路Ｒ１を通流して空調され、第２加湿器４１にて加湿冷却された後に空調用空気ＳＡとして空調対象空間（図示せず）へ導かれる。一方、室内空気ＲＡは、第２空調流路Ｒ２を通流した後に排気として空調対象空間の外部へ導かれる。
説明を追加すると、室外空気ＯＡは、第１四方切替弁３１を通過した後に、第１ファン２１で圧送され、ロータ部１０の吸湿部１０ｂにて吸湿時の放熱作用による温度上昇を伴って除湿され、第２加熱器２２にて熱媒との熱交換により加熱され、対向流型熱交換器２３にて室内空気ＲＡと熱交換して降温し、第２四方切替弁３２を通過し、第２加湿器４１にて加湿冷却された後に、低湿・低温の空調用空気ＳＡとして空調対象空間へ導かれる。
一方、室内空気ＲＡは、第１四方切替弁３１を通過した後に、第１加湿器２４にて加湿冷却され、対向流型熱交換器２３にて室外空気ＯＡと熱交換して昇温し、第１加熱器２５にて熱媒との熱交換により加熱されて十分に昇温された状態で、ロータ部１０の再生部１０ａを通過することで、当該再生部１０ａに位置するデシカントロータ１１の部位を再生した後、第２ファン２６にて圧送されて排気ＶＡとして空調対象空間の外部へ排出される。 [Dehumidifying and cooling operation]
In the dehumidifying and cooling operation, the first four-way switching valve 31 and the second four-way switching valve 32 are switched to the circuit state shown in FIG. Thereby, the outdoor air OA is air-conditioned by flowing through the first air conditioning channel R1, and after being humidified and cooled by the second humidifier 41, is led to the air conditioning target space (not shown) as the air conditioning air SA. On the other hand, the indoor air RA is led to the outside of the air-conditioning target space as exhaust after flowing through the second air-conditioning channel R2.
When the explanation is added, the outdoor air OA passes through the first four-way switching valve 31, and is then pumped by the first fan 21. The dehumidification is accompanied by a temperature increase due to the heat dissipation action at the time of moisture absorption by the moisture absorbing part 10b of the rotor part 10. The second heater 22 is heated by heat exchange with the heat medium, the counter air flow heat exchanger 23 exchanges heat with the indoor air RA, cools the temperature, passes through the second four-way switching valve 32, After being humidified and cooled by the 2 humidifier 41, the air is guided to the air-conditioning target space as low-humidity / low-temperature air-conditioning air SA.
On the other hand, the indoor air RA is humidified and cooled by the first humidifier 24 after passing through the first four-way switching valve 31, and is heated by exchanging heat with the outdoor air OA in the counterflow heat exchanger 23. By passing through the regeneration unit 10a of the rotor unit 10 while being heated sufficiently by heat exchange with the heat medium in the first heater 25, the desiccant rotor 11 located in the regeneration unit 10a After the part is regenerated, it is pumped by the second fan 26 and discharged to the outside of the air conditioning target space as exhaust VA.

〔除湿冷房運転における空調性能〕
当該除湿冷房運転の除湿冷房性能を、シミュレーションにより評価する。空調する空間は、床面積が１０７ｍ²、天井高さ４．２ｍの空間とした。図２に示されるＰ１〜Ｐ１０は、図１における回路上のＰ１〜Ｐ１０に対応しており、図２の空気線図では、各Ｐ１〜Ｐ１０における気体の状態（温度、絶対湿度、相対湿度）を示している。
シミュレーションを行う条件としては、室内空気ＲＡが、温度２７℃、絶対湿度１０．３ｇ／ｋｇＤＡ、相対湿度４７％とし、室外空気ＯＡが、温度３５℃、絶対湿度１３．９ｇ／ｋｇＤＡ、相対湿度４０％とし、室内空気ＲＡ及び室外空気ＯＡの流量（換気流量）が、３４７ｍ³／ｈとする。
空調装置１００を構成する各機器の条件としては、第１ファン２１及び第２ファン２６の消費電力を夫々１５０Ｗとし、その断熱効率をモータ効率を含め５０％とし、ロータ部１０のデシカントロータ１１の除湿効率を７５％とし、対向流型熱交換器２３の伝熱係数を７００Ｗ／Ｋとし、第１加熱器２５及び第２加熱器２２の伝熱係数を１２５Ｗ／Ｋとし、第１ファン２１の揚程を７８０Ｐａとし、第２ファン２６の揚程を７２０Ｐａとし、第１加湿器２４の水噴霧量を０．１０ｋｇ／ｈとし、第２加湿器４１の水噴霧量を０．５７ｋｇ／ｈとし、熱媒の導入温度を７０℃、循環流量を３．４Ｌ／ｍｉｎとする。 [Air conditioning performance in dehumidifying and cooling operation]
The dehumidifying and cooling performance of the dehumidifying and cooling operation is evaluated by simulation. The air-conditioned space has a floor area of 107 m ² and a ceiling height of 4.2 m. P1 to P10 shown in FIG. 2 correspond to P1 to P10 on the circuit in FIG. 1, and in the air diagram of FIG. 2, the gas states (temperature, absolute humidity, relative humidity) in each P1 to P10 are shown. Is shown.
As conditions for the simulation, the room air RA is 27 ° C., the absolute humidity is 10.3 g / kgDA, and the relative humidity is 47%, and the outdoor air OA is 35 ° C., the absolute humidity is 13.9 g / kgDA, and the relative humidity is 40%. %, And the flow rate (ventilation flow rate) of the indoor air RA and the outdoor air OA is 347 m ³ / h.
The condition of each device constituting the air conditioner 100 is that the power consumption of the first fan 21 and the second fan 26 is 150 W, the heat insulation efficiency is 50% including the motor efficiency, and the desiccant rotor 11 of the rotor unit 10 is The dehumidification efficiency is 75%, the heat transfer coefficient of the counterflow heat exchanger 23 is 700 W / K, the heat transfer coefficients of the first heater 25 and the second heater 22 are 125 W / K, The lift is 780 Pa, the lift of the second fan 26 is 720 Pa, the water spray amount of the first humidifier 24 is 0.10 kg / h, the water spray amount of the second humidifier 41 is 0.57 kg / h, The introduction temperature of the medium is 70 ° C., and the circulation flow rate is 3.4 L / min.

上記条件でシミュレーションを行った結果、図２の空気線図に示すように、室内空気ＲＡが加湿・昇温されて排気ＶＡとして排出されるのに伴って、室外空気ＯＡが、除湿・冷却され、温度２６．９℃、絶対湿度９．８ｇ／ｋｇＤＡ、相対湿度４５％、風量３３６ｍ³／ｈの空調用空気ＳＡ（図２でＰ５における空気）として空調対象空間（図示せず）に導かれることとなった。尚、当該シミュレーションにおいて、ロータ部１０の吸湿部１０ｂにおける除湿量（図２でＰ１―Ｐ２での除湿量）は、２．１６ｋｇ／ｈ（正味除湿量は１．５９ｋｇ／ｈ）となり、熱媒の戻り温度は、６１．８℃となり、熱媒熱負荷は２１３５Ｗとなった。 As a result of the simulation under the above conditions, as shown in the air diagram of FIG. 2, the outdoor air OA is dehumidified and cooled as the indoor air RA is humidified and heated and discharged as exhaust VA. , 26.9 ° C., absolute humidity 9.8 g / kgDA, relative humidity 45%, air volume 336 m ³ / h air conditioning air SA (air in P5 in FIG. 2) is led to the air conditioning target space (not shown) It became a thing. In this simulation, the dehumidification amount (the dehumidification amount at P1-P2 in FIG. 2) in the moisture absorption unit 10b of the rotor unit 10 is 2.16 kg / h (the net dehumidification amount is 1.59 kg / h). The return temperature was 61.8 ° C., and the heat transfer heat load was 2135 W.

一方、図８に示す従来技術においても同様のシミュレーションを行った。尚、図８は加湿暖房運転時の回路状態を示すものであるが、第１四方切替弁３１、第２四方切替弁３２を回転させて除湿冷房運転時の回路状態としたものを前提として、当該シミュレーションを行った。シミュレーションの条件は、熱交換器２３の伝熱係数が１９０Ｗ／Ｋとする点、及び第２加熱器２２を設けない点以外は、上述の条件と同様である。
当該シミュレーションの結果、図８に示す従来技術では、空気線図には示さないが、室外空気ＯＡが、除湿・冷却され、温度３１．４℃、絶対湿度１０．１ｇ／ｋｇＤＡ、相対湿度３７．３％、風量３４１ｍ³／ｈの空調用空気ＳＡとして空調対象空間（図示せず）に導かれることとなった。尚、当該シミュレーションにおいて、ロータ部１０の吸湿部１０ｂにおける除湿量は、１．８９ｋｇ／ｈ（正味除湿量は１．３２ｋｇ／ｈ）となり、熱媒の戻り温度は、６１．６℃となり、熱媒熱負荷は１９７８Ｗとなった。 On the other hand, a similar simulation was performed in the prior art shown in FIG. FIG. 8 shows the circuit state during the humidifying and heating operation, assuming that the circuit state during the dehumidifying and cooling operation is set by rotating the first four-way switching valve 31 and the second four-way switching valve 32. The simulation was performed. The simulation conditions are the same as those described above except that the heat transfer coefficient of the heat exchanger 23 is 190 W / K and the second heater 22 is not provided.
As a result of the simulation, in the prior art shown in FIG. 8, although not shown in the air diagram, the outdoor air OA is dehumidified and cooled to a temperature of 31.4 ° C., an absolute humidity of 10.1 g / kgDA, and a relative humidity of 37.degree. The air-conditioning air SA with 3% and air volume of 341 m ³ / h was led to the air-conditioning target space (not shown). In this simulation, the dehumidifying amount in the moisture absorbing portion 10b of the rotor portion 10 is 1.89 kg / h (net dehumidifying amount is 1.32 kg / h), the return temperature of the heat medium is 61.6 ° C., The medium heat load was 1978 W.

これらの結果より、熱媒の導入温度及び循環流量が同一である場合、本発明の空調装置１００によれば、図８に示す従来技術に比べ、空調用空気ＳＡの温度を４．５℃低下させることができ、除湿量も２７０ｇ／ｋｇＤＡ増加させることができるといえる。 From these results, when the introduction temperature of the heat medium and the circulation flow rate are the same, according to the air conditioner 100 of the present invention, the temperature of the air conditioning air SA is lowered by 4.5 ° C. compared to the prior art shown in FIG. It can be said that the amount of dehumidification can be increased by 270 g / kgDA.

〔加湿暖房運転〕
加湿暖房運転では、図示しない制御装置による制御により、第１四方切替弁３１と第２四方切替弁３２とを、図３に示す回路状態へと切り替えられる。これにより、室外空気ＯＡは、第２空調流路Ｒ２を通流して空調され、空調用空気ＳＡとして空調対象空間（図示せず）へ導かれる。一方、室内空気ＲＡは、第１空調流路Ｒ１を通流した後に排気ＶＡとして空調対象空間の外部へ導かれる。
説明を追加すると、室外空気ＯＡは、第１四方切替弁３１を通過した後に、第１加湿器２４にて加湿冷却され、対向流型熱交換器２３にて室内空気ＲＡと熱交換して昇温し、第１加熱器２５にて熱媒との熱交換により加熱されて十分に昇温され、ロータ部１０の再生部１０ａにて放湿時の吸熱作用による温度低下を伴って加湿され、第２ファン２６にて圧送されて第２四方切替弁３２を通過した後、空調用空気ＳＡとして空調対象空間へ供給される。
一方、室内空気ＲＡは、第１四方切替弁３１を通過した後に、第１ファン２１で圧送され、ロータ部１０の吸湿部１０ｂにて吸湿時の放熱作用による温度上昇を伴って除湿され、第２加熱器２２にて熱媒との熱交換により加熱され、対向流型熱交換器２３にて室外空気ＯＡと熱交換して降温し、第２四方切替弁３２を通過した後に、排気ＶＡとして空調対象空間の外部へ排出される。 [Humidification heating operation]
In the humidifying and heating operation, the first four-way switching valve 31 and the second four-way switching valve 32 are switched to the circuit state shown in FIG. 3 by control by a control device (not shown). Thereby, the outdoor air OA flows through the second air conditioning channel R2 and is air-conditioned, and is led as air conditioning air SA to an air conditioning target space (not shown). On the other hand, the indoor air RA is guided to the outside of the air-conditioning target space as the exhaust VA after flowing through the first air-conditioning flow path R1.
When the explanation is added, the outdoor air OA is humidified and cooled by the first humidifier 24 after passing through the first four-way switching valve 31, and is raised by exchanging heat with the indoor air RA in the counterflow heat exchanger 23. Is heated by heat exchange with the heat medium in the first heater 25 and sufficiently heated, and is humidified with a temperature decrease due to an endothermic action during moisture release in the regeneration unit 10a of the rotor unit 10, After being pumped by the second fan 26 and passing through the second four-way switching valve 32, the air-conditioning air SA is supplied to the air-conditioning target space.
On the other hand, the indoor air RA is pumped by the first fan 21 after passing through the first four-way switching valve 31, is dehumidified with a temperature increase due to a heat dissipation action during moisture absorption by the moisture absorbing part 10b of the rotor part 10, 2 is heated by heat exchange with the heat medium in the heater 22, is cooled by exchanging heat with the outdoor air OA in the counterflow heat exchanger 23, passes through the second four-way switching valve 32, and then is exhausted as VA It is discharged outside the air-conditioned space.

〔加湿暖房運転における空調性能〕
当該除湿冷房運転の除湿冷房性能を、シミュレーションにより評価する。図４に示されるＰ１〜Ｐ９は、図３における回路上のＰ１〜Ｐ９に対応しており、図４の空気線図では、各Ｐ１〜Ｐ９における気体の状態（温度、絶対湿度、相対湿度）を示している。
以下、シミュレーションを行う条件につき、上記除湿冷房運転のシミュレーションの条件と異なるものについて示す。
加湿暖房運転のシミュレーションの条件は、室内空気ＲＡが、温度１６．８℃、絶対湿度５．３ｇ／ｋｇＤＡ、相対湿度４５％とし、室外空気ＯＡが、温度７．０℃、絶対湿度２．３ｇ／ｋｇＤＡ、相対湿度３９％とし、室内空気ＲＡ及び室外空気ＯＡの流量（換気流量）が、３４７ｍ³／ｈとする。
空調装置１００を構成する各機器の条件としては、第１ファン２１の揚程を７８０Ｐａとし、第２ファン２６の揚程を７００Ｐａとし、第１加湿器２４の水噴霧量を０．１０ｋｇ／ｈとし、熱媒の導入温度を６０℃、循環流量を１．７Ｌ／ｍｉｎとする。 [Air conditioning performance in humidification heating operation]
The dehumidifying and cooling performance of the dehumidifying and cooling operation is evaluated by simulation. P1 to P9 shown in FIG. 4 correspond to P1 to P9 on the circuit in FIG. 3. In the air diagram of FIG. 4, the gas states (temperature, absolute humidity, relative humidity) in each of P1 to P9 are shown. Is shown.
Hereinafter, the simulation conditions are different from the simulation conditions of the dehumidifying and cooling operation.
The conditions for the simulation of the humidifying and heating operation are as follows: indoor air RA has a temperature of 16.8 ° C., absolute humidity 5.3 g / kg DA, and relative humidity 45%, outdoor air OA has a temperature 7.0 ° C., and absolute humidity 2.3 g. / KgDA, relative humidity 39%, and the flow rates (ventilation flow rate) of the indoor air RA and the outdoor air OA are 347 m ³ / h.
As conditions of each apparatus which comprises the air conditioner 100, the lift of the 1st fan 21 shall be 780 Pa, the lift of the 2nd fan 26 shall be 700 Pa, the water spray amount of the 1st humidifier 24 shall be 0.10 kg / h, The introduction temperature of the heat medium is 60 ° C., and the circulation flow rate is 1.7 L / min.

上記条件でシミュレーションを行った結果、図４の空気線図に示すように、室内空気ＲＡが除湿・降温されて排気ＶＡとして排出されるのに伴って、室外空気ＯＡが、加湿・昇温され、温度３６．０℃、絶対湿度５．６ｇ／ｋｇＤＡ、相対湿度１５％、風量３８２ｍ³／ｈの空調用空気ＳＡ（図４でＰ５における空気）として空調対象空間（図示せず）に導かれることとなった。尚、当該シミュレーションにおいて、ロータ部１０の再生部１０ａにおける加湿量（図２でＰ４―Ｐ５での除湿量）は、１．３４ｇ／ｈ（正味除湿量は１．４４ｋｇ／ｈ）となり、熱媒の戻り温度は、３６．８℃となり、熱媒熱負荷は２７２２Ｗとなった。 As a result of the simulation under the above conditions, as shown in the air diagram of FIG. 4, the outdoor air OA is humidified and heated as the indoor air RA is dehumidified and cooled and discharged as exhaust VA. The air-conditioning air SA having a temperature of 36.0 ° C., an absolute humidity of 5.6 g / kgDA, a relative humidity of 15%, and an air volume of 382 m ³ / h (air at P5 in FIG. 4) is led to the air-conditioning target space (not shown). It became a thing. In the simulation, the humidification amount (the dehumidification amount at P4-P5 in FIG. 2) in the regeneration unit 10a of the rotor unit 10 is 1.34 g / h (the net dehumidification amount is 1.44 kg / h). The return temperature was 36.8 ° C., and the heat transfer heat load was 2722 W.

一方、図８に示す従来技術においても同様のシミュレーションを行った。シミュレーションの条件は、熱交換器２３の伝熱係数を１９０Ｗ／Ｋとする点、第２加熱器２２を設けない点、及び第２ファン２６の揚程を７１７Ｐａとする点以外は、上述の条件と同様である。
当該シミュレーションの結果、図８に示す従来技術では、空気線図には示さないが、室外空気ＯＡが、除湿・冷却され、温度３０．９℃、絶対湿度５．４ｇ／ｋｇＤＡ、相対湿度２０％、風量３７３ｍ³／ｈの空調用空気ＳＡとして空調対象空間（図示せず）に導かれることとなった。尚、当該シミュレーションにおいて、ロータ部１０の再生部１０ａにおける加湿量は、１．２４ｋｇ／ｈ（正味除湿量は１．３４ｋｇ／ｈ）となり、熱媒の戻り温度は、３８．８℃となり、熱媒熱負荷は２８９７Ｗとなった。 On the other hand, a similar simulation was performed in the prior art shown in FIG. The simulation conditions are the same as those described above except that the heat transfer coefficient of the heat exchanger 23 is 190 W / K, the second heater 22 is not provided, and the lift of the second fan 26 is 717 Pa. It is the same.
As a result of the simulation, in the prior art shown in FIG. 8, the outdoor air OA is dehumidified and cooled to a temperature of 30.9 ° C., an absolute humidity of 5.4 g / kgDA, and a relative humidity of 20%, although not shown in the air diagram. Thus, the air-conditioning air SA having an air volume of 373 m ³ / h was led to an air-conditioning target space (not shown). In this simulation, the humidification amount in the regeneration unit 10a of the rotor unit 10 is 1.24 kg / h (net dehumidification amount is 1.34 kg / h), the return temperature of the heat medium is 38.8 ° C., The medium heat load was 2897W.

これらの結果より、熱媒の導入温度及び循環流量が同一である場合、本発明の空調装置１００によれば、図８に示す従来技術に比べ、空調用空気ＳＡの温度を５．１℃上昇させることができ、加湿量も１００ｇ／ｋｇＤＡ増加させることができるといえる。 From these results, when the introduction temperature of the heat medium and the circulation flow rate are the same, according to the air conditioner 100 of the present invention, the temperature of the air conditioning air SA is increased by 5.1 ° C. as compared to the prior art shown in FIG. It can be said that the humidification amount can also be increased by 100 g / kgDA.

次に、当該加湿暖房運転において、本発明と従来技術でのエクセルギーサンキーダイアグラムを比較したものを図５に示す。ここで、エクセルギーとは、ある系から仕事として取り出せるエネルギーのことであり、エクセルギー損失とは、当該仕事を取り出す際に、エントロピーの増大により伝熱や燃焼などの過程において必ず発生する有効仕事に変換できないエネルギーのことをいう。
当該ダイアグラムを、加熱器でのエクセルギー損失の観点でみると、従来技術の加熱器でのエクセルギー損失は４４６Ｗであり、本発明の加熱器（第１加熱器の９５Ｗと第２加熱器６６Ｗとの合計）でのエクセルギー損失は１６１Ｗであるから、エクセルギー損失の低減率は、（４４５Ｗ−１６１Ｗ）／４４５Ｗ≒６５％となることがわかる。これにより、同様の負荷で加湿暖房運転を行う場合、熱媒の循環量を従来技術に比べて約４５％まで減らすことが可能となる。 Next, FIG. 5 shows a comparison of the exergy sanky diagrams of the present invention and the prior art in the humidifying and heating operation. Here, exergy is energy that can be extracted as work from a certain system, and exergy loss is effective work that is always generated in the process of heat transfer and combustion due to increased entropy when the work is extracted. The energy that cannot be converted into.
From the viewpoint of the exergy loss in the heater, the exergy loss in the prior art heater is 446 W, and the heaters of the present invention (95 W of the first heater and 66 W of the second heater). The exergy loss is 161 W, and the reduction rate of the exergy loss is (445W-161W) / 445W≈65%. Thereby, when performing humidification heating operation by the same load, it becomes possible to reduce the circulation amount of a heat medium to about 45% compared with a prior art.

〔第２実施形態〕
第１実施形態に係る空調装置１００にあっては、除湿冷房運転時において、第１空調流路Ｒ１を通流する空気（空調用空気として供給される空気）が、ロータ部１０の吸湿部１０ｂを通過して除湿され、第２加熱器２２にて加熱され、対向流型熱交換器２３における熱交換により降温し、第２加湿器４１にて加湿冷却され、空調用空気ＳＡとして空調用空間に供給される。しかしながら、除湿冷房運転時で、第１空調流路Ｒ１を通流する空気（空調用空気として供給される空気）の除湿よりも降温を優先させる場合には、当該空気を第２加熱器２２での加熱を行わないことが好ましい。
当該第２実施形態では、第１空調流路Ｒ１において、第２加熱器２２をバイパスするバイパス路Ｒ４を備えると共に、第１空調流路Ｒ１を通流する空気の通流状態を、バイパス路Ｒ４の側に通流するバイパス状態と、第２加熱器２２の側に通流する非バイパス状態との間で択一的に切り換える三方弁４２を備えている。
これにより、除湿冷房運転時には、図示しない制御装置により、三方弁４２が、第１空調流路Ｒ１を通流する空気が第２加熱器２２をバイパスするバイパス状態に切り換え制御され、第１空調流路Ｒ１を通流する空気が第２加熱器２２にて不要に昇温させることを回避し、空調用空気ＳＡの温度を、比較的低温に維持する。
ここで、上記三方弁４２及びその開閉状態を制御する制御装置が、通流状態切替手段として働く。
尚、当該第２実施形態においても、加湿暖房運転時には、第１空調流路Ｒ１を通流する空気が第２加熱器２２を通過する非バイパス状態とし、熱媒の保有する熱を第２加熱器２２でも十分に回収し、エクセルギー損失を低減する。 [Second Embodiment]
In the air conditioner 100 according to the first embodiment, during the dehumidifying and cooling operation, the air flowing through the first air conditioning channel R1 (air supplied as air for air conditioning) is the moisture absorbing unit 10b of the rotor unit 10. , Dehumidified, heated by the second heater 22, cooled by heat exchange in the counter-flow heat exchanger 23, humidified and cooled by the second humidifier 41, and air-conditioned space SA as air-conditioning air SA To be supplied. However, in the dehumidifying and cooling operation, when priority is given to lowering the temperature over the dehumidification of the air flowing through the first air conditioning channel R1 (air supplied as air conditioning air), the air is supplied to the second heater 22. It is preferable not to perform heating.
In the second embodiment, the first air conditioning flow path R1 includes the bypass path R4 that bypasses the second heater 22, and the air flow state that flows through the first air conditioning flow path R1 is changed to the bypass path R4. A three-way valve 42 that selectively switches between a bypass state that flows to the second heater 22 and a non-bypass state that flows to the second heater 22 side is provided.
Thus, during the dehumidifying and cooling operation, the three-way valve 42 is controlled to be switched to a bypass state in which the air flowing through the first air conditioning flow path R1 bypasses the second heater 22 by a control device (not shown). The air flowing through the path R1 is prevented from being unnecessarily heated by the second heater 22, and the temperature of the air conditioning air SA is maintained at a relatively low temperature.
Here, the control device for controlling the three-way valve 42 and its open / close state functions as a flow state switching means.
In the second embodiment as well, during the humidifying and heating operation, the air flowing through the first air conditioning channel R1 is in a non-bypass state in which it passes through the second heater 22, and the heat held by the heat medium is second heated. The vessel 22 is also fully recovered to reduce exergy loss.

〔別実施形態〕
（１）上記実施形態において、室外空気ＯＡと室内空気ＲＡとを熱交換する熱交換器２３は、そこでの温端温度差を減少させて、エクセルギー損失を低減するべく、伝熱係数の高い対向流型の熱交換器を採用した。しかしながら、ある程度のエクセルギー損失の低減を許容できる場合には、当該熱交換器２３は、クロスフィン型の熱交換器等を採用することもできる。 [Another embodiment]
(1) In the above embodiment, the heat exchanger 23 for exchanging heat between the outdoor air OA and the indoor air RA has a high heat transfer coefficient in order to reduce the temperature difference at that temperature and reduce exergy loss. A counter-flow heat exchanger was adopted. However, when a certain amount of exergy loss can be allowed to be reduced, the heat exchanger 23 may be a cross-fin heat exchanger or the like.

（２）上記第２実施形態では、第１空調流路Ｒ１を通流する空気を第２加熱器２２をバイパスさせるバイパス状態と、バイパスさせない非バイパス状態とを、択一的に切り換え可能な構成において、除湿冷房運転時にあっては、第２加熱器２２をバイパスするバイパス状態とする例を示した。
しかしながら、本発明にあっては、第１空調流路Ｒ１を通流する室外空気ＯＡが第２加熱器２２で回収した熱は、対向流型熱交換器２３で回収され、ロータ部１０の再生部１０ａにてデシカントロータ１１の再生の用に供される。即ち、第１空調流路Ｒ１を通流する室外空気ＯＡが、第２加熱器２２で回収した熱が多いほど、デシカントロータ１１の再生が促進されるため、第１空調流路Ｒ１を通流する室外空気ＯＡが、ロータ部１０の吸湿部１０ｂでのデシカントロータ１１により吸湿される吸湿量が多くなる。
従って、除湿冷房運転において、降温よりも除湿を優先させる場合には、バイパス状態としても構わない。
また、三方弁４２は、第１空調流路Ｒ１を通流する空気を、第２加熱器２２の側とバイパス路Ｒ４の側とで択一的に切り換えるのではなく、要求される除湿量・降温量に応じて、空気の一部を第２加熱器２２の側へ導き、空気の残部をバイパス路Ｒ４の側へ導く流量調整機能を有するものを採用することができる。 (2) In said 2nd Embodiment, the structure which can selectively switch between the bypass state which bypasses the 2nd heater 22 with the air which flows through 1st air-conditioning flow path R1, and the non-bypass state which does not bypass In the above, an example in which the second heater 22 is bypassed is shown in the dehumidifying and cooling operation.
However, in the present invention, the heat recovered by the second heater 22 in the outdoor air OA flowing through the first air conditioning flow path R1 is recovered by the counterflow heat exchanger 23 to regenerate the rotor unit 10. The part 10a is used for the regeneration of the desiccant rotor 11. That is, since the regeneration of the desiccant rotor 11 is promoted as the outdoor air OA flowing through the first air conditioning channel R1 has more heat recovered by the second heater 22, the flow through the first air conditioning channel R1. The amount of moisture absorbed by the outdoor air OA to be absorbed by the desiccant rotor 11 in the moisture absorbing portion 10b of the rotor portion 10 increases.
Therefore, in the dehumidifying and cooling operation, when priority is given to dehumidification over temperature drop, a bypass state may be used.
Further, the three-way valve 42 does not selectively switch the air flowing through the first air conditioning channel R1 between the second heater 22 side and the bypass channel R4 side, but the required dehumidification amount / Depending on the temperature drop, it is possible to adopt a flow rate adjusting function that guides a part of the air to the second heater 22 side and guides the remaining part of the air to the bypass path R4 side.

（３）本発明の空調装置１００は、加湿暖房運転と除湿冷房運転とが切替可能な空調装置に限定されるものではない。例えば、図８に示すように、第１四方切替弁３１及び第２四方切替弁３２を含まず、加湿暖房運転のみを行う空調装置をも含むものである。
当該構成においても、加湿暖房運転においては、上述の実施形態で説明したように、エクセルギー損失の低減を図ることができる。 (3) The air conditioner 100 of the present invention is not limited to an air conditioner capable of switching between a humidifying and heating operation and a dehumidifying and cooling operation. For example, as shown in FIG. 8, the first four-way switching valve 31 and the second four-way switching valve 32 are not included, and an air conditioner that performs only humidification heating operation is also included.
Even in this configuration, in the humidifying and heating operation, as described in the above-described embodiment, it is possible to reduce the exergy loss.

本発明の空調装置、及びその運転方法は、従来にない回路構成を採用することにより、特に、冬季で熱不足が発生する状況であっても、エクセルギー損失の低減を図ることができながら、実用に耐え得る加湿暖房運転を実行可能な空調装置及びその運転方法として、有効に利用可能である。 The air conditioner of the present invention and the operation method thereof adopt a circuit configuration that has not been used in the past, and in particular, even in a situation where heat shortage occurs in winter, it is possible to reduce exergy loss, The present invention can be effectively used as an air conditioner capable of performing a humidifying and heating operation that can withstand practical use and an operation method thereof.

１０：ロータ部
１０ａ：再生部
１０ｂ：吸湿部
１１：デシカントロータ
２２：第２加熱器
２３：対向流型熱交換器
２４：第１加湿器
２５：第１加熱器
３１：第１四方切替弁
３２：第２四方切替弁
４１：第２加湿器
１００：空調装置
ＯＡ：室外空気
Ｒ１：第１空調流路
Ｒ２：第２空調流路
Ｒ４：バイパス路
ＲＡ：室内空気
ＳＡ：空調用空気
ＶＡ：排気 DESCRIPTION OF SYMBOLS 10: Rotor part 10a: Regenerating part 10b: Hygroscopic part 11: Desiccant rotor 22: 2nd heater 23: Counterflow type heat exchanger 24: 1st humidifier 25: 1st heater 31: 1st four-way switching valve 32 : Second four-way switching valve 41: second humidifier 100: air conditioner OA: outdoor air R1: first air conditioning channel R2: second air conditioning channel R4: bypass channel RA: indoor air SA: air conditioning air VA: exhaust

Claims

A rotor unit for dehumidifying and humidifying the air by rotating and driving a desiccant rotor made of a breathable hygroscopic material between a hygroscopic unit through which air flows and a regeneration unit;
A first heater that heats the air before passing through the regeneration portion of the rotor portion with a heat medium guided from the outside;
Humidification supplied to the heat exchanger for exchanging heat with the air after passing through the moisture absorption part of the rotor part, the first heater, and the regeneration part of the rotor part and supplied as air for air conditioning An air conditioner capable of performing heating operation,
A first humidifier for humidifying the air;
A second heater that heats the air after passing through the hygroscopic part of the rotor part with a heat medium after passing through the first heater;
A first air-conditioning flow path for allowing air to pass through the hygroscopic portion of the rotor portion, the second heater, and the heat exchanger in the order described; and air for the first humidifier, the heat exchanger, and the first heating. And a second air-conditioning channel that passes through the regenerator and the regenerating unit of the rotor unit in the order described,
An air conditioner configured to execute a humidifying and heating operation in which the air flowing through the second air conditioning channel is supplied as air conditioning air and the air flowing through the first air conditioning channel is discharged as exhaust.

An operation for selectively switching between the dehumidifying and cooling operation for supplying the air that has passed through the first air-conditioning channel as air-conditioning air and exhausting the air that has passed through the second air-conditioning channel as an exhaust, and the humidifying and heating operation. The air conditioner of Claim 1 provided with a switching means.

The first air conditioning flow path includes a bypass path that bypasses the second heater,
A flow state switching means that selectively switches between a bypass state in which air is passed through a bypass passage that bypasses the second heater and a non-bypass state that passes through the second heater;
The air conditioner according to claim 2, wherein the flow state switching means switches to the bypass state during the dehumidifying and cooling operation and switches to the non-bypass state during the humidifying and heating operation.

A second humidifier that humidifies air separately from the first humidifier;
The air conditioner according to claim 2 or 3, wherein the air after passing through the first air conditioning channel is humidified and cooled by the second humidifier during the dehumidifying and cooling operation.

The said heat exchanger is a counterflow type heat exchanger which heat-exchanges the air which flows through the said 1st air conditioning channel | path and the air which flows through the said 2nd air conditioning channel | channel by counterflow. The air conditioner according to any one of the above.

In the air conditioner as described in any one of Claims 1-5,
The temperature of the heat medium guided to the first heater is set higher than the temperature of the air passing through the first heater in the second air conditioning channel, and the heat medium guided to the second heater is A method for operating an air conditioner, wherein a temperature is set higher than a temperature of air passing through the second heater in the first air conditioning channel.