CN117419389A

CN117419389A - Air conditioner and air conditioning system

Info

Publication number: CN117419389A
Application number: CN202310879441.2A
Authority: CN
Inventors: 严辰旭; 松村贤治; 内藤宏治
Original assignee: Hitachi Johnson Controls Air Conditioning Inc
Current assignee: Hitachi Johnson Controls Air Conditioning Inc
Priority date: 2022-07-19
Filing date: 2023-07-18
Publication date: 2024-01-19
Also published as: JP7312894B1; JP2024013040A

Abstract

The invention provides an air conditioner and an air conditioning system, which have excellent operation efficiency. An air conditioner (1) is provided with: a dehumidifying rotor (2); a heat exchanger (31) provided in the flow path (71) and arranged upstream of the air flow of the dehumidifying rotor; a heat exchanger (32) disposed in parallel with the heat exchanger (31) and disposed downstream of the air flow of the dehumidifying rotor; a heat exchanger (33) provided in the flow path (72) and arranged upstream of the air flow of the dehumidifying rotor; a heat exchanger (34) disposed in parallel with the heat exchanger (33) and disposed downstream of the air flow of the dehumidifying rotor; an expansion valve (41) for controlling the flow rate of the refrigerant to the heat exchanger (31); an expansion valve (42) which is separate from the expansion valve (41) and controls the flow rate of the refrigerant to the heat exchanger (32); an expansion valve (43) for controlling the flow rate of the refrigerant to the heat exchanger (33); an expansion valve (44) which is separate from the expansion valve (43) and controls the flow rate of the refrigerant to the heat exchanger (34); a compressor (5).

Description

Air conditioner and air conditioning system

Technical Field

The present disclosure relates to an air conditioner and an air conditioning system.

Background

In the field of air conditioners, energy saving performance is improved in consideration of comfort. Therefore, as an electrical device that is active in a living room environment of a person, "improvement of energy saving performance" is not simply "reduction of power consumption", but is established on the premise of "comfort is not impaired".

Ventilation of buildings is essential to maintain hygiene in living rooms. However, in a general ventilator, the latent heat load and the sensible heat load increase due to the introduction of outside air. Therefore, the air conditioner cannot maintain comfort due to insufficient dehumidification capability, and power consumption of the air conditioner increases.

Patent document 1 discloses a "ventilator (100) including a first air flow path (12), a second air flow path (13), an outdoor temperature detection means (23), an outdoor humidity detection means (24), a rotary moisture adsorption means (8), a refrigerant means (90), and a control unit (31) for controlling, wherein the ventilator (100) is characterized in that: comprises a dehumidification mode (II), a humidification mode (III), a cooling mode (IV), a heating mode (V), a total heat exchange mode (VI) and a purification mode (I), wherein the control part (31) operates in any mode according To the outdoor detected humidity (Ho) and the outdoor detected temperature (To).

Prior art literature

Patent document 1: japanese patent application laid-open No. 2019-82308

Disclosure of Invention

Problems to be solved by the invention

In the technique described in patent document 1, the flow rate of the refrigerant to the first heat exchanger 5 and the third heat exchanger 4 is controlled by the first expansion valve 18. The flow rate of the refrigerant to the second heat exchanger 7 and the fourth heat exchanger 6 is controlled by the second expansion valve 19. Therefore, the flow rate of the refrigerant to the four heat exchangers cannot be independently controlled. Therefore, the operation amount of the heat exchanger cannot be finely controlled on the adsorption side and the regeneration side of the desiccant rotor 8 or on the upstream side and the downstream side of the air flow, and the operation efficiency is liable to be lowered.

An object of the present disclosure is to provide an air conditioner and an air conditioning system having excellent operation efficiency.

Effects of the invention

According to the present disclosure, an air conditioner and an air conditioning system having excellent operation efficiency can be provided.

Drawings

Fig. 1 is a schematic view showing an air conditioner according to an embodiment.

Fig. 2 is a plan view of the air conditioner shown in fig. 1 as viewed from above.

Fig. 3 is a plan view of the air conditioner shown in fig. 1, viewed from the lateral direction.

Fig. 4 is a schematic view showing an air conditioner according to another embodiment.

Fig. 5 is a schematic view showing an air conditioner according to another embodiment.

Fig. 6 is a schematic view showing an air conditioner according to another embodiment.

Fig. 7 is a schematic view showing an air conditioner according to another embodiment.

Fig. 8 is a flow when the first operation mode is performed.

Fig. 9 is a flow when the second operation mode is performed.

Fig. 10 is an air line graph showing the relationship between the dry bulb temperature and the absolute humidity.

FIG. 11 is a graph showing water vapor adsorption isotherms.

Fig. 12 is a diagram illustrating the flow of refrigerant in the dehumidification mode.

Fig. 13 is a diagram illustrating the flow of refrigerant in the humidification mode.

Fig. 14 is a diagram illustrating the flow of refrigerant in the cooling mode.

Fig. 15 is a diagram illustrating the flow of refrigerant in the heating mode.

Fig. 16 is a diagram illustrating the flow of refrigerant in the normal ventilation mode.

Fig. 17 is a block diagram of an air conditioning system of the present invention.

Fig. 18 is a block diagram of an air conditioning system of another embodiment.

Description of the reference numerals

1 air conditioner (first air conditioner)

10 Total heat exchange element (Total heat exchange mechanism)

100 air conditioning system

11 baffle (first switching mechanism)

110 sensor

111 indoor heat exchanger

112 expansion mechanism

113 outdoor heat exchanger

12 flow path (third flow path)

13 flow path (fourth flow path)

2 dehumidifying rotor (adsorption release mechanism)

31 heat exchanger (first heat exchanger)

32 heat exchanger (second heat exchanger)

33 heat exchanger (third heat exchanger)

34 Heat exchanger (fourth heat exchanger)

4 heat exchanger

41 expansion valve (first flow control mechanism)

42 expansion valve (second flow control mechanism)

43 expansion valve (third flow control mechanism)

44 expansion valve (fourth flow control mechanism)

45 refrigeration cycle

5 compressor (first compressor)

50 air conditioner (second air conditioner)

51 compressor

52 outdoor heat exchanger

53 expansion mechanism

54 indoor heat exchanger

55 control device

56 electric signal wire

57 remote controller

58 sensor

6 four-way valve (second switching mechanism)

71 flow path (first flow path)

72 flow path (second flow path)

73 shell

81 fan

82 fan

83 piping

9 control device

94 remote controller

95 sensor.

Detailed Description

Hereinafter, modes (referred to as embodiments) for carrying out the present disclosure will be described with reference to the drawings. In the following description of one embodiment, description of other embodiments applicable to one embodiment is also made as appropriate. The present disclosure is not limited to the following embodiments, and different embodiments can be combined with each other or arbitrarily modified within a range that does not significantly impair the effects of the present disclosure. The same reference numerals are given to the same components, and duplicate descriptions are omitted. The components having the same functions are given the same names. The content of the drawings is merely illustrative, and for convenience of illustration, the actual configuration may be changed or some of the components may be omitted from the drawings or modified within a range that does not significantly impair the effects of the present disclosure.

Fig. 1 is a schematic diagram showing an air conditioner 1 according to an embodiment. The air conditioner 1 (air conditioner outdoor unit) performs air conditioning on outdoor air OA such as outdoors, for example, and supplies the air OA as air SA to the indoor space. The air conditioner 1 appropriately collects sensible heat and latent heat from indoor air RA and then discharges the sensible heat and latent heat as air EA to the outside such as the outside. Adsorption and release of moisture are performed between the flow path 71 and the flow path 72.

The air conditioner 1 includes a dehumidifying rotor 2. The dehumidifying rotor 2 is an example of a rotary adsorption/release mechanism. The rotary adsorption/release mechanism is not limited to the dehumidifying rotor as long as it is a mechanism capable of adsorbing and releasing moisture by rotation. The air conditioner 1 further includes a heat exchanger 31 (first heat exchanger), a heat exchanger 32 (second heat exchanger), a heat exchanger 33 (third heat exchanger), and a heat exchanger 34 (fourth heat exchanger). The air conditioner 1 further includes an expansion valve 41 (an example of a first flow rate adjustment mechanism), an expansion valve 42 (an example of a second flow rate adjustment mechanism), an expansion valve 43 (an example of a third flow rate adjustment mechanism), and an expansion valve 44 (an example of a fourth flow rate adjustment mechanism). The flow rate adjustment mechanisms are not limited to the expansion valves, as long as they can adjust the flow rate. The air conditioner 1 includes a compressor 5, and in the example of fig. 1, a four-way valve 6.

The dehumidifying rotor 2 is disposed across a flow path 71 (first flow path, fig. 3) and a flow path 72 (second flow path, fig. 3). An air flow indicated by a solid arrow is formed in the flow path 71. An air flow indicated by a broken-line arrow is formed in the flow path 72. The flow path 71 supplies outdoor air OA to an indoor space (not shown) to be air-conditioned. The air SA after air conditioning is introduced into the room by driving the fan 81. Therefore, the air SA is generated from the air OA taken into the flow path 71 by the air conditioner 1. The flow path 72 discharges the indoor air RA to the outside. The air RA is used for air conditioning of the air OA. The air EA used for air OA is discharged to the outside by driving the fan 82. Therefore, the air EA is generated from the air RA taken into the flow path 72 by the air conditioner 1.

The dehumidifying rotor 2 adsorbs moisture in the air OA, RA flowing through one of the flow paths 71, 72 by, for example, continuous rotation of a motor (not shown), and releases the moisture to the air SA, EA flowing through the other flow path 72, 71. By releasing, the desiccant rotor 2 regenerates. For example, in summer or the like, the air OA is highly humid. Therefore, by the rotation of the dehumidifying rotor 2, moisture in the air OA is adsorbed by the dehumidifying rotor 2. Thereby, air SA having reduced humidity is generated. On the other hand, the moisture adsorbed on the dehumidifying rotor 2 is released to the air EA. Thereby, moisture in the air OA is discharged outdoors via the air EA.

On the other hand, for example, in winter season, the air OA is low humidity. The air RA from the room has a certain degree of humidity due to a person in the room or the like. Therefore, by the rotation of the dehumidifying rotor 2, moisture in the air RA is adsorbed by the dehumidifying rotor 2. Thereby, moisture in the air RA is recovered, and the recovered air EA is discharged outdoors. On the other hand, the moisture adsorbed on the dehumidifying rotor 2 is released to the air SA. This allows moisture recovered from the indoor air RA to be returned to the room via the air SA.

The heat exchanger 31 is provided in the flow path 71 and is disposed upstream of the air flow (indicated by solid arrows) of the dehumidifying rotor 2. Therefore, the heat exchanger 31 preheats or precools the air OA supplied to the dehumidifying rotor 2. The heat exchanger 32 is disposed on the downstream side of the air flow (indicated by solid arrows) of the dehumidifying rotor 2. Therefore, the air humidified or dehumidified by the dehumidifying rotor 2 and heated or cooled by the heat exchanger 32 is supplied as air SA into the room. The heat exchanger 32 is disposed in parallel with the heat exchanger 31 in the refrigerant flow indicated by the broken-line arrow. Therefore, the refrigerant compressed by the compressor 5 flows in parallel to the heat exchangers 31 and 32, which will be described in detail later.

The heat exchanger 33 is provided in the flow path 72 and is disposed upstream of the air flow (indicated by the broken arrow) of the desiccant rotor 2. Therefore, the heat exchanger 33 preheats or precools the air RA supplied to the dehumidifying rotor 2. The heat exchanger 34 is disposed on the downstream side of the air flow (indicated by the broken arrow) of the dehumidifying rotor 2. Therefore, the air humidified or dehumidified by the dehumidifying rotor 2 and heated or cooled by the heat exchanger 34 is discharged to the outside as air EA. The heat exchanger 34 is disposed in parallel with the heat exchanger 33 in the refrigerant flow indicated by the broken line arrow. Therefore, the refrigerant compressed by the compressor 5 flows in parallel to the heat exchangers 33 and 34, which will be described in detail later.

As described above, the heat exchangers 31 and 33 disposed upstream of the dehumidifying rotor 2 are used for preheating or precooling the air OA and RA, for example. On the other hand, the heat exchanger 32 and the heat exchanger 34 disposed downstream of the dehumidifying rotor 2 are used for, for example, post-treatment of the air treated by the dehumidifying rotor 2 and improvement of efficiency of the refrigeration cycle.

Fig. 2 is a plan view of the air conditioner 1 shown in fig. 1 as viewed from above. Fig. 3 is a plan view of the air conditioner 1 shown in fig. 1 viewed from the lateral direction. The air conditioner 1 includes a flow path 71 in a lower layer and a flow path 72 in an upper layer in the illustrated example, inside a casing 73. The flow path 71 includes an inlet 851 through which the air OA flows in and an outlet 852 through which the air SA flows out. The flow path 72 includes an inlet 853 through which the air RA flows in and an outlet 854 through which the air EA flows out. The inflow openings 851 and 853 and the outflow openings 852 and 854 are formed in the housing 73. In the illustrated example, the heat exchangers 31, 32, 33, 34, the dehumidifying rotor 2, and the fans 81, 82 are accommodated in the housing 73.

The flow path 71 includes a fan 81. By driving the fan 81, the air OA is air-conditioned by the heat exchanger 31, the dehumidifying rotor 2, and the heat exchanger 32, and then the air SA is released into the room. The flow path 72 includes a fan 82. By driving the fan 82, moisture and the like in the air RA are appropriately collected by the heat exchanger 33, the dehumidifying rotor 2, and the heat exchanger 34, and then the air EA is discharged to the outside.

Fig. 4 is a schematic diagram showing an air conditioner 1 according to another embodiment. In the above example, only one dehumidifying rotor 2 is provided, but in the example of fig. 4, a plurality of dehumidifying rotors 2 (adsorption/release mechanisms) are provided. This makes it possible to disperse the adsorption and regeneration functions of the desiccant rotor 2, and to improve the durability of the desiccant rotor 2. In addition, the amount of water that can be adsorbed and regenerated by the dehumidifying rotor 2 can be increased, and extremely fine control can be performed.

The plurality of dehumidifying rotors 2 may be arranged in series with respect to the air flow, or may be arranged in parallel, for example. In the illustrated example, the two dehumidifying rotors 2 are arranged in parallel with respect to the air flow.

Returning to fig. 1, the expansion valve 41 controls the flow of refrigerant to the heat exchanger 31. The expansion valve 42 is formed separately from the expansion valve 41, and controls the flow rate of the refrigerant to the heat exchanger 32. The expansion valve 43 controls the flow of refrigerant to the heat exchanger 33. The expansion valve 44 is formed separately from the expansion valve 43, and controls the flow rate of the refrigerant to the heat exchanger 34. The opening degree of each of the expansion valves 41, 42, 43 can be independently adjusted. The flow rates of the refrigerants flowing through the heat exchangers 31, 32, 33, 34 are independently controlled by the opening degree adjustment of the expansion valves 41, 42, 43, respectively.

The refrigerant flow rate to the heat exchangers 31, 32, 33, 34, that is, the opening degree adjustment of the expansion valves 41, 42, 43, 44, for example, can be determined based on a predetermined relationship. The predetermined relationship may be, for example, a predetermined equation that correlates a difference between the actual humidity and the set humidity with a flow rate ratio. Accordingly, the opening degree of the expansion valves 41, 42, 43, 44 is adjusted so as to be the flow rate ratio determined based on the predetermined expression. This is also true for temperature.

The compressor 5 (first compressor) compresses the refrigerant supplied to the heat exchangers 31, 32, 33, 34. When the operation capacity of the air conditioner 1 is reduced due to, for example, surplus operation capacity, the operation capacity of the air conditioner 1 can be reduced by reducing the rotation speed of the compressor 5, for example.

The four-way valve 6 (an example of the second switching mechanism) controls the flow direction of the refrigerant in the refrigeration cycle 45. The refrigeration cycle 45 is composed of the compressor 5, the heat exchangers 31, 32, 33, 34, and the expansion valves 41, 42, 43. The refrigeration cycle 45 is also suitably provided with an accumulator (not shown) that temporarily stores the refrigerant supplied to the compressor 5. The second switching mechanism is not limited to the four-way valve 6 as long as it can control the flow direction of the refrigerant in the refrigeration cycle 45. By providing the four-way valve 6, the heat exchangers 31, 32, 33, 34 can be switched to either the evaporator or the condenser, and for example, the air SA can be warmed or cooled according to seasons.

Fig. 5 is a schematic diagram showing an air conditioner 1 according to another embodiment. The air conditioner 1 shown in fig. 5 is the same as the air conditioner 1 shown in fig. 1, except that the four-way valve 6 is not provided.

In the air conditioner 1 shown in fig. 5, the direction of flow of the refrigerant in the refrigeration cycle 45 is fixed, for example, in the direction of the broken-line arrow by the absence of the four-way valve 6. The air conditioner 1 can be used as a dehumidification-dedicated or humidification-dedicated air conditioner 1 depending on the installation place, installation environment, or the like of the air conditioner 1. Therefore, in such a case, by fixing the flow direction of the refrigerant in the refrigeration cycle 45, the four-way valve 6 can be omitted, and the control and the device configuration of the air conditioner 1 can be simplified.

Fig. 6 is a schematic diagram showing an air conditioner 1 according to another embodiment. The air conditioner 1 shown in fig. 6 is the same as the air conditioner 1 shown in fig. 1 except that it further includes a total heat exchange element 10.

The total heat exchange element 10 (an example of a total heat exchange means) performs total heat exchange between the air OA from the outside and the air RA from the inside on the upstream side of each of the heat exchangers 31 and 33. The total heat exchange means is not limited to the total heat exchange element 10 as long as it is a means capable of total heat exchange between the air OA from the outside and the air RA from the inside on the upstream side of each of the heat exchangers 31 and 33. By providing the total heat exchange element 10, it is possible to exchange latent heat and sensible heat between the air RA from the indoor and the air OA from the outdoor. Thereby, the air conditioning efficiency can be improved.

Fig. 7 is a schematic diagram showing an air conditioner 1 according to another embodiment. The air conditioner 1 shown in fig. 7 is the same as the air conditioner 1 shown in fig. 1 except that it further includes a total heat exchange element 10, a baffle 11, and flow paths 12 and 13. Fig. 7 is a conceptual diagram illustrating a bypass of the total heat exchange element 10 formed by the baffle 11 and the flow paths 12 and 13, and does not show the actual structure itself of the product. That is, fig. 7 includes at least one of the following two concepts. That is, either air OA (fig. 1) bypasses total heat exchange element 10 before being supplied as air SA (fig. 1), or air RA bypasses total heat exchange element 10 before being exhausted as air EA (fig. 1).

The flow path 12 (third flow path) supplies the air OA from the outside to the total heat exchange element 10. The flow path 13 (fourth flow path) bypasses the total heat exchange element 10 and supplies the air OA from the outside to the heat exchanger 31. In the illustrated example, the baffle 11 (an example of the first switching mechanism) closes one of the flow path 12 and the flow path 13, and switches the flow path of the air OA from the outside to the flow path 12 or the flow path 13. The switching mechanism is not limited to the baffle 11, and any mechanism is possible as long as it can switch the flow path of the air OA to either the flow path 12 or the flow path 13. By providing the flow paths 12, 13 and the baffle 11, for example, whether or not total heat exchange by the total heat exchange element 10 is performed can be switched according to seasons, use conditions, and the like. This reduces unnecessary total heat exchange.

Returning to fig. 1, the refrigerant flows through the pipe 83 as indicated by the broken-line arrow. The refrigerant compressed by the compressor 5 is branched after passing through the four-way valve 6, and is supplied to the heat exchangers 33 and 34. At this time, the flow rate of the refrigerant to the heat exchangers 33, 34 is controlled by adjusting the opening degree of the expansion valves 43, 44 as described above. In the heat exchangers 33, 34, heat of the refrigerant is released to the air RA. The refrigerant flowing out of the heat exchangers 33, 34 is expanded by the expansion valves 43, 44. The expanded refrigerants once merge and branch again. After branching, the mixture is expanded again by expansion valves 41 and 42 and supplied to heat exchangers 31 and 32. As described above, the opening degree of the expansion valves 41 and 42 is adjusted to control the flow rate of the refrigerant flowing to the heat exchangers 31 and 32. In the heat exchangers 31 and 32, the air OA is cooled by the cooled refrigerant. The refrigerants flowing out of the heat exchangers 31 and 32 merge together, pass through the four-way valve 6, and return to the compressor 5.

Fig. 8 is a flow when the first operation mode is performed. The air conditioner 1 has a first operation mode. The first operation mode is controlled to increase the flow rate of the refrigerant to the heat exchangers 31 and 32 or to decrease the flow rate of the refrigerant to the heat exchangers 33 and 34, respectively, in comparison with the steady state. The steady state means that the difference between the indoor temperature and humidity and the set temperature and humidity is within a predetermined range. The predetermined range is a range in which the difference is small to such an extent that the air conditioning operation is not required. By having the first operation mode, the heat exchange amount on the upstream side of the desiccant rotor 2 can be relatively increased compared to the heat exchange amount on the downstream side, and the heat exchange amounts of the latent heat and the sensible heat can be increased.

The control device 9 determines whether or not the difference between the indoor humidity and the set humidity is within a predetermined range every predetermined time (step S1). If the setting range is within (yes), the control device 9 stands by for a predetermined time (step S2). After waiting, the control device 9 executes step S1 again. On the other hand, in step S1, when the difference between the indoor humidity and the set humidity exceeds the predetermined range (no), the control device 9 executes the first operation mode (step S3). When the operation is performed such that the humidity difference is large and the humidity is close to the set humidity, the humidity can be adjusted by increasing the flow rate of the refrigerant on the upstream side of the dehumidifying rotor 2.

Fig. 9 is a flow when the second operation mode is performed. The air conditioner 1 has a second operation mode. The second operation mode performs control to reduce the flow rate of the refrigerant to the heat exchangers 31 and 32 or to increase the flow rate of the refrigerant to the heat exchangers 33 and 34, respectively, in comparison with the steady state. The steady state is synonymous with the steady state described in the first operation mode described above. By providing the second operation mode, the amount of heat exchange on the downstream side of the desiccant rotor 2 is relatively increased compared to the amount of heat exchange on the upstream side, and the amount of post-treatment heat development of the discharged air can be increased, thereby improving the circulation efficiency.

The control device 9 determines whether or not the difference between the indoor temperature and the set temperature is within a predetermined range every predetermined time (step S4). If the setting range is within (yes), the control device 9 stands by for a predetermined time (step S5). After waiting, the control device 9 executes step S4 again. On the other hand, in step S4, when the difference between the indoor temperature and the set temperature exceeds the predetermined range (no), the control device 9 executes the second operation mode (step S6). When the operation is performed such that the temperature difference is large and the temperature is close to the set temperature, the temperature can be adjusted by increasing the flow rate of the refrigerant on the downstream side of the dehumidifying rotor 2.

In the air conditioner 1, the first operation mode, the second operation mode, and the third operation mode can be switched. As described above, in the first operation mode, the refrigerant flow rate to at least one (preferably both) of the heat exchanger 31 and the heat exchanger 33 is made greater than the refrigerant flow rate to at least one (preferably both) of the heat exchanger 32 and the heat exchanger 34. Thereby giving priority to latent heat treatment. As described above, in the second operation mode, the refrigerant flow rate to at least one (preferably both) of the heat exchanger 32 and the heat exchanger 34 is made greater than the refrigerant flow rate to at least one (preferably both) of the heat exchanger 31 and the heat exchanger 33. Thereby, the sensible heat treatment is prioritized. The third operation mode makes the flow rate of the refrigerant to the heat exchanger 31 and the heat exchanger 33 equal to the flow rate of the refrigerant to the heat exchanger 32 and the heat exchanger 34. This improves the operation efficiency. In this way, by being able to switch the first operation mode, the second operation mode, and the third operation mode, improvement of comfort and improvement of energy saving performance for a person located indoors can be more appropriately performed.

In the example of the present disclosure, in the first operation mode, the second operation mode, and the third operation mode, the refrigerant flow rates of both the heat exchangers 31 and 33 are controlled, and the refrigerant flow rates of both the heat exchangers 32 and 34 are controlled. However, for example, in the first operation mode, although the flow rate of the refrigerant to the heat exchanger 31 is larger than the flow rate of the refrigerant to the heat exchanger 32, the flow rate of the refrigerant to the heat exchanger 33 and the flow rate of the refrigerant to the heat exchanger 34 may be controlled to be equal to each other. In the second operation mode, for example, although the flow rate of the refrigerant to the heat exchanger 32 is larger than the flow rate of the refrigerant to the heat exchanger 31, the flow rate of the refrigerant to the heat exchanger 34 may be controlled to be equal to the flow rate of the refrigerant to the heat exchanger 33. That is, for example, control focusing only on the flow path 71 that generates the air SA to be supplied into the room may be performed. Although the explanation is omitted, control focusing only on the flow path 72 through which the air RA discharged from the room flows may be performed.

The operation control of the air conditioner 1 including the first operation mode, the second operation mode, and the third operation mode is performed by the control device 9. The control device 9 includes, for example, a CPU91, a ROM92, a RAM93, and the like. The control device 9 is implemented by expanding a predetermined control program stored in the ROM92 in the RAM93, for example, and executing the program by the CPU91, for example.

Fig. 10 is an air line graph showing the relationship between the dry bulb temperature and the absolute humidity. Fig. 10 illustrates a graph (graph of moisture absorption in the dehumidifying rotor 2) when air SA is generated from air OA when the air conditioner 1 shown in fig. 6 is used. The graph when generating air EA from air RA (graph when regenerating dehumidifying rotor 2) is the same as the graph shown in fig. 10, and therefore is not shown.

The horizontal axis represents dry bulb temperature, and the vertical axis represents absolute humidity. A saturation line L1 shown in the graph is illustrated. In the air conditioner 1 of the present disclosure, the dry-bulb temperature and the absolute humidity can be adjusted as indicated by solid lines and broken lines by independently controlling the flow rates of the refrigerant to the four heat exchangers 31, 32, 33, 34 (fig. 6). For example, in normal operation, control (the third operation mode) is performed as indicated by a solid line. The steady operation is equivalent to the above-described normal operation, and the expansion valves 41, 42, 43, 44 all have the same opening degree in the normal operation. When the absolute humidity cannot be reduced to the set humidity during the normal operation, the control is switched to the control shown by the broken line. The control shown by the broken line is the first operation mode described above. In the illustrated example, the opening degree of the expansion valves 41 and 43 (fig. 6) is controlled to be larger than the opening degree of the expansion valves 42 and 44 (fig. 6), whereby the refrigerant flow rates of the heat exchangers 31 and 32 are larger than the refrigerant flow rates of the heat exchangers 33 and 34. This makes it possible to reduce the absolute humidity as compared with the normal operation.

The air OA undergoes total heat exchange in the total heat exchange element 10 (fig. 6) between point a and point B. Thereby, the dry bulb temperature and absolute humidity are reduced. In the normal operation shown by the solid line, the dry bulb temperature is lowered by cooling the heat exchanger 31 at the evaporating temperature T1 from the point B to the point C1. Between the point C1 to the point D1, moisture is adsorbed to the dehumidifying rotor 2, whereby the absolute humidity is reduced. At this time, the dry bulb temperature rises. At point D1 to point E1, the dry bulb temperature is reduced by being cooled again by the heat exchanger 32. The lowered air is supplied as air SA into the room.

On the other hand, in the first operation mode shown by the broken line from point B to point C2, the refrigerant flow rate in the heat exchangers 31, 33 is greater than that in the normal state (steady operation) as described above. Therefore, the air OA is cooled as compared with the normal air by the heat exchanger 31 having the evaporation temperature T2 lower than the evaporation temperature T1. As a result, the dry bulb temperature is lower than that in the normal state shown by the solid line, and the absolute humidity is also lower than that in the normal state. At the point C2 to the point D2, moisture is adsorbed to the dehumidifying rotor 2 as in the normal case. However, at point C2, the dry bulb temperature is lower than at point C1 at normal times, as described above. Therefore, the precooling effect of the air is large, and thus, although described in detail later, the moisture adsorption effect of the dehumidifying rotor 2 increases. Therefore, the dehumidifying amount of the dehumidifying rotor 2 increases more than usual, and thereby reaches a point D2 where the absolute humidity is lower than a point D1 at usual. From point D2 to point E2, the dry bulb temperature is reduced by re-cooling through heat exchanger 32. The lowered air is supplied as air SA into the room.

In this way, in the normal operation mode, the evaporation temperature T1 of the heat exchanger 31 is made relatively higher than the evaporation temperature T2, and the operation efficiency can be improved. On the other hand, in the first operation mode, for example, when the air OA is high in humidity in summer, the adsorption effect of the dehumidifying rotor 2 can be improved, and the properly dehumidified air SA can be supplied into the room. This can improve the comfort of the person present in the room.

The increase in the adsorption effect of the precooling-based dehumidifying rotor 2 will be described. The adsorption amount of water to the adsorbent of the dehumidifying rotor 2 and the like depends on the air condition. The adsorbent is placed in air under certain conditions, and after a sufficient time, the adsorption amount is no longer changed. The adsorption amount in this state is referred to as equilibrium adsorption amount.

FIG. 11 is a graph showing water vapor adsorption isotherms. In fig. 11, a graph (water vapor adsorption isotherm) is considered in which the horizontal axis represents relative humidity and the vertical axis represents water vapor adsorption amount. The water vapor adsorption isotherm represents the change in equilibrium adsorption amount caused by the change in relative humidity of air. The vertical axis represents the amount of moisture adsorbed per unit mass of the adsorbent, and is the so-called adsorption rate. Thus, the water vapor adsorption isotherm may also be referred to as an adsorption rate curve.

As an example, although an adsorption example for a specific adsorbent is shown, the amount of water vapor adsorption increases as the relative humidity increases, regardless of the material of the adsorbent in the dehumidifying rotor 2. Therefore, the temperature of the air is sufficiently reduced by the heat exchanger 31 before the adsorption by the dehumidifying rotor 2, and the relative humidity is thereby increased. As a result, the amount of water vapor adsorbed increases, and the adsorption effect increases. On the other hand, in the air RA (fig. 1) on the regeneration side, if the air temperature is increased by the increase of the preheating effect, the relative humidity is lowered. Thereby promoting the moisture releasing effect.

Fig. 12 is a diagram illustrating the flow of refrigerant in the dehumidification mode. The dehumidification mode is a mode in which outdoor air OA is dehumidified and supplied to the indoor space, and the air OA sequentially passes through the heat exchanger 31, the dehumidification rotor 2, and the heat exchanger 32 in the flow path 71 (fig. 3). Thereby, the humidity of the air OA is reduced, and the air SA is supplied into the room. At the same time, the air RA sequentially passes through the heat exchanger 33, the dehumidifying rotor 2, and the heat exchanger 34 in the flow path 72. In this way, the air containing the moisture generated by the regeneration of the desiccant rotor 2 and the exhaust heat generated in the refrigeration cycle such as the compressor 5 is discharged to the outside as air EA. By the continuous rotation of the dehumidifying rotor 2, adsorption on the air SA side and regeneration on the air EA side are continuously performed, and moisture moves from the flow path 71 to the flow path 72.

The operation of the refrigeration cycle in the dehumidification mode will be described. The flow of refrigerant based on the operation of the four-way valve 6 is shown by the dashed arrow. The heat exchangers 31 and 32 in the flow path 71 serve as evaporators, and the refrigerant evaporates to reduce the air temperature. At this time, condensation may occur in the heat exchangers 31 and 32 depending on the evaporation temperature and the air condition, and the humidity may be lowered. The heat exchangers 33 and 34 in the flow path 72 serve as condensers, and the refrigerant condenses, whereby heat extracted from the flow path 71 is discharged. The opening degree of each of the expansion valves 41, 42, 43, 44 provided in each of the four heat exchangers 31, 32, 33, 34 is controlled to control the flow rate of the refrigerant to each of the heat exchangers 31, 32, 33, 34. By the individual control, the capacity of the heat exchangers 31, 32, 33, 34 and the performance of the air conditioner 1 as a whole can be adjusted according to the load conditions.

The passage of the change in the state of air will be described. The air OA in the flow path 71 decreases in temperature and increases in relative humidity in the heat exchanger 31. Next, when passing through the dehumidifying rotor 2, moisture is adsorbed by an adsorbent (not shown) provided in the dehumidifying rotor 2, and the amount of moisture in the air OA decreases. At this time, an exothermic reaction is caused by the moisture absorption of the adsorbent, and the temperature rises. Finally, after the temperature is reduced again in the heat exchanger 32 provided on the downstream side of the dehumidifying rotor 2, air is supplied as air SA into the room.

At the same time, the temperature of the air RA in the flow path 72 increases in the heat exchanger 33 and the relative humidity decreases. Next, when passing through the dehumidifying rotor 2, moisture is released from an adsorbent (not shown) provided in the dehumidifying rotor 2, and the amount of moisture in the air RA increases. The process is a regeneration of the desiccant rotor 2. At this time, the endothermic reaction is caused by the moisture releasing action of the adsorbent, and the temperature is lowered. Finally, the temperature is again raised by the heat exchanger 34 provided on the downstream side of the dehumidifying rotor 2, and then discharged to the outside as air EA.

Fig. 13 is a diagram illustrating the flow of refrigerant in the humidification mode. The humidification mode is performed in winter, for example, and is a mode in which air OA is humidified and supplied to the room. In contrast to the dehumidification mode described above, the humidification mode moves moisture from the air RA in the flow path 72 to the air OA in the flow path 71. The operation of the refrigerant circuit is reverse to the dehumidification mode, and therefore, the description thereof is omitted.

Fig. 14 is a diagram illustrating the flow of refrigerant in the cooling mode. The cooling mode is performed in, for example, early summer of drying, and is a mode in which high-temperature air OA is cooled and then supplied to the room. As a use scenario of the cooling mode, a condition of "outdoor air OA is high in temperature, cooling is required, but dehumidification is not required" is assumed. Therefore, the rotation of the dehumidifying rotor 2 is stopped, and the dehumidifying rotor 2 is indicated by a two-dot chain line. In the cooling mode, the condensation dehumidification by the heat exchangers 31 and 32 functioning as evaporators in the flow path 71 is performed only for the purpose of reducing the temperature of the air OA. The operation of the refrigerant circuit is only required to refer to the dehumidification mode, and therefore, the description thereof will be omitted.

Fig. 15 is a diagram illustrating the flow of refrigerant in the heating mode. The heating mode is, for example, a mode in which the air OA at a low temperature is heated and supplied to the room after the humidity is high to some extent in early autumn. As a use scenario of the heating mode, a condition of "the outside air temperature is low, heating is required, but humidification processing is not required" is assumed. Therefore, the rotation of the dehumidifying rotor 2 is stopped, and the dehumidifying rotor 2 is indicated by a two-dot chain line. In the heating mode, the purpose is only to raise the temperature of the air in the flow path 71. The operation of the refrigerant circuit is only required to refer to the humidification mode, and therefore, the description thereof will be omitted.

Fig. 16 is a diagram illustrating the flow of refrigerant in the normal ventilation mode. The normal ventilation mode is a mode in which the indoor air RA is discharged to the outside and the outdoor air OA is supplied to the inside without requiring dehumidification, humidification, cooling, and heating. In the normal ventilation mode, the rotation of the dehumidifying rotor 2 is stopped, and the refrigerant circuit is also stopped. Therefore, the flow of the refrigerant to the heat exchangers 31, 32, 33, and 34 and the rotation of the desiccant rotor 2 are stopped, and the heat exchangers 31, 32, 33, and 34 and the desiccant rotor 2 are indicated by two-dot chain lines. The air-exchanging system can be used for cleaning in the middle period and night of low load as a use scene of a common air-exchanging mode.

In the example shown in fig. 16, the total heat exchange element 10 is further provided, and thus the total heat exchange mode can be used.

According to the air conditioner 1 of the present disclosure, by providing the expansion valves 41, 42, 43, 44 for each of the heat exchangers 31, 32, 33, 34, the refrigerant flow rate can be adjusted for each of the heat exchangers 31, 32, 33, 34. This can improve the efficiency of the refrigeration cycle, and can achieve excellent operation efficiency. Further, the pretreatment and post-treatment effects of the air OA and RA contacting the desiccant rotor 2 can be finely controlled, and the capacity of the desiccant rotor 2 and the ratio adjustment of sensible heat and latent heat of the air conditioner 1 can be performed with high accuracy.

Fig. 17 is a block diagram of an air conditioning system 100 of the present disclosure. In the air conditioners 1 and 50, the flow direction of the refrigerant is determined according to which of the heat exchangers 31, 32, 33, and 34, the outdoor heat exchanger 52, and the indoor heat exchanger 54 functions as an evaporator or a condenser. Therefore, the direction of the flow of the refrigerant indicated by the solid arrows in fig. 17 is merely an example, and is not limited to the direction shown in the drawing.

The air conditioning system 100 includes an air conditioner 1 (first air conditioner) and an air conditioner 50 (second air conditioner). The air conditioner 1 is an air conditioner 1 for conditioning air in a room, and is described with reference to fig. 1. The remote controller 94 and the sensor 95 are connected to the control device 9 constituting the air conditioner 1 through an electric signal line 121. In the illustrated example, the sensor 95 is incorporated in a remote control 94 constituting the air conditioner 1. Instead of the electric signal line 121, the control device 9 may be connected to the remote control 94 and the sensor 95 by wireless. The remote controller 94 receives at least an operation instructing the operation of the air conditioner 1. The sensor 95 is incorporated in the air conditioner 1, and measures at least one (in the example of the present disclosure, both) of the temperature and the humidity in the room where the air SA is supplied.

The air conditioner 50 is configured to air-condition the same indoor space as the air conditioner 1, separately from the air conditioner 1, and operates in cooperation with the air conditioner 1. The air conditioner 50 includes a compressor 51 (second compressor), an outdoor heat exchanger 52, an expansion mechanism 53 (expansion valve, etc.), and an indoor heat exchanger 54. The compressor 51, the outdoor heat exchanger 52, the expansion mechanism 53, and the indoor heat exchanger 54 constitute a refrigeration cycle. The indoor heat exchanger 54 is disposed indoors, and cold air or warm air is supplied to the indoor by using the refrigerant compressed by the compressor 51.

The air conditioner 50 includes a control device 55 that controls the operation of the air conditioner 50. The specific hardware configuration of the control device 55 is the same as that of the control device 9, and therefore, the description thereof is omitted. In the control device 55, a remote controller 57 and a sensor 58 are provided via an electric signal line 56. In the illustrated example, the sensor 58 is incorporated in a remote controller 57 constituting the air conditioner 50. Instead of the electric signal line 56, the control device 55 may be connected to the remote controller 57 and the sensor 58 by wireless. The remote controller 57 receives at least an operation for instructing the operation of the air conditioner 50. The sensor 58 is incorporated in the air conditioner 50, and measures at least one (in the example of the present disclosure, both) of the temperature and the humidity in the room in which the air SA is supplied.

The control device 9 and the control device 55 are connected by an electrical signal line 120. Thus, the air conditioners 1 and 50 operate cooperatively. Instead of the electrical signal line 120, the control device 9 and the control device 55 may also be connected wirelessly. The remote control 94 provided in the air conditioner 1 may receive an operation instruction of the air conditioner 50. The remote controller 57 provided in the air conditioner 50 may receive an operation instruction of the air conditioner 1.

The operation of the air conditioners 1 and 50 is controlled based on the measured values of the temperature and the humidity of at least one (in the example of fig. 7) of the sensor 95 or the sensor 58. Thus, the air conditioners 1 and 50 can operate cooperatively based on the measured values from one of the sensors 95 and 58.

In the example of the present disclosure, the air conditioner 1 mainly deals with latent heat in a room. Specifically, the latent heat treatment is, for example, humidity adjustment in a room. The "main process latent heat" is mainly the humidity adjustment in the room as a function of the air conditioner 1, and if there is a margin in the capacity of the air conditioner 1 when the humidity adjustment is performed, the temperature adjustment (sensible heat process) in the room is also performed.

The air conditioner 50 mainly processes sensible heat in a room. Specifically, the sensible heat treatment is, for example, indoor temperature adjustment. The "main process sensible heat" is a function of the air conditioner 50, mainly, temperature adjustment in the room, and if there is a margin in the capacity of the air conditioner 50 when temperature adjustment is performed, humidity adjustment (latent heat process) in the room is also performed.

The indoor latent heat process and the indoor sensible heat process are performed in parallel by the air conditioners 1 and 50. Accordingly, the latent heat and the sensible heat can be handled independently by the respective air conditioners 1 and 50, and thus the followability to the set temperature and the set humidity can be improved.

In another embodiment, when the sensible heat process of the air conditioner 1 is insufficient while the flow of the refrigerant to the indoor heat exchanger 54 is stopped in the air conditioner 50, the sensible heat process of the air conditioner 50 is performed. The sensible heat process varies according to the actual conditions such as the load conditions and the user demands. Therefore, when both latent heat and sensible heat can be handled by only the air conditioner 1, only the air conditioner 1 is operated, and the flow of the refrigerant to the indoor heat exchanger 54 is stopped (for example, the operation of the air conditioner 50 is stopped). On the other hand, when the sensible heat treatment of the air conditioner 1 is insufficient, the air conditioner 50 is used in combination. This can reduce the operation cost as compared with the case where both the air conditioners 1 and 50 are operated at all times.

By controlling the air conditioning system 100 in this manner, various operation methods can be realized. For example, under low load conditions, there are a single operation control in which the full load is handled only by the air conditioner 1 in a well-balanced manner, a construction of an energy saving system in which the air conditioner 50 is made to be dedicated to full sensible heat by providing the full latent heat load handling by the air conditioner 1, and the like. In addition, even in the dehumidification mode which aims at the humidity control amount, the water-free humidification in winter can be performed, and high comfort, convenience in installation and maintainability can be realized.

Fig. 18 is a block diagram of an air conditioning system 100 according to another embodiment. In the example shown in fig. 18, the air conditioning system 100 is the same as the air conditioning system 100 shown in fig. 17, except that the air conditioning system 100 includes a sensor 110 that is disposed separately from each of the air conditioner 1 and the air conditioner 50.

In the example shown in fig. 18, the operation of the air conditioners 1 and 50 is controlled based on the measured values of the temperature and the humidity of at least one (in the example of fig. 18) of the sensors 95, 58, or 110. In particular, by using the measurement value of the sensor 110 disposed separately from the air conditioners 1 and 50, the variation in the indoor temperature and humidity can be suppressed.

The sensor 110 is connected to at least one of the control devices 9 and 55 (in the illustrated example, the control device 9) via an electric signal line 122. Instead of the electrical signal line 122, the sensor 110 may also be connected to the control device 9, 55 by wireless.

Claims

1. An air conditioner is characterized in that,

the air conditioner is provided with:

a rotary adsorption/release mechanism configured to adsorb moisture of air flowing through one of a first flow path and a second flow path for supplying air from outside to inside and discharging air from inside to outside, and release the moisture to air flowing through the other flow path;

A first heat exchanger provided in the first flow path and disposed on an upstream side of the air flow of the adsorption/release mechanism;

a second heat exchanger provided in the first flow path and arranged in parallel with the first heat exchanger in the refrigerant flow, and disposed on the downstream side of the adsorption/release mechanism from the air flow;

a third heat exchanger provided in the second flow path and disposed on an upstream side of the adsorption/release mechanism with respect to an air flow;

a fourth heat exchanger provided in the second flow path and arranged in parallel with the third heat exchanger in the refrigerant flow, and disposed on the downstream side of the adsorption/release mechanism from the air flow;

a first flow rate control mechanism that controls a flow rate of the refrigerant to the first heat exchanger;

a second flow rate control mechanism configured separately from the first flow rate control mechanism and configured to control a flow rate of the refrigerant to the second heat exchanger;

a third flow rate control mechanism that controls a flow rate of the refrigerant to the third heat exchanger;

a fourth flow rate control means configured separately from the third flow rate control means for controlling the flow rate of the refrigerant to the fourth heat exchanger; and

A compressor for compressing the refrigerant supplied to the first heat exchanger, the second heat exchanger, the third heat exchanger, and the fourth heat exchanger,

the first flow control mechanism, the second flow control mechanism, the third flow control mechanism, and the fourth flow control mechanism are each constituted by an expansion mechanism.

2. The air conditioner according to claim 1, wherein,

the air conditioner has a first operation mode in which at least one of the flow rates of the refrigerant to the first heat exchanger and the third heat exchanger and the flow rates of the refrigerant to the second heat exchanger and the fourth heat exchanger are increased or decreased in comparison with a steady state in which differences between the indoor temperature and the indoor humidity and the set temperature and the set humidity are within a predetermined range.

3. The air conditioner according to claim 1, wherein,

the air conditioner has a second operation mode in which at least one of the flow rates of the refrigerant to the first heat exchanger and the third heat exchanger and the flow rates of the refrigerant to the second heat exchanger and the fourth heat exchanger are reduced or increased in comparison with a steady state in which differences between the indoor temperature and the indoor humidity and the set temperature and the set humidity are within a predetermined range.

4. The air conditioner according to claim 1, wherein,

and a total heat exchange mechanism for performing total heat exchange between the air from the outside and the air from the inside is provided on the upstream side of each of the first heat exchanger and the third heat exchanger.

5. The air conditioner according to claim 4, wherein,

the air conditioner is provided with:

a third flow path that supplies air from the outside to the total heat exchange mechanism;

a fourth flow path for supplying air from the outside to the first heat exchanger while bypassing the total heat exchange mechanism; and

and a first switching mechanism that switches a flow path of air from the outside to the third flow path or the fourth flow path.

6. The air conditioner according to claim 1, wherein,

the air conditioner includes a second switching mechanism for controlling a flow direction of a refrigerant in a refrigeration cycle.

7. The air conditioner according to claim 1, wherein,

the flow direction of the refrigerant in the refrigeration cycle is fixed.

8. An air conditioner is characterized in that,

the air conditioner is provided with:

the air conditioner can switch the first operation mode, the second operation mode and the third operation mode,

the first operation mode is one in which the flow rate of refrigerant to at least one of the first heat exchanger and the third heat exchanger is greater than the flow rate of refrigerant to at least one of the second heat exchanger and the fourth heat exchanger,

the second operation mode is one in which the flow rate of the refrigerant to at least one of the second heat exchanger and the fourth heat exchanger is greater than the flow rate of the refrigerant to at least one of the first heat exchanger and the third heat exchanger,

the third operation mode equalizes the flow rate of refrigerant to the first heat exchanger and the third heat exchanger with the flow rate of refrigerant to the second heat exchanger and the fourth heat exchanger.

9. An air conditioning system, characterized in that,

the air conditioning system is provided with:

a first air conditioner that conditions air in a room; and

a second air conditioner which is configured separately from the first air conditioner and operates in cooperation with the first air conditioner, and which is provided with a second compressor, an outdoor heat exchanger, an expansion mechanism, and an indoor heat exchanger,

The first air conditioner is provided with:

10. An air conditioning system according to claim 9, wherein,

the operation of the first air conditioner and the second air conditioner is controlled based on measured values of temperature and humidity of at least one of a sensor built in the first air conditioner, a sensor built in the second air conditioner, or a sensor disposed separately from the first air conditioner and the second air conditioner.