All fresh air type two-stage rotating wheel dehumidification air conditioning unit

Abstract

The invention discloses a full fresh air type two-stage rotating wheel dehumidification air conditioning unit, and relates to the technical field of air conditioners. Wherein the first dehumidification rotating wheel is configured to be a low-temperature regeneration rotating wheel, and the first dehumidification rotating wheel is provided with a first dehumidification channel and a first regeneration channel; the second dehumidification rotating wheel is provided with a second dehumidification channel and a second regeneration channel; the fresh air channel, the first dehumidification channel, the second dehumidification channel and the air supply channel are sequentially communicated through a pipeline; the air return channel, the second regeneration channel, the first regeneration channel and the air exhaust channel are sequentially communicated through pipelines. The electric heater and a condenser of the heat pump system are arranged on a pipeline between the air return channel and the second regeneration channel, and the electric heater is located between the condenser and the second regeneration channel. The inlet end of the bypass channel is connected to the pipeline between the condenser and the electric heater, and the outlet end of the bypass channel is connected to the pipeline between the first regeneration channel and the second regeneration channel. Deep dehumidification of fresh air can be achieved, the energy recycling rate is high, and operation energy consumption is low.

Description

Technical Field

[0001] The invention relates to the technical field of air conditioning, and in particular to a fresh air type two-stage rotary dehumidification air conditioning unit. Background Art

[0002] Since the rotary dehumidification technology has the advantages of large dehumidification capacity, strong dehumidification ability and low environmental pollution, the rotary dehumidification technology is gradually being widely used to provide excellent dehumidification effect. For some occasions with deep dehumidification requirements, a two-stage rotary dehumidification system is usually required to achieve the purpose of deep dehumidification by performing secondary dehumidification treatment on the air.

[0003] At present, in the two-stage rotary dehumidification air-conditioning unit of the fresh air type, the regeneration temperature of each dehumidification rotary wheel is high, and an electric heater needs to be configured for each dehumidification rotary wheel to provide high-temperature regeneration air so that the dehumidification rotary wheel can restore its strong dehumidification capacity, which will result in a large amount of electric energy consumption during operation; at the same time, outdoor fresh air is used as the regeneration air to regenerate the dehumidification rotary wheel. Due to the high moisture content of the outdoor fresh air, the regeneration effect on the dehumidification rotary wheel is poor, and therefore the outdoor fresh air needs to be converted into high-temperature dry air, which will cause a further increase in electric energy consumption and an increase in operating costs. In addition, the energy recovery rate of the two-stage rotary dehumidification air-conditioning unit of the fresh air type is low, which does not conform to the current energy-saving and environmental protection concept.

[0004] Therefore, the existing fresh air type two-stage rotary dehumidification air-conditioning unit needs to be further optimized. Summary of the invention

[0005] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a two-stage rotary dehumidification air conditioning unit of a fresh air type, which can achieve the purpose of deep dehumidification of fresh air, and has high energy recovery rate and low operating energy consumption.

[0006] The embodiment of the present invention provides a two-stage rotary dehumidification air conditioning unit of a fresh air type, which comprises:

[0007] a first dehumidification rotor configured as a low-temperature regeneration rotor, the first dehumidification rotor having a first dehumidification channel and a first regeneration channel;

[0008] a second dehumidification wheel having a second dehumidification channel and a second regeneration channel;

[0009] Fresh air channel;

[0010] An air supply channel, wherein the fresh air channel, the first dehumidification channel, the second dehumidification channel and the air supply channel are sequentially connected through a pipeline;

[0011] Return air duct;

[0012] an exhaust passage, wherein the return air passage, the second regeneration passage, the first regeneration passage and the exhaust passage are sequentially connected through a pipeline;

[0013] A heat pump system comprising a condenser;

[0014] an electric heater, which and the condenser are arranged on the pipeline between the return air channel and the second regeneration channel, and the electric heater is located between the condenser and the second regeneration channel;

[0015] The bypass channel has an inlet end connected to the pipeline between the condenser and the electric heater, and an outlet end of the bypass channel connected to the pipeline between the first regeneration channel and the second regeneration channel.

[0016] The two-stage rotary dehumidification air-conditioning unit of the fresh air type according to the embodiment of the present invention has at least the following beneficial effects: the outdoor fresh air can complete the two-stage dehumidification treatment under the joint operation of the first dehumidification rotary wheel and the second dehumidification rotary wheel, and become dry air that meets the deep dehumidification requirements of the indoor space, thereby realizing the fresh air ventilation function; the low-humidity indoor air is used as the regeneration air, which becomes high-temperature and low-humidity air with strong regeneration ability after heating treatment, which can reduce the dehumidification energy consumption of the regeneration air.

[0017] Moreover, by effectively utilizing the heat carried by the condenser in the heat pump system, the regeneration air flowing into the second regeneration channel and part of the regeneration air flowing into the first regeneration channel are preheated, so that the air energy can be fully utilized, the energy recovery rate can be improved, and the energy consumption of the electric heater can be effectively reduced; at the same time, the regeneration air flowing out of the bypass channel is mixed with the regeneration air flowing out of the second regeneration channel before entering the first regeneration channel to increase the flow rate and temperature of the regeneration air flowing into the first regeneration channel. By effectively utilizing the flow rate and heat of the regeneration air flowing out of the second regeneration channel, the temperature and flow rate requirements of the regeneration air of the first dehumidification wheel with a low regeneration temperature can be achieved. There is no need to perform secondary heating on the regeneration air flowing into the first regeneration channel, which can save the electric heating energy consumption required for the first dehumidification wheel, thereby greatly reducing the operating energy consumption.

[0018] In some embodiments of the present invention, the air flow rate of the bypass passage is greater than the air flow rate of the second regeneration passage.

[0019] In some embodiments of the present invention, the air flow rate of the first regeneration channel is 65% to 85% of the air flow rate of the fresh air channel, and the air flow rate of the second regeneration channel is 30% to 35% of the air flow rate of the fresh air channel.

[0020] In some embodiments of the present invention, the bypass channel is provided with a first flow control valve, and one side of the second regeneration channel is provided with a second flow control valve.

[0021] In some embodiments of the present invention, the heat pump system further includes an evaporator, and the evaporator is disposed on a pipeline between the first dehumidification channel and the second dehumidification channel.

[0022] In some embodiments of the present invention, the two-stage rotary dehumidification air-conditioning unit of the fresh air type also includes a second precooler, which is arranged on the pipeline between the first dehumidification channel and the second dehumidification channel, and the second precooler is located between the first dehumidification channel and the evaporator.

[0023] In some embodiments of the present invention, the second precooler has a second cold flow channel for connecting to a centralized cold source.

[0024] In some embodiments of the present invention, the fresh air type two-stage rotary dehumidification air-conditioning unit further includes a first precooler, which is arranged on the pipeline between the fresh air channel and the first dehumidification channel.

[0025] In some embodiments of the present invention, the first precooler has a first cold flow channel for connecting to a centralized cold source.

[0026] In some embodiments of the present invention, the two-stage rotary dehumidification air-conditioning unit of the fresh air type further includes a cooler and a warmer, and the cooler and the warmer are arranged on the pipeline between the second dehumidification channel and the air supply channel.

[0027] Other features and advantages of the present invention will be described in the following description, and partly become apparent from the description, or understood by practicing the present invention. The purpose and other advantages of the present invention can be realized and obtained by the structures particularly pointed out in the description, claims and drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Figure 1 2 is a schematic structural diagram of a fresh air type two-stage rotary dehumidification air conditioning unit provided according to an embodiment of the present invention;

[0029] Figure 2 It is a structural schematic diagram of a fresh air type two-stage rotary dehumidification air conditioning unit provided according to another embodiment of the present invention.

[0030] Figure numerals: 111, first air filter; 112, first precooler; 113, first dehumidification wheel; 114, first fan; 115, second air filter; 116, evaporator; 117, second dehumidification wheel; 118, cooler; 119, heater; 120, third air filter; 121, compressor; 122, condenser; 123, electric heater; 124, second fan; 125, bypass channel; 126, high-temperature air channel; 127, third fan; 128, second precooler. DETAILED DESCRIPTION

[0031] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0032] In the description of the present invention, it is to be understood that a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

[0033] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "connected" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0034] Reference below Figure 1 to Figure 2 A fresh air type two-stage rotary dehumidification air conditioning unit provided according to an embodiment of the present invention is described.

[0035] like Figure 1 As shown, the two-stage rotary dehumidification air conditioning unit of the fresh air type according to the embodiment of the present invention can achieve the purpose of deep dehumidification of fresh air, and it has the advantages of unique design, practicality and reliability, high energy recovery rate, low operating energy consumption, etc. The two-stage rotary dehumidification air conditioning unit of the fresh air type provided in this embodiment can be applied to some occasions with deep dehumidification requirements.

[0036] The two-stage rotary dehumidification air conditioning unit of the fresh air type includes a two-stage rotary dehumidification system, an air duct system, a heat pump system, an electric heater 123 and a thermostat.

[0037] The two-stage rotary dehumidification system includes a first dehumidification rotary wheel 113 and a second dehumidification rotary wheel 117, wherein the first dehumidification rotary wheel 113 is configured as a low-temperature regeneration rotary wheel, and the first dehumidification rotary wheel 113 has a first dehumidification channel and a first regeneration channel. The second dehumidification rotary wheel 117 is configured as a high-temperature regeneration rotary wheel, and the second dehumidification rotary wheel 117 has a second dehumidification channel and a second regeneration channel.

[0038] It can be understood that in the first dehumidification wheel 113, the first dehumidification channel and the first regeneration channel are arranged separately and are not connected to each other. The first dehumidification channel can dehumidify the fresh air flowing through it to achieve the dehumidification function of the first dehumidification wheel 113, and the first regeneration channel can absorb the heat carried by the regeneration wind flowing through it to achieve the desorption regeneration function of the first dehumidification wheel 113. Similarly, in the second dehumidification wheel 117, the second dehumidification channel and the second regeneration channel are also arranged separately. The second dehumidification channel is used to dehumidify the fresh air, and the second regeneration channel is used to absorb the heat of the regeneration wind to complete the regeneration work of the second dehumidification wheel 117.

[0039] The first dehumidification wheel 113 and the second dehumidification wheel 117 are both driven by a driving motor and a transmission structure such as a belt transmission structure to realize rotational drive, so that the adsorption saturated part of the first dehumidification wheel 113 and the second dehumidification wheel 117 can be rotated to the regeneration side to perform desorption regeneration work and restore the original dehumidification capacity, and the desorption regeneration part of the first dehumidification wheel 113 and the second dehumidification wheel 117 can be rotated to the dehumidification side to perform dehumidification work. The two-stage wheel dehumidification system realizes two-stage dehumidification treatment of fresh air through the cooperation of the first dehumidification wheel 113 and the second dehumidification wheel 117, thereby reducing the humidity of the fresh air to meet the requirements of deep dehumidification.

[0040] The heat pump system includes a compressor 121, a condenser 122, a throttling device and an evaporator 116. The compressor 121, the condenser 122, the throttling device and the evaporator 116 are connected in a closed loop in sequence through pipelines to form a refrigerant circulation loop. It is understood that the throttling device can be a throttle valve or a capillary tube. The heat pump system is a direct expansion heat pump. The condenser 122 and the evaporator 116 can use a finned heat exchanger.

[0041] The air duct system includes a fresh air channel, an air supply channel, a return air channel, a bypass channel 125 and an exhaust air channel. The fresh air channel, the first dehumidification channel, the second dehumidification channel and the air supply channel are connected in sequence through pipelines to form a fresh air channel; the return air channel, the second regeneration channel, the first regeneration channel and the exhaust air channel are connected in sequence through pipelines to form a regeneration air channel.

[0042] It is understandable that the fresh air duct can be connected to the outdoor space through a pipeline so that fresh air from the outdoor can enter the fresh air duct. The air supply duct can be connected to the indoor space through a pipeline so that fresh air after deep dehumidification can enter the indoor space. The return air duct can be connected to the indoor space through a pipeline so that dirty air in the room can flow into the return air duct. The exhaust duct can be connected to the outdoor space through a pipeline so that indoor air can be discharged to the outdoor environment.

[0043] The electric heater 123 and the condenser 122 are both arranged on the pipeline between the return air channel and the second regeneration channel, so the air between the return air channel and the second regeneration channel can absorb the heat released by the electric heater 123 and the condenser 122. The electric heater 123 and the condenser 122 are arranged between the condenser 122 and the second regeneration channel.

[0044] It can be understood that the condenser 122 and the electric heater 123 are both located in the regeneration air channel and can heat and increase the temperature of the regeneration air. The condenser 122 and the electric heater 123 are arranged in sequence along the flow direction of the regeneration air. The regeneration air is preheated by the condenser 122 to increase the temperature of the regeneration air, and the regeneration air is reheated by the electric heater 123 to further increase the temperature of the regeneration air.

[0045] The inlet end of the bypass channel 125 is connected to the pipeline between the condenser 122 and the electric heater 123 , and the outlet end of the bypass channel 125 is connected to the pipeline between the first regeneration channel and the second regeneration channel.

[0046] It is understood that the electric heater 123 and the second regeneration channel are connected through a pipeline to form a high-temperature air channel 126, and the high-temperature air channel 126 is connected in parallel with the bypass channel 125. The return air (i.e., the dirty air in the room) flowing into the return air channel is used as the regeneration air, and after being preheated by the condenser 122, it will be split, wherein a part of the return air will flow into the high-temperature air channel 126, and the temperature will be greatly increased after the heating treatment of the electric heater 123, so as to heat and regenerate the second dehumidification rotor 117 for high-temperature regeneration, and the other part of the return air will flow into the bypass channel 125, and mix with the regeneration air flowing out of the high-temperature air channel 126, so as to form a mixed regeneration air. The temperature of the regeneration air flowing out of the high-temperature air channel 126 is higher than that of the regeneration air flowing out of the bypass channel 125. Therefore, after the mixing treatment, the regeneration air flowing into the first regeneration channel can achieve a temperature increase and a flow increase to meet the temperature and flow requirements of the first dehumidification rotor 113 for low-temperature regeneration.

[0047] The thermostat is arranged on the pipeline between the second dehumidification channel and the air supply channel, and can adjust the temperature of the fresh air that has completed the secondary dehumidification so that the temperature of the fresh air meets the air supply temperature requirement of the indoor space. Specifically, the thermostat includes a cooler 118 and a heater 119. The cooler 118 and the heater 119 are both arranged on the pipeline between the second dehumidification channel and the air supply channel, and the cooler 118 and the heater 119 are arranged in sequence along the flow direction of the fresh air, that is, the cooler 118 is installed between the second dehumidification channel and the heater 119.

[0048] It is understandable that the cooler 118 can cool the fresh air to reduce the temperature of the fresh air to a set temperature. The warmer 119 can heat the fresh air to increase the temperature of the fresh air to a set temperature. The cooler 118 and the warmer 119 can be coil-type heat exchangers, and cooling water flows in the cold flow channel of the cooler 118, and hot water flows in the hot flow channel of the warmer 119. In this embodiment, the cold flow channel of the cooler 118 is externally connected to a centralized cold source, and the centralized cold source can be medium-temperature chilled water with a supply / return water temperature of 7°C / 12°C. Of course, it is not excluded that in other embodiments, the warmer 119 is located between the second dehumidification channel and the cooler 118. The warmer 119 is an electric heating device.

[0049] The fresh air from outside undergoes secondary dehumidification treatment as it flows through the fresh air channel, the first dehumidification channel and the second dehumidification channel in sequence, becoming dry air that meets the requirements of deep dehumidification. Then, the dry air flows to the indoor space through the air supply channel, thereby providing fresh air ventilation to the indoor space.

[0050] At the same time, the indoor air flowing in from the return air channel will increase its temperature after absorbing the heat released by the condenser 122. Then, a part of the heated air will flow to the second regeneration channel and will significantly increase its temperature after absorbing the heat energy of the electric heater 123 to meet the high inlet air temperature requirement of the second regeneration channel, thereby enabling the desorption and regeneration of the second dehumidification wheel 117. The other part will be mixed and heat-exchanged with the air flowing out of the second regeneration channel to form mixed regeneration wind. At this time, since the first dehumidification wheel 113 is a low-temperature regeneration wheel with a low regeneration temperature, the temperature and flow rate of the mixed regeneration wind meet the inlet air temperature and inlet air flow rate requirements of the first regeneration channel. Subsequently, the mixed regeneration wind flows into the first regeneration channel to desorb and regenerate the first dehumidification wheel 113, and is finally discharged to the outdoors through the exhaust channel.

[0051] In some embodiments, the air flow of the bypass channel 125 is greater than the air flow of the second regeneration channel. Specifically, the air flow of the first regeneration channel is 65% to 85% of the air flow of the fresh air channel, and the air flow of the second regeneration channel is 30% to 35% of the air flow of the fresh air channel.

[0052] In this embodiment, the air flow rate of the first regeneration channel (that is, the regeneration air flow rate of the first dehumidification wheel 113) is 70% of the air flow rate of the fresh air channel (that is, the fresh air flow rate, the dehumidification treatment flow rate), and the air flow rate of the second regeneration channel (that is, the regeneration air flow rate of the second dehumidification wheel 117) is 33% of the air flow rate of the fresh air channel.

[0053] It is understandable that, since the first dehumidification wheel 113 is a low-temperature regeneration wheel and the second dehumidification wheel 117 is a high-temperature regeneration wheel, the regeneration air flow rate of the first dehumidification wheel 113 is relatively large, and the regeneration air flow rate of the second dehumidification wheel 117 is relatively small, and the ratio between the regeneration air flow rate of the first dehumidification wheel 113 and the regeneration air flow rate of the second dehumidification wheel 117 is approximately 2:1. Moreover, the flow rate of the regeneration air preheated by the condenser 122 can meet the regeneration air flow rate requirement of the first dehumidification wheel 113, but the temperature of the regeneration air preheated by the condenser 122 does not meet the regeneration air temperature requirement of the second dehumidification wheel 117, and therefore, the regeneration air to be flowed into the second regeneration channel needs to be subjected to secondary heating treatment by the electric heater 123 to meet the heating regeneration condition of the second dehumidification wheel 117.

[0054] The flow rate of the regeneration air flowing out of the second regeneration channel does not meet the regeneration air flow rate requirement of the first dehumidification rotor 113, so the regeneration air flowing out of the bypass channel 125 is mixed with the regeneration air flowing out of the second regeneration channel to form a mixed regeneration air, the flow rate of the mixed regeneration air is equal to the return air flow rate flowing into the return air channel, and can meet the air intake flow rate requirement of the first regeneration channel. Moreover, the regeneration air flowing out of the second regeneration channel still has a certain amount of heat, and its temperature is higher than the temperature of the regeneration air flowing out of the bypass channel 125. By effectively utilizing the waste heat of the regeneration air of the second dehumidification rotor 117, the temperature of the mixed regeneration air is increased to meet the air intake temperature requirement of the first regeneration channel, and the energy recovery rate is improved.

[0055] If the return air flow rate is increased to the sum of the regeneration air flow rate of the first dehumidification rotor 113 and the regeneration air flow rate of the second dehumidification rotor 117, the heat required to be released by the condenser 122 will increase, resulting in an increase in the energy consumption of the heat pump system. If the bypass channel 125 is not provided, and the return air is directly sent to the second regeneration channel and the first regeneration channel in sequence, the regeneration air flow rate that the electric heater 123 needs to handle will increase, resulting in an increase in the power consumption of the electric heater 123.

[0056] Compared with the two methods mentioned above, the embodiment of the present invention uses the ingenious design and mutual cooperation of the low-temperature regeneration wheel, the condenser 122 of the heat pump system, the electric heater 123, the bypass channel 125 and the high-temperature air channel 126 to enable the heat dissipation of the condenser 122 to be used for the preheating of the regeneration air, so as to increase the temperature of the regeneration air, thereby reducing the energy consumption of the electric heater 123, and the preheated regeneration air is diverted to reduce the regeneration air processing volume of the electric heater 123, further reducing the energy consumption of the electric heater 123, and at the same time, The flow rate and waste heat of the regeneration air of the second dehumidification wheel 117 are effectively utilized to promote the mixing of the regeneration air flowing out of the second regeneration channel and the regeneration air flowing out of the bypass channel 125, so that the flow rate and temperature of the mixed regeneration air can reach the inlet air flow rate and inlet air temperature required by the first dehumidification wheel 113. This can effectively reduce the return air flow rate and make the return air flow rate equal to the regeneration air flow rate of the first dehumidification wheel 113, thereby reducing the power consumption of the heat pump system and improving the recovery rate of energy (air energy and the waste heat of the regeneration air of the second dehumidification wheel 117).

[0057] In some embodiments, the bypass channel 125 is provided with a first flow control valve, which can control the flow of the regeneration air flowing from the return air channel into the bypass channel 125. A second flow control valve is provided on one side of the second regeneration channel. It can be understood that the second flow control valve is provided on the high-temperature air channel 126, and can control the flow of the regeneration air flowing from the return air channel into the high-temperature air channel 126. The second flow control valve can be provided on the inlet side or the outlet side of the second regeneration channel.

[0058] In this embodiment, the first flow control valve on the bypass channel 125 is disposed near the inlet end of the bypass channel 125, and the second flow control valve on the high-temperature air channel 126 is disposed near the inlet end of the high-temperature air channel 126. In addition, a third flow control valve may be disposed on the fresh air channel, and a fourth flow control valve may be disposed on the return air channel.

[0059] Of course, it is not excluded that in other embodiments, by designing the duct diameter sizes of the bypass channel 125 and the high-temperature air channel 126, the ratio between the regeneration air flow rate of the bypass channel 125 and the regeneration air flow rate of the high-temperature air channel 126 meets the set conditions, so that the ratio between the regeneration air flow rate of the first dehumidification wheel 113 and the regeneration air flow rate of the second dehumidification wheel 117 is approximately 2:1.

[0060] In some embodiments, Figure 1As shown, the evaporator 116 in the heat pump system is arranged on the pipeline between the first dehumidification channel and the second dehumidification channel. The evaporator 116 can pre-cool the fresh air flowing from the first dehumidification channel into the second dehumidification channel, thereby reducing the inlet air temperature of the second dehumidification channel and improving the dehumidification capacity of the second dehumidification wheel 117.

[0061] In some embodiments, Figure 1 As shown, the fresh air type two-stage rotary dehumidification air conditioning unit also includes a first precooler 112. Among them, the first precooler 112 is arranged on the pipeline between the fresh air channel and the first dehumidification channel. The first precooler 112 can precool the fresh air flowing from the fresh air channel to the first dehumidification channel, so that the temperature of the fresh air can be reduced, thereby reducing the inlet air temperature of the first dehumidification channel, which helps to improve the dehumidification capacity of the first dehumidification rotary wheel 113. The first precooler 112 can be but not limited to a coil heat exchanger. In this embodiment, the first precooler 112 has a first cold flow channel, and the first cold flow channel can be used to connect to a centralized cold source.

[0062] In some embodiments, Figure 2 As shown, the two-stage rotary dehumidification air conditioning unit of the fresh air type also includes a second precooler 128. The second precooler 128 is arranged on the pipeline between the first dehumidification channel and the second dehumidification channel, and the second precooler 128 is located between the first dehumidification channel and the evaporator 116. The second precooler 128 can apply a primary precooling effect to the fresh air that will flow into the second dehumidification channel, and then the evaporator 116 applies a secondary precooling effect to the fresh air after the primary precooling, which greatly reduces the temperature of the fresh air, thereby making the inlet air temperature of the second dehumidification channel lower, and further improving the dehumidification capacity of the second dehumidification rotary wheel 117. In this embodiment, the second precooler 128 has a second cold flow channel, and the second cold flow channel can be used to connect to a centralized cold source.

[0063] The two-stage rotary dehumidification air conditioning unit of the fresh air type also includes at least two fans. Through the operation of the fans, the outdoor fresh air can flow from the fresh air channel to the air supply channel, and the indoor dirty air can flow from the return air channel to the exhaust channel. The setting position of the fan can be set according to actual needs.

[0064] In this embodiment, if Figure 1 As shown, a first fan 114 is provided on the pipeline between the first dehumidification channel and the second dehumidification channel, and the first fan 114 can be located between the first precooler 112 and the first dehumidification channel. A second fan 124 is provided on the high-temperature air channel 126, and the second fan 124 is provided near the outlet end of the second regeneration channel. A third fan 127 is provided on the exhaust channel.

[0065] The two-stage rotary dehumidification air conditioning unit of the fresh air type also includes at least three air filters. The air filters can remove impurities in the fresh air. Figure 1 As shown, a first air filter 111 is provided in the fresh air channel, and a first precooler 112 is located between the first air filter 111 and the first dehumidification channel. A second air filter 115 is provided on the pipeline between the first dehumidification channel and the second dehumidification channel, and the second air filter 115 is located between the first fan 114 and the evaporator 116. When a second precooler 128 is provided, the second air filter 115 is located between the first fan 114 and the second precooler 128. A third air filter 120 is provided in the air supply channel.

[0066] The following example assumes that the dry bulb temperature (DB) is 35.0°C and the flow rate (FR) is 21450m 3 / h and the absolute humidity (AH) of fresh air is 17.40g / kg as an example. Table 1 is a table showing the changes in air flow, dry bulb temperature and absolute humidity when the fresh air type two-stage rotary dehumidification air conditioning unit is running. Table 1 is shown in the following table:

[0067]

[0068] It is understandable that if Figure 1 As shown in Table 1, when the two-stage rotary dehumidification air conditioning unit of the fresh air type is started, the fresh air (i.e., the fresh air outside) will continuously flow into the fresh air channel when the first fan 114 is running. Figure 1 The fresh air flow rate at point 1 is 21450m 3 / h, dry bulb temperature is 35.0℃, and absolute humidity is 17.40g / kg.

[0069] Next, the fresh air will flow through the first air filter 111 and the first precooler 112 in sequence, so that the fresh air can complete the filtering and precooling processes, making the fresh air become low-temperature clean air. Figure 1 The fresh air flow at point 2 is 21450m 3 / h, dry bulb temperature is 13.0℃, and absolute humidity is 8.86g / kg.

[0070] Then, the pre-cooled fresh air flows into the first dehumidification channel of the first dehumidification wheel 113 to complete the primary dehumidification of the fresh air and reduce the humidity of the fresh air. Figure 1 The fresh air flow at point 3 is 21450m 3 / h, dry bulb temperature is 28.8℃, and absolute humidity is 3.50g / kg.

[0071] After that, the fresh air that has completed the dehumidification will flow through the second air filter 115 and the evaporator 116 in sequence, so that the fresh air can complete the filtering and pre-cooling process, making the fresh air become low-temperature and low-humidity clean air. Figure 1 The fresh air flow rate at point 4 is 21450m 3 / h, the dry bulb temperature is 12.0°C, and the absolute humidity is 3.50g / kg. When the second precooler 128 is provided, the fresh air will flow through the second air filter 115, the second precooler 128, and the evaporator 116 in sequence.

[0072] Then, the pre-cooled fresh air will flow into the second dehumidification channel of the second dehumidification wheel 117 to complete the secondary dehumidification of the fresh air, so that the humidity of the fresh air is further reduced, which can meet the deep dehumidification requirements of the indoor space. Figure 1 The fresh air flow at point 5 is 21450m 3 / h, dry bulb temperature is 27.0℃, and absolute humidity is 1.15g / kg.

[0073] Finally, the temperature of the fresh air is lowered when the cooler 118 is running to meet the low temperature requirement of the indoor space, and flows into the indoor space through the air supply channel, thereby realizing the fresh air ventilation function. At this time, the warmer 119 is in a non-working state. Figure 1 The fresh air flow rate at point 6 is 21450m 3 / h, dry bulb temperature is 12.0℃, and absolute humidity is 1.15g / kg.

[0074] At the same time, since the second fan 124 and the third fan 127 are operating, the return air (i.e., the dirty air in the room) will flow into the return air duct as the regeneration air. Figure 1 The fresh air flow at point 7 is 15000m 3 / h, dry bulb temperature is 17.0℃, and absolute humidity is 2.15g / kg.

[0075] Then, the return air is preheated after absorbing the condensation heat of the condenser 122, so that the temperature of the return air rises. Figure 1 The return air flow rate at point 8 is 15000m 3 / h, dry bulb temperature is 45.0℃, and absolute humidity is 2.15g / kg.

[0076] Then, the preheated return air will be split, with one part of the return air flowing to the high-temperature air channel 126 and the other part flowing to the bypass channel 125. The return air in the high-temperature air channel 126 will first absorb the heat released by the electric heater 123 to achieve secondary heating, so that the temperature of the return air will rise significantly, which can meet the heating and regeneration requirements of the second dehumidification rotor 117 for high-temperature regeneration. Figure 1 The return air flow rate at point 9 is 7200m 3 / h, dry bulb temperature is 120.0℃, and absolute humidity is 2.15g / kg. Then, the flow rate of return air flowing into bypass channel 125 is 7800m 3 / h, dry bulb temperature is 45.0℃, and absolute humidity is 2.15g / kg.

[0077] Then, the return air after secondary heating will flow into the second regeneration channel, prompting the second dehumidification wheel 117 regenerated at high temperature to complete the desorption regeneration work. The return air flowing out of the second regeneration channel will experience a decrease in temperature and an increase in humidity. Figure 1 The return air flow rate at point 10 is 7200m 3 / h, dry bulb temperature is 70.0℃, and absolute humidity is 9.30g / kg.

[0078] Then, the return air flowing out of the second regeneration channel will be mixed with the return air flowing out of the bypass channel 125 to form mixed regeneration air. Figure 1 The flow rate of the mixed regeneration wind at point 11 is 15000m 3 / h, the dry bulb temperature is 58.0°C, and the absolute humidity is 5.70g / kg, which can meet the heating regeneration requirement of the first dehumidification wheel 113 for low-temperature regeneration.

[0079] Finally, the mixed regeneration wind will pass through the first regeneration channel, so that the first dehumidification rotor 113 regenerated at low temperature can complete the desorption regeneration work, and then be discharged to the outdoor environment through the exhaust channel. The mixed regeneration wind flowing out of the first regeneration channel will have a phenomenon of temperature drop and humidity increase. Figure 1 The flow rate of the mixed regeneration wind at point 12 is 15000m 3 / h, dry bulb temperature is 32.0℃, and absolute humidity is 15.40g / kg.

[0080] In the two-stage rotary dehumidification air-conditioning unit of the fresh air type provided in the embodiment of the present invention, the outdoor fresh air can complete secondary dehumidification treatment under the operation of the first dehumidification rotary wheel 113 and the second dehumidification rotary wheel 117, and become dry air that meets the deep dehumidification requirements of the indoor space, thereby realizing the fresh air ventilation function.

[0081] If outdoor fresh air is directly used as regeneration air, the regeneration air needs to be subjected to cooling and dehumidification and wheel dehumidification to obtain low-humidity regeneration air, thereby ensuring a good regeneration effect of the second dehumidification wheel 117, which will increase the dehumidification energy consumption of the regeneration air. However, the embodiment of the present invention uses low-humidity indoor air as regeneration air, which becomes high-temperature and low-humidity air with strong regeneration ability after heating treatment, so that the low humidity advantage of indoor air can be effectively utilized, thereby reducing the dehumidification energy consumption of the regeneration air.

[0082] Moreover, the embodiment of the present invention effectively utilizes the heat carried by the condenser 122 in the heat pump system to preheat the regeneration air flowing into the second regeneration channel and part of the regeneration air flowing into the first regeneration channel, thereby making full use of air energy, improving energy recovery efficiency, and effectively reducing the energy consumption of the electric heater 123.

[0083] At the same time, the regeneration air flowing out from the bypass channel 125 is mixed with the regeneration air flowing out from the second regeneration channel before entering the first regeneration channel to increase the flow rate and temperature of the regeneration air flowing into the first regeneration channel. By effectively utilizing the flow rate and heat of the regeneration air flowing out from the second regeneration channel, the temperature and flow rate requirements of the regeneration air of the first dehumidification wheel 113 with a low regeneration temperature can be met. There is no need to perform secondary heating on the regeneration air flowing into the first regeneration channel, which can save the electric heating energy consumption required for the first dehumidification wheel 113, thereby greatly reducing the electric energy consumption of the regeneration air during operation, and further improving the energy recovery utilization rate, ultimately achieving the purpose of energy saving and environmental protection.

[0084] In addition, the embodiment of the present invention adopts a two-stage precooling combination of a second precooler 128 connected to an external centralized cold source and an independently arranged evaporator 116 of a direct expansion heat pump to perform secondary precooling on the air that will enter the second dehumidification channel, and uses the condenser 122 of the direct expansion heat pump to preheat the regeneration wind of the second dehumidification rotor 117 and heat part of the regeneration wind of the first dehumidification rotor 113. Such a design can not only utilize the high energy efficiency advantage of the second precooler 128 connected to an external centralized cold source, but also utilize the built-in evaporator 116 of the direct expansion heat pump to achieve a lower inlet air temperature of the second dehumidification rotor 117, which is beneficial to improving the dehumidification capacity of the second dehumidification rotor 117. At the same time, the condensation heat carried by the condenser 122 of the direct expansion heat pump can also be directly utilized to provide a part of the regeneration heat source for the two-stage rotor dehumidification system, which is beneficial to reducing the load and power of the electric heater 123, saving operating costs, and ultimately achieving the best comprehensive energy efficiency.

[0085] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0086] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A two-stage rotary dehumidification air conditioning unit of a fresh air type, characterized in that: include: a first dehumidification rotor configured as a low-temperature regeneration rotor, the first dehumidification rotor having a first dehumidification channel and a first regeneration channel; a second dehumidification wheel having a second dehumidification channel and a second regeneration channel; Fresh air channel; An air supply channel, wherein the fresh air channel, the first dehumidification channel, the second dehumidification channel and the air supply channel are sequentially connected through a pipeline; Return air duct; an exhaust passage, wherein the return air passage, the second regeneration passage, the first regeneration passage and the exhaust passage are sequentially connected through a pipeline; A heat pump system comprising a condenser; an electric heater, which and the condenser are arranged on the pipeline between the return air channel and the second regeneration channel, and the electric heater is located between the condenser and the second regeneration channel; The bypass channel has an inlet end connected to the pipeline between the condenser and the electric heater, and an outlet end of the bypass channel connected to the pipeline between the first regeneration channel and the second regeneration channel.

2. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 1 is characterized in that: An air flow rate of the bypass passage is greater than an air flow rate of the second regeneration passage.

3. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 2 is characterized in that: The air flow rate of the first regeneration channel is 65% to 85% of the air flow rate of the fresh air channel, and the air flow rate of the second regeneration channel is 30% to 35% of the air flow rate of the fresh air channel.

4. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 2 or 3, characterized in that: The bypass channel is provided with a first flow control valve, and one side of the second regeneration channel is provided with a second flow control valve.

5. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 1 is characterized in that: The heat pump system further includes an evaporator, which is disposed on a pipeline between the first dehumidification channel and the second dehumidification channel.

6. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 5 is characterized in that: It also includes a second precooler, which is arranged on the pipeline between the first dehumidification channel and the second dehumidification channel, and the second precooler is located between the first dehumidification channel and the evaporator.

7. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 6 is characterized in that: The second precooler has a second cold flow channel for connecting to a centralized cold source.

8. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 1 is characterized in that: It also includes a first precooler, which is arranged on the pipeline between the fresh air channel and the first dehumidification channel.

9. The two-stage rotary dehumidification air conditioning unit of the fresh air type according to claim 8 is characterized in that: The first precooler has a first cold flow channel for connecting to a centralized cold source.

10. The fresh air type two-stage rotary dehumidification air conditioning unit according to claim 1, characterized in that: It also includes a cooler and a warmer, and the cooler and the warmer are arranged on the pipeline between the second dehumidification channel and the air supply channel.

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