CN113418324A

CN113418324A - Air source heat pump drying system and control method and control device thereof

Info

Publication number: CN113418324A
Application number: CN202110552575.4A
Authority: CN
Inventors: 柴婷; 任滔; 宋强
Original assignee: Haier Shanghai R & D Center Co ltd; Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Current assignee: Haier Shanghai R & D Center Co ltd; Qingdao Haier Air Conditioner Gen Corp Ltd; Qingdao Haier Air Conditioning Electric Co Ltd; Haier Smart Home Co Ltd
Priority date: 2021-05-20
Filing date: 2021-05-20
Publication date: 2021-09-21

Abstract

The present application relates to the technical field of heat pumps, and discloses an air source heat pump drying system, which includes a plurality of refrigeration cycle units, a plurality of corresponding condensers are arranged in parallel, and a plurality of corresponding evaporators are arranged in parallel. Part of the evaporator is arranged outdoors; one end of the first air flow path is connected to the return air outlet of the drying area and is set to flow the first return air through the indoor evaporator and then through a plurality of condensers before being sent out; the second air flow One end is communicated with the return air outlet of the drying area and is set to confluence the second return air into the first return air after flowing through the indoor evaporator. Through the combination of multiple refrigeration cycle units, different drying modes can be realized to meet different drying needs. At the same time, combined with the air mixing function, part of the return air flows through the evaporator for dehumidification treatment, so as to achieve the best drying and dehumidification efficiency. Cost efficient. The application also discloses a control method and a control device for an air source heat pump drying system.

Description

Air source heat pump drying system and control method and control device thereof

Technical Field

The present application relates to the field of air source heat pump technology, and for example, to an air source heat pump drying system, and a control method and a control device thereof.

Background

Currently, an air source heat pump drying system can be divided into an external dehumidification system and an internal dehumidification system. The external dehumidification system is an open air system, and heated hot air is directly discharged to the outdoor atmosphere after drying products such as grains and the like, so that a large amount of heat is wasted. The inner dehumidification system is a closed air system, heated hot air is not discharged to the outside after drying products such as grains, but is led back to the evaporator through an air duct, and after the evaporator in the equipment room is dehumidified, the heated hot air is sent to the condenser to be heated and then sent into the drying room. It can be seen that the closed circulating air system of the inner dehumidification system can recycle high-temperature return air and save a large amount of heat compared with the open circulation of outer dehumidification. However, in the internal dehumidification system, the return air humidity coming out of the drying room is relatively high, and needs to be cooled to the dew point firstly, then enters the evaporator for cooling and dehumidification, and then enters the condenser for heating after being reheated to a higher temperature, and then is sent to the drying room. The treatment of cooling first and then heating wastes a large amount of heat. On the other hand, different drying objects have different requirements on dehumidification and heat supply of the system. For example, grain drying mainly requires high dehumidification performance, while tobacco drying not only requires dehumidification but also requires high-heat high-temperature baking. The internal dehumidification system mainly provides good dehumidification capacity; the outer dehumidification system can pump outdoor heat into the drying room, and provides a large amount of heat.

In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art: the existing air source heat pump drying system cannot meet different requirements of dehumidification and heat supply.

Disclosure of Invention

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview nor is intended to identify key/critical elements or to delineate the scope of such embodiments but rather as a prelude to the more detailed description that is presented later.

The embodiment of the disclosure provides an air source heat pump drying system, and a control method and a control device thereof, so as to solve the problem that the existing air source heat pump drying system cannot give consideration to different requirements of dehumidification and heat supply.

In some embodiments, the air-source heat pump drying system comprises: a plurality of refrigeration cycle units, each of which has a plurality of condensers arranged in parallel and each of which has a plurality of evaporators arranged in parallel; a part of the evaporators are arranged outdoors; one end of the first air flow path is communicated with the air return opening of the drying area and is set to enable the first return air to flow through the indoor evaporator and then flow through the condensers and then be sent out; one end of the second air flow path is communicated with the air return opening of the drying area and is set to enable the second path of return air to flow into the first path of return air after passing through the indoor evaporator; the return air of the air source heat pump drying system comprises a first path of return air and a second path of return air.

In some embodiments, the control method comprises: determining a target operation mode according to the target drying material; acquiring target operation parameters corresponding to the target operation mode according to a preset corresponding relation between the operation mode and the operation parameters; and controlling the air source heat pump drying system to operate at the target operation parameter.

In some embodiments, the control device comprises a processor and a memory storing program instructions, wherein the processor is configured to execute the aforementioned control method for the air source heat pump drying system when executing the program instructions.

The air source heat pump drying system, the control method and the control device thereof provided by the embodiment of the disclosure can realize the following technical effects:

in the air source heat pump drying system of the embodiment of the disclosure, in a plurality of refrigeration cycle units, condensers and evaporators of part of the refrigeration cycle units are arranged in an equipment room, and the refrigeration cycle units are defined as inner refrigeration cycle units; the condenser of the remaining refrigeration cycle units is disposed in the equipment room, and the evaporator is disposed outside the equipment room, which is defined as an outer refrigeration cycle unit. That is, can realize different stoving modes through the combination of a plurality of refrigeration cycle units to satisfy different stoving demands, combine the function of mixing the wind simultaneously, make partial return air flow through the evaporimeter and dehumidify, reach and optimize stoving dehumidification efficiency, low-cost high energy efficiency.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:

fig. 1 is a schematic structural diagram of an air source heat pump drying system provided in an embodiment of the present disclosure;

fig. 2 is a schematic structural diagram of another air source heat pump drying system provided in the embodiment of the disclosure;

fig. 3 is a schematic structural diagram of another air source heat pump drying system provided in the embodiment of the present disclosure;

fig. 4 is a schematic structural diagram of another air source heat pump drying system provided in the embodiment of the present disclosure;

fig. 5 is a schematic structural diagram of another air source heat pump drying system provided in the embodiment of the present disclosure;

FIG. 6 is a schematic structural diagram of a heat recovery unit provided by an embodiment of the present disclosure;

FIG. 7 is a schematic structural diagram of another heat recovery unit provided by embodiments of the present disclosure;

FIG. 8 is a schematic view of a heat recovery unit shown in direction C of FIG. 6;

fig. 9 is a schematic diagram of a control method for an air-source heat pump drying system according to an embodiment of the present disclosure;

fig. 10 is a schematic diagram of another control method for an air source heat pump drying system according to an embodiment of the present disclosure

Fig. 11 is a schematic diagram of another control method for an air-source heat pump drying system according to an embodiment of the present disclosure;

fig. 12 is a schematic diagram of a control device for an air source heat pump drying system according to an embodiment of the present disclosure.

Reference numerals:

10. a refrigeration cycle unit; 101. a compressor; 102. a condenser; 103. a throttle valve; 104. an evaporator; 105. an auxiliary evaporator; 11. an internal refrigeration cycle unit; 111. an indoor evaporator; 12. an external refrigeration cycle unit; 13. an internal/external refrigeration cycle unit; 131. a first parallel branch; 132. a first valve; 133. a second parallel branch; 134. a second valve; 21. a first air flow path; 211. a first fan; 212. a second fan; 22. a second air flow path; 221. a second air valve; 31. a total return air flow path; 32. a main air supply flow path; 40. a heat recovery unit; 41. a heat absorbing portion (first heat exchanger); 42. a heat releasing portion (second heat exchanger); 401. a heat pipe; 402. a first header; 403. a second header; 404. a fin; A. an equipment room; B. and a drying area.

Detailed Description

So that the manner in which the features and elements of the disclosed embodiments can be understood in detail, a more particular description of the disclosed embodiments, briefly summarized above, may be had by reference to the embodiments, some of which are illustrated in the appended drawings. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.

The terms "first," "second," and the like in the description and in the claims, and the above-described drawings of embodiments of the present disclosure, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged under appropriate circumstances such that embodiments of the present disclosure described herein may be made. Furthermore, the terms "comprising" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the disclosed embodiments and their examples and are not intended to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship in some cases. The specific meanings of these terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art as appropriate.

In addition, the terms "disposed," "connected," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements or components. Specific meanings of the above terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art according to specific situations.

The term "plurality" means two or more unless otherwise specified.

In the embodiment of the present disclosure, the character "/" indicates that the preceding and following objects are in an or relationship. For example, A/B represents: a or B.

The term "and/or" is an associative relationship that describes objects, meaning that three relationships may exist. For example, a and/or B, represents: a or B, or A and B.

It should be noted that, in the case of no conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

As shown in fig. 1 to 8, an embodiment of the present disclosure provides an air-source heat pump drying system, which includes a plurality of refrigeration cycle units 10, a first air flow path 21 and a second air flow path 22. A plurality of condensers 102 corresponding to the plurality of refrigeration cycle units 10 are arranged in parallel, a plurality of evaporators 104 corresponding to the plurality of refrigeration cycle units are arranged in parallel, and some of the evaporators 104 of the plurality of evaporators 104 are arranged outdoors. One end of the first air flow path 21 is communicated with a return air inlet of the drying area B and is set to send out a first return air after flowing through the indoor evaporator 111 and then flowing through the plurality of condensers 102; one end of the second air flow path 22 is communicated with the return air inlet of the drying area B and is set to collect the second return air into the first return air flowing through the indoor evaporator 111; the return air of the air source heat pump drying system comprises a first path of return air and a second path of return air.

In the air source heat pump drying system of the embodiment of the present disclosure, in the plurality of refrigeration cycle units 10, the condenser 102 and the evaporator 104 of some refrigeration cycle units are both disposed in the equipment room a, and the refrigeration cycle unit is defined as an inner refrigeration cycle unit 11; the condenser 102 of the remaining refrigeration cycle unit 10 is disposed inside the equipment room a, and the evaporator 104 is disposed outside the equipment room a, which is defined as an outer refrigeration cycle unit 12. That is, different drying modes can be realized through the combination of a plurality of refrigeration cycle units 10 to satisfy different drying requirements, and the function of mixing wind is combined simultaneously, so that part of return air flows through the evaporator to be dehumidified, and the purposes of optimizing drying and dehumidifying efficiency, low cost and high energy efficiency are achieved.

In the air source heat pump drying system according to the embodiment of the present disclosure, the indoor evaporator 111 refers to the evaporator 104 disposed in the equipment room a.

Depending on the type of refrigeration cycle unit that is started to operate among the plurality of refrigeration cycle units, the following three operation modes can be realized: a full internal dehumidification operation mode, a full external drying operation mode, and a half internal dehumidification operation mode. The refrigeration cycle units in the complete internal dehumidification operation mode for starting operation are all internal refrigeration cycle units 11, the refrigeration cycle units in the complete external drying operation mode for starting operation are all external refrigeration cycle units 12, and the refrigeration cycle units in the semi-internal dehumidification operation mode for starting operation comprise the internal refrigeration cycle units 11 and the external refrigeration cycle units 12.

In the semi-internal dehumidification operation mode, on the basis of an internal dehumidification system, the external refrigeration cycle unit 12 with the evaporator 104 arranged outdoors is added, on the basis of dehumidification, outdoor heat can be exchanged to the condenser 102 and transferred to the air flowing through the condenser 102 and finally sent into the drying chamber, so that the comprehensive efficiency of dehumidification and drying is realized, and the low-cost and high-energy-efficiency operation of the drying system can be realized.

Here, the "chamber" in "outdoor" and "indoor" means an equipment chamber a in which a refrigeration cycle unit is provided, which is a compartment relatively isolated from a drying zone B in which the materials to be dried are placed.

In the embodiment of the present disclosure, one refrigeration cycle unit 10 includes a refrigeration cycle loop formed by a compressor 101, a condenser 102, a throttle valve 103, and an evaporator 104, which are connected in sequence. A refrigeration cycle unit in which the evaporator 104 is disposed indoors is defined as an inner refrigeration cycle unit 11, and a refrigeration cycle unit in which the evaporator 104 is disposed outdoors is defined as an outer refrigeration cycle unit 12, depending on the disposition position of the evaporator. Alternatively, the number of the inner refrigeration cycle units 11 is one or more, and the number of the outer refrigeration cycle units 12 is one or more. The method is determined according to the requirement of the air source heat pump drying system.

That is, the air source heat pump drying system according to the embodiment of the present disclosure further includes a controller (not shown), a control end of which is respectively in control connection with the plurality of refrigeration cycle units 10, and is configured to control and start some or all of the plurality of refrigeration cycle units 10 according to the operation mode and control each refrigeration cycle unit that is started to operate according to preset unit operation parameters. The number of the partial refrigeration cycle units is any positive integer lower than that of the whole refrigeration cycle units.

Specifically, when the operation mode is the complete internal dehumidification operation mode, all the refrigeration cycle units which start to operate are the internal refrigeration cycle units 11; when the operation mode is a semi-internal dehumidification operation mode, the refrigeration cycle unit which is started to operate comprises an internal refrigeration cycle unit 11 and an external refrigeration cycle unit 12; when the operation mode is the complete external dehumidification operation mode, all the refrigeration cycle units that are started to operate are the external refrigeration cycle units 12.

The preset unit operation parameters of the respective refrigeration cycle units started to operate are related to the operation mode and the drying condition of the target drying material, the preset unit operation parameters of the same refrigeration cycle unit may be different in different operation modes, and the preset unit operation parameters of the same refrigeration cycle unit may be different due to different drying conditions (for example, supply air temperatures) of different target drying materials even in the same operation mode. Therefore, according to different operation parameters of the preset unit, the same operation mode can be further subdivided into a plurality of operation modes, such as a complete internal dehumidification operation mode I, a complete internal dehumidification operation mode II and the like. The drying conditions include air supply temperature, dehumidification demand, heat demand and the like.

The preset unit operation parameters include the operation frequency of the compressor 101, the rotating speed of the fan, the flow rate of the refrigerant and the like, are not limited, and are determined according to the drying conditions of the target drying materials.

Optionally, the air source heat pump drying system further includes a plurality of unit controllers (not shown), and the unit controllers are disposed in one-to-one correspondence with the refrigeration cycle units and are used for controlling the operation of the corresponding refrigeration cycle units; the control end of the controller is respectively in control connection with the plurality of unit controllers and is used for controlling and starting part or all of the plurality of unit controllers according to the operation mode and sending corresponding unit operation parameters to the started unit controllers; the unit controller receives the corresponding unit operation parameters and controls the operation of the corresponding refrigeration cycle unit. In the embodiment, the unit controller is added, so that the control system has hierarchy and is convenient to control.

In some embodiments, as shown in fig. 1 to 3, the air source heat pump drying system includes two refrigeration cycle units 10, one is an internal refrigeration cycle unit 11, each of which is disposed in the equipment room a; the other is an external refrigeration cycle unit 12, and the evaporator 104 of the respective elements is disposed outdoors. Wherein, the operation of the internal refrigeration cycle unit 11 is controlled to be a complete internal dehumidification operation mode, or the operation of the external refrigeration cycle unit 12 is controlled to be a complete external drying operation mode, or the operation of the internal refrigeration cycle unit 11 and the external refrigeration cycle unit 12 is controlled to be simultaneously started to be a semi-internal dehumidification operation mode.

In some embodiments, as shown in fig. 4, the air-source heat pump drying system includes three refrigeration cycle units, including two inner refrigeration cycle units 11 (a first inner refrigeration cycle unit and a second inner refrigeration cycle unit) and one outer refrigeration cycle unit 12. The method comprises the steps that a first internal refrigeration cycle unit and a second internal refrigeration cycle unit are controlled to be in a complete internal dehumidification operation mode when being started and operated simultaneously; the operation is controlled to be the complete external drying operation mode only when the external refrigeration cycle unit 12 is started; the first internal refrigeration cycle unit (and/or the second internal refrigeration cycle unit) is controlled to be in the semi-internal dehumidification operation mode when being started to operate simultaneously with the external refrigeration cycle unit 12.

In the embodiment of the present disclosure, the air source heat pump drying system includes, in addition to the refrigeration cycle of the refrigeration cycle unit 10, a return air flow cycle, that is, return air flowing out of the drying area B returns to the drying area B after heat exchange treatment by the evaporator 104 and the condenser 102 in the refrigeration cycle unit in the equipment area. Accordingly, the air source heat pump drying system includes an air flow path that provides a path for the return air flow cycle. In the embodiment of the present disclosure, the air flow path includes the first air flow path 21 and the second air flow path 22, so that the return air in the drying area B is divided into two return air paths, the first return air path flows through the evaporator 104, the second return air path does not flow through the evaporator 104, and the first return air path joins with the return air flowing through the evaporator 104, flows through the condenser 102, and then returns to the drying area B.

The air flow paths (the first air flow path 21 and the second air flow path 22) may be constructed air ducts or may be opposing separate channels physically separated in the apparatus chamber a. Therefore, the first air flow path 21 and the second air flow path 22 are not limited in construction, as long as two air flow paths are realized, the first air flow path 21 flows through the evaporator, and the second air flow path 22 does not flow through the evaporator but can communicate with the section of the first air flow path 21 after flowing through the evaporator. In some embodiments, a fan is provided on the first air flow path 21 and/or the second air flow path 22 to drive the return air flow. The setting position of the fan is not limited, and the return air flow can be realized.

Optionally, the air-source heat pump drying system further includes a first fan 211 disposed on the first air flow path 21 and located on the fluid outflow side of the evaporator 104 (the indoor evaporator 111).

Optionally, the air-source heat pump drying system further includes a second fan 212 disposed on the air flow path on the air outflow side of the condenser 102.

In some embodiments, a damper is disposed on the first air flow path 21 and/or the second air flow path 22. For adjusting the cross-sectional flow area of the first air flow path 21 and/or the second air flow path 22 and thereby adjusting the amount of return air flow in the flow paths.

Optionally, a second air valve 221 is disposed on the second air flow path 22, and is used for adjusting the flow cross-sectional area of the second air flow path 22, so as to adjust the amount of return air branched from the second air flow path 22, and adjust the branching ratio.

Optionally, a first air valve (not shown) is disposed on the first air flow path 21 for adjusting the flow cross-sectional area of the first air flow path 21, so as to adjust the amount of return air branched from the first air flow path 21, and adjust the branching ratio.

In the embodiment of the present disclosure, the diversion process of the return air is realized by the arrangement of the first air flow path 21 and the second air flow path 22. The first proportion that the first return air accounts for the total return air influences the dehumidification effect and the like of the internal refrigeration cycle unit 11, and the evaporator capacity which is located indoors and in a working state can be fully exerted by adjusting the first proportion, so that better dehumidification efficiency is achieved. The adjustment means of the first embodiment is not limited, and may be realized by adjusting an air damper provided in the first air flow path 21 and/or the second air flow path 22, or may be realized by matching the cross-sectional areas (i.e., the flow rates) of the first air flow path 21 and the second air flow path 22, or may be realized by matching the rotation speed of a fan provided in the first air flow path 21 and/or the second air flow path 22.

Optionally, when the operation mode is a full internal dehumidification operation mode, the first return air is controlled to account for 25% -45% of the first proportion of the return air. Optionally, the corresponding first proportion in the full internal dehumidification mode of operation is between 30% and 40%. Optionally, the corresponding first fraction in the full internal dehumidification mode of operation is 35%.

Optionally, when the operation mode is a semi-internal dehumidification operation mode, the first return air is controlled to account for 15% -30% of the first proportion of the return air. The first proportion corresponding to the semi-internal dehumidification operation mode is 20% -28%. Optionally, the semi-internal dehumidification mode of operation corresponds to a first fraction of 25%.

In some embodiments, the air source heat pump drying system further comprises a total return air flow path 31 and a total supply air flow path 32. The return air inflow end of the main return air flow path 31 is communicated with the drying area B, and the return air outflow end is communicated with the first inflow end of the first air flow path 21 and the second inflow end of the second air flow path 22; a main air supply flow path 32, an air supply outflow end of which is communicated with the drying zone B, and an air supply inflow end of which is communicated with a first outflow end of the first air flow path 21 and a second outflow end of the second air flow path 22; among them, the plurality of condensers 102 are located in the total blowing air flow path 32. In this embodiment, the first air flow path 21 and the second air flow path 22 are connected in parallel between the return air outflow end of the total return air flow path 31 and the supply air inflow end of the total supply air flow path 32, so that the distribution of return air and the mixing of supply air are facilitated, and the uniformity of supply air entering the drying area B is ensured. That is, the first air flow path 21 in which the plurality of condensers 102 are provided is divided into the total blowing flow path 32.

Optionally, a first flow direction of the first outflow end of the first air flow path 21 and a second flow direction of the second outflow end of the second air flow path 22 form a set angle. When the air in the first air flow path 21 and the air in the second air flow path 22 enter the main air supply flow path 32, they are mixed by means of the hedging, so that the uniformity of the air supply is ensured.

Alternatively, the air supply inflow end of the total air supply flow path 32 is provided with an air mixing structure. The mixing of the air flow in the first air flow path 21 and the air flow in the second air flow path 22 is promoted, and the uniformity of the air supply is ensured. The air mixing structure is not limited, and may be a plurality of baffles provided on the inner wall of the air supply inflow end of the main air supply flow path 32.

In some embodiments, the air source heat pump drying system further comprises a heat recovery unit 40; the heat recovery unit 40 includes a heat absorbing portion 41 and a heat releasing portion 42, the heat absorbing portion 41 and the heat releasing portion 42 being in heat exchange communication; the heat absorbing portion 41 is provided in the first air flow path 21 on the air inflow side of the indoor evaporator 111, and the heat releasing portion 42 is provided in the first air flow path 21 on the air outflow side of the indoor evaporator 111. In this embodiment, the heat absorbing unit 41 is disposed in front of the evaporator 104, and recovers heat from the return air to cool the air entering the evaporator 104; the heat releasing part 42 releases the heat absorbed by the heat absorbing part 41 to the return air dehumidified by the evaporator 104, so that the temperature of the return air is increased, and the heat carried by the return air is fully utilized.

In the embodiment of the present disclosure, the structural form of the heat recovery unit 40 is not limited, and may be set according to actual requirements. Alternatively, the heat recovery unit 40 includes a heat pipe heat exchanger (as shown in FIG. 1), a wind-wind heat exchanger (as shown in FIG. 2), or a wind-water-wind heat exchanger (as shown in FIG. 3).

In some embodiments, the heat absorbing part 41 and the heat releasing part 42 are provided in a split type. To facilitate the arrangement on the air inflow side and the air outflow side of the evaporator. In the present embodiment, alternatively, as shown in fig. 6 and 7, the first fan 211 provided on the first air flow path 21 is provided on the air outlet side of the heat absorbing portion 41. The smooth flow of the air can be completed only by arranging one fan at the evaporator and the heat recovery unit 40, the number of the arranged fans is reduced, and the optimal configuration of the fans is realized.

Alternatively, the heat absorbing part 41 and the heat releasing part 42 are each an independent heat exchanger. In the present embodiment, the heat exchanger of the heat absorbing portion 41 is defined as a first heat exchanger, and the heat exchanger of the heat releasing portion 42 is defined as a second heat exchanger.

Optionally, as shown in fig. 6 to 8, the first heat exchanger and the second heat exchanger are both tube heat exchangers including heat exchange tubes arranged in an array. In this embodiment, among the tubular heat exchanger, including the heat exchange tube matrix of array arrangement, the clearance between the adjacent heat exchanger pipe constitutes to be become the heat transfer wind channel.

Alternatively, as shown in fig. 6, both the first heat exchanger and the second heat exchanger are heat pipe heat exchangers. That is, the heat recovery unit 40 includes a first heat pipe exchanger and a second heat pipe exchanger. The heat pipe heat exchanger includes a plurality of heat pipes 401 arranged in an array.

Optionally, as shown in fig. 6 to 8, the heat pipe heat exchanger includes: a plurality of heat pipes 401, a first header 402 and a second header 403, the plurality of heat pipes 401 being arranged in an array; a first header 402 communicating with first ends of the plurality of heat pipes 401, respectively; the second headers 403 communicate with second ends of the plurality of heat pipes 401, respectively. In the heat recovery unit 40, a first header 402 of the first heat pipe heat exchanger is communicated with a first header 402 of the second heat pipe heat exchanger, and a second header 403 of the second heat pipe heat exchanger is communicated with a second header 403 of the first heat pipe heat exchanger. And the heat exchange between the first heat pipe heat exchanger and the second heat pipe heat exchanger is realized. In this embodiment, the first heat pipe heat exchanger is provided as the heat pipe 401 evaporator in the first air flow path 21 in front of the indoor evaporator 111, and absorbs heat in the return air to lower the temperature of the return air; the second heat pipe exchanger serves as the condenser 102 of the heat pipe 401, releases heat absorbed by the evaporator end of the heat pipe 401 to return air subjected to dehumidification by the evaporator, improves the temperature of the return air, and makes full use of the heat carried by the return air.

Optionally, a plurality of heat pipes 401 arranged in an array form one or more groups of heat pipes in each row/each row, and a first header 402 and a second header 403 are respectively and correspondingly arranged at two ends of each group of heat pipes to form a heat pipe heat exchange unit; one heat pipe heat exchange unit of the first heat pipe heat exchanger is communicated with one heat pipe heat exchange unit of the second heat pipe heat exchanger in a heat exchange mode in a one-to-one correspondence mode. As shown in fig. 6 and 7, for the sake of simplifying the drawings, it is only shown that the first header 402 (and the second header 403) of one heat pipe heat exchange unit of the first heat pipe heat exchanger is communicated with the first header 402 (and the second header 403) of one heat pipe heat exchange unit of the second heat pipe heat exchanger, and the rest of the heat pipe heat exchange units are communicated in one-to-one correspondence.

Optionally, the heat pipe heat exchanger further includes a plurality of fins 404, which are sleeved on the plurality of heat pipes 401 in a manner perpendicular to the heat pipes 401 and are disposed on the heat pipes 401 at set intervals. The heat exchange area with the air is increased, and the heat exchange efficiency is improved. Specifically, as shown in fig. 6 and 8, one fin 404 is sleeved on a plurality of heat pipes 401 in one heat pipe heat exchange unit; and a plurality of fins 404 are arranged on a plurality of heat pipes 401 in each heat pipe heat exchange unit at set intervals.

In some embodiments, the second heat pipe heat exchanger is disposed above the first heat pipe heat exchanger. The refrigerant fluid in the heat recovery unit 40 using the heat pipe 401 is self-driven by gravity to perform efficient heat exchange.

In some embodiments, as shown in fig. 6 and 7, the heat absorbing part 41 (first heat exchanger) and/or the heat releasing part 42 (second heat exchanger) are disposed obliquely so as to turn the flow direction of the air after flowing through the heat absorbing part 41 and/or the heat releasing part 42. The heat absorbing part 41 and/or the heat releasing part 42 are/is obliquely arranged, so that the heat in the return air is recovered or the return air after being dehumidified by the evaporator is heated, and the flow direction of the return air can be turned and guided; in the diversion process, the wind resistance is small, and the return air is in contact collision with the heat exchange surface of the heat absorbing part 41 and/or the heat releasing part 42, so that the heat exchange efficiency is improved. In this embodiment, the first return air may be turned after flowing through the heat absorbing portion 41, or the first return air may be turned after flowing through the heat releasing portion 42, or both the first return air and the first return air may be turned after flowing through the heat absorbing portion 41 and the heat releasing portion 42, respectively. The air mixing method is determined according to factors such as space layout and air mixing requirements in the equipment room A in actual production application.

In the present embodiment, "inclination" in the inclined arrangement is relative to the air flowing direction at the air inflow side, and generally, the heat exchange surface of the heat absorbing portion 41 or the heat releasing portion 42 is perpendicular to the air flowing direction (i.e. the included angle α between the heat exchange surface and a reference line is 90 °, wherein the reference line is a straight line parallel to the air flowing direction at the air inflow side), and the air flowing direction does not turn after passing through the heat absorbing portion 41 or the heat releasing portion 42. When the included angle α is not 90 °, the air is regarded as being obliquely disposed, and the air flow direction is turned after passing through the heat absorbing portion 41 or the heat releasing portion 42.

Alternatively, the heat exchanging surface of the heat absorbing portion 41 and/or the heat releasing portion 42 may include an angle α of 15 ° or more and less than 90 ° (the angle range is defined as a first angle range) or an angle α of 90 ° or more and less than 150 ° (the angle range is defined as a second angle range) with the respective base line. In the present embodiment, the included angle α is 90 ° as a boundary point, and when the included angle α is in the first angle range, the heat exchange surface of the heat absorbing portion 41 and/or the heat releasing portion 42 is inclined toward the air inflow side, which is defined as a first inclined arrangement (as shown in fig. 6). When the included angle α is in the second angle range, the heat exchange surface of the heat absorbing part 41 and/or the heat releasing part 42 is inclined along the air flowing direction, which is defined as the second inclined arrangement (as shown in fig. 7). Therefore, different steering directions can be realized, and the inclined arrangement mode of the heat absorbing part 41 or the heat releasing part 42 can be determined according to actual requirements. Here, since the air inflow side of the heat absorbing portion 41 and the heat releasing portion 42 is different from the air flowing direction, the reference line (defined as the first reference line l1) of the heat absorbing portion 41 is different from the reference line (defined as the second reference line l2) of the heat releasing portion 42.

Alternatively, the heat absorbing part 41 (first heat exchanger) and the heat releasing part 42 (second heat exchanger) are both disposed obliquely, and the oblique arrangement of the two is the same or different. According to actual requirements, the first return air is turned for at least two times, the first air flow path 21 is matched, the third turning can be achieved, the heat absorbing portion 41 and the heat releasing portion 42 are matched and arranged in an inclined mode, wind resistance is small, and heat exchange capacity of each heat exchanger can be favorably exerted.

In the present embodiment, the two are arranged in the same inclination manner, and the first turning direction of the air flowing direction after passing through the heat absorbing portion 41 and the second turning direction of the air flowing direction after passing through the heat releasing portion 42 are the same. For example, the first turning direction and the second turning direction are both clockwise or both counterclockwise, so that the flowing direction of the first return air is changed.

When the two are arranged in different inclination manners, the first steering direction and the second steering direction are different, for example, the first steering direction is clockwise, and the second steering direction is counterclockwise. In this case, the entire first air flow path 21 extends in one direction, but is not aligned with the same line.

In some embodiments, the angle α 1 between the heat exchange surface of the heat absorbing portion 41 and the reference line (the first reference line l1) is greater than or equal to 30 ° and less than or equal to 75 °, or greater than or equal to 105 ° and less than or equal to 140 °. Alternatively, the included angle α 1 is greater than or equal to 45 ° and less than or equal to 65 °, or greater than or equal to 115 ° and less than or equal to 130 °. Alternatively, included angle α 1 is 60 °, or included angle α 1 is 120 °.

In some embodiments, the included angle α 2 between the heat exchanging surface of the heat releasing portion 42 and the reference line (the second reference line l2) is greater than or equal to 30 ° and less than or equal to 75 °, or greater than or equal to 105 ° and less than or equal to 140 °. Alternatively, the included angle α 2 is greater than or equal to 45 ° and less than or equal to 65 °, or greater than or equal to 115 ° and less than or equal to 130 °. Alternatively, included angle α 2 is 60 °, or included angle α is 120 °.

In some embodiments, the heat absorbing part 41 (first heat exchanger) and the heat releasing part 42 (second heat exchanger) are both disposed obliquely in the same manner; and the included angle beta between the two opposite side surfaces of the heat absorbing part 41 and the heat releasing part 42 is 90-150 degrees.

Alternatively, the included angle β between the heat absorbing portion 41 and the two opposite side surfaces of the heat releasing portion 42 is 100 ° to 140 °. Alternatively, the included angle β between the heat absorbing portion 41 and the two opposite side surfaces of the heat releasing portion 42 is 120 °.

Alternatively, as shown in fig. 6, the heat absorbing portion 41 and the heat releasing portion 42 are both disposed obliquely in the same manner; and the included angle α 1 between the heat exchange surface of the heat absorbing portion 41 and the first base line l1 (in the horizontal direction) is 60 °, and the included angle α 2 between the heat exchange surface of the heat releasing portion 42 and the second base line l2 (in the vertical direction) is 30 °. That is, the heat absorbing portion 41 and the heat releasing portion 42 are formed at an angle of 120 ° with respect to the opposite side surfaces. The method is suitable for application scenes in which the air flow direction is turned by 180 degrees.

Alternatively, as shown in fig. 7, the heat absorbing portion 41 and the heat releasing portion 42 are both disposed obliquely in the same manner; and the included angle α 1 between the heat exchange surface of the heat absorbing portion 41 and the first base line l1 (in the horizontal direction) is 120 °, and the included angle α 2 between the heat exchange surface of the heat releasing portion 42 and the second base line l2 (in the vertical direction) is 120 °. The heat absorbing part 41 is at an angle of 120 ° with respect to the opposite side surfaces of the heat discharging part 42. The method is suitable for application scenes in which the air flow direction is turned by 180 degrees.

In the present embodiment, the heat absorbing unit 41 is disposed in the heat recovery unit 40 in an inclined manner so as to divert the flow direction of the return air, and the first air flow path 21 is also diverted, so that the present invention is applicable to an application in which the space of the equipment room a is limited. That is, each functional element of the internal refrigeration cycle unit 11 is disposed in the equipment room a, and in order to ensure air distribution and air mixing, the first air flow path 21 needs to have a certain length, and the space of the equipment room a is limited, so when the first air flow path 21 is designed to include a turning section, the layout of the refrigeration cycle unit is compact on the premise of satisfying the distribution and air mixing requirements, and the refrigeration cycle unit is suitable for an application scenario in which the space of the equipment room a is limited.

In some embodiments, the first air flow path 21 includes a turning section where the indoor evaporator 111 and the heat recovery unit 40 are disposed. At the turn to the section department, the air flow takes place to turn to, then turbulent phenomenon can appear, turbulent phenomenon increases to a certain extent and collides with the contact of the heat transfer surface of evaporimeter, improves heat exchange efficiency, improves dehumidification effect.

Alternatively, the heat absorbing portion 41 is provided at the starting end position of the turning section of the first air flow path 21; the heat releasing portion 42 is provided at the terminal end position of the turning section of the first air flow path 21.

In some embodiments, as shown in fig. 1, 4 and 5, the first air flow path 21 has a U-shape, and the indoor evaporator 111 may be disposed at a U-turn section of the U-shaped first air flow path 21. That is, the first air flow path 21 makes a 180 ° turn.

Alternatively, the heat absorbing portion 41 is provided at a starting end position of the U-turn of the U-shaped first air flow path 21, and the heat releasing portion 42 is provided at a terminating end position of the U-turn of the U-shaped first air flow path 21.

In some embodiments, the heat exchange surface of the indoor evaporator 111 is parallel to the heat exchange surface of the heat discharging part 42 in the heat recovery unit 40.

In the embodiment of the present disclosure, the first return air on the first air flow path 21 needs to exchange heat with the evaporator, and therefore, the arrangement of the plurality of evaporators needs to ensure that the first return air can exchange heat with the evaporator in the operating state. In some embodiments, a plurality of indoor evaporators 111 are sequentially disposed on the first air flow path 21, and a heat exchange surface of each evaporator covers the first air flow path 21. That is, the edge of each indoor evaporator 111 is connected to the inner wall of the air flow path. The first return air on the first air flow path 21 can exchange heat with the evaporator. Of course, the arrangement of a plurality of evaporators is not limited to the sequential arrangement, and other arrangement modes capable of ensuring that the first return air can exchange heat with the evaporator in the working state are all applicable.

With the heat recovery unit 40 shown in fig. 6 or fig. 7, under one operating condition (e.g., a semi-internal dehumidification operating mode), the temperature of the first return air entering the first heat pipe exchanger (heat absorbing portion 41) is 45 ℃, the temperature of the first return air after primary treatment by the first heat pipe exchanger is reduced to 40 ℃, and the temperature of the first return air after secondary treatment by the evaporator and the second heat pipe exchanger in sequence can still be maintained at 38 ℃. The temperature entering the evaporator is reduced, the heat exchange efficiency of the evaporator is guaranteed, and the heat loss is reduced to the minimum extent through the arrangement of the heat recovery unit 40.

In some embodiments, as shown in fig. 5, the refrigeration cycle unit with the evaporator located outdoors (outside the equipment room a), that is, the outer refrigeration cycle unit 12, further includes an auxiliary evaporator 105 and a valve, the auxiliary evaporator 105 is located outdoors and is arranged in parallel communication with the evaporator located outdoors; the valves are respectively disposed on the parallel branch (defined as the first parallel branch 131) of the auxiliary evaporator 105 and the parallel branch (defined as the second parallel branch 133) of the outdoor evaporator, and the outdoor evaporator and/or the auxiliary evaporator 105 is connected to the refrigeration cycle unit by controlling the opening or closing of the valves. In this embodiment, the external refrigeration cycle unit 12 including the auxiliary evaporator 105 is defined as the internal/external refrigeration cycle unit 13, that is, a refrigeration cycle unit that can be switched between the internal refrigeration cycle unit 11 and the external refrigeration cycle unit 12, so that the operation modes can be switched more flexibly to meet the requirements of different drying materials.

Optionally, the valves include a first valve 132 and a second valve 134, the first valve 132 is disposed in the first parallel branch 131, and the second valve 134 is disposed in the second parallel branch 133. That is, when the first valve 132 is controlled to be opened and the second valve 134 is controlled to be closed, the refrigeration cycle unit is the external refrigeration cycle unit 12; when the first valve 132 is controlled to be closed and the second valve 134 is controlled to be opened, the refrigeration cycle unit is the inner refrigeration cycle unit 11; when the first valve 132 and the second valve 134 are controlled to be opened simultaneously, the refrigeration cycle unit is the internal and external refrigeration cycle unit 12. Optionally, the number of the first valves 132 is two, and the first valves are respectively disposed at two ends of the first parallel branch 131; the number of the second valves 134 is two, and the second valves are respectively disposed at both ends of the second parallel branch 133. The refrigerant is ensured to completely flow into the evaporator in the working state.

An air source heat pump drying system as shown in fig. 5 includes two refrigeration cycle units, one is an inner refrigeration cycle unit 11, and the other is an inner/outer refrigeration cycle unit 13. Controlling the internal refrigeration cycle unit 11 and the internal/external refrigeration cycle unit 13 to be started simultaneously, and controlling the first parallel branch 131 in the internal/external refrigeration cycle unit 13 to be conducted and the second parallel branch 133 in the internal/external refrigeration cycle unit 13 to be cut off, wherein the operation mode is a complete internal dehumidification operation mode; or, the internal refrigeration cycle unit 11 and the internal/external refrigeration cycle unit 13 are controlled to be started simultaneously, the first parallel branch 131 in the internal/external refrigeration cycle unit 13 is controlled to be cut off, and the second parallel branch 133 in the internal/external refrigeration cycle unit 13 is controlled to be conducted, so that a semi-internal dehumidification operation mode is adopted; or, the internal refrigeration cycle unit 11 and the internal/external refrigeration cycle unit 13 are controlled to be started simultaneously, and the first parallel branch 131 and the second parallel branch 133 in the internal/external refrigeration cycle unit 13 are controlled to be conducted, so that the semi-internal dehumidification operation mode is adopted.

With reference to fig. 9, an embodiment of the present disclosure provides a control method for an air source heat pump drying system, where the air source heat pump drying system of any of the foregoing embodiments is adopted, and the control method includes:

and S110, determining a target operation mode according to the target drying material.

In step S110, the target drying material is a material placed in the drying region B, for example, grain, vegetable, fruit, or tobacco, and the target drying material may be input by a user, or the target drying material may be a drying material selected by the user from preset material options, or the target drying material may be obtained by obtaining an image of the material by an image obtaining device (for example, a camera) disposed in the drying region B and then performing image analysis, so that the obtaining manner of the target drying material is not limited, that is, in step S110, the method may further include a step of obtaining the target drying material.

Different drying conditions are required for drying different target materials. The drying conditions include air supply temperature, dehumidification demand, heat demand, and the like. For example, when grains, tobacco and the like are dried, the air supply temperature of hot air entering the drying area B needs to be greater than or equal to 55 ℃, wherein grains are mainly used for dehumidification, and the tobacco needs to be dried by heat while dehumidification is performed. When vegetable and fruit materials such as vegetables and fruits are dried, the requirement on the air outlet temperature of hot air entering the drying area B is not high, and the emphasis is on dehumidification. Therefore, different drying materials correspond to different operation modes so as to meet the drying requirements of different drying materials.

Optionally, the target operation mode is determined according to a drying condition of the target drying material.

As mentioned above, the operation modes of the air source heat pump drying system include a complete internal dehumidification operation mode, a semi-internal dehumidification operation mode and a complete external drying operation mode, and the unit operation parameters of each refrigeration cycle unit in each operation mode are different according to the different air supply temperatures of different target drying materials, so that each operation mode is further refined into a plurality of operation modes. For example, the full internal dehumidification operation mode is further refined into a full internal dehumidification operation mode i, a full internal dehumidification operation mode ii, and the like.

And S120, acquiring target operation parameters corresponding to the target operation mode according to the preset corresponding relation between the operation mode and the operation parameters.

The operation parameters comprise the types and the corresponding number of the refrigeration cycle units which are started to operate, the unit operation parameters of each refrigeration cycle unit which is started to operate, the first proportion of the first return air in the return air and the like. The operation mode is the same as that described in step S110.

The unit operation parameters include the operation frequency of the compressor 101, the rotating speed of the fan, the flow rate of the refrigerant and the like, are not limited, and are determined according to the drying conditions of the target drying materials. For example, the definition of the unit operating parameters may be determined in accordance with the supply air temperature of the target drying material.

The first proportion that the first return air accounts for the total return air influences the dehumidification effect and the like of the internal refrigeration cycle unit 11, and the evaporator capacity which is located indoors and in a working state can be fully exerted by adjusting the first proportion, so that better dehumidification efficiency is achieved. The adjustment means of the first embodiment is not limited, and may be implemented by adjusting an air damper provided in the first air flow path 21 and/or the second air flow path 22, or by matching the cross-sectional areas (i.e., the flow rates) of the first air flow path 21 and the second air flow path 22, or by further matching the rotation speed of a fan provided in the first air flow path 21 and/or the second air flow path 22.

Optionally, the target operating parameter includes a first proportion of the first return air to the total return air; and the first proportion corresponding to the complete internal dehumidification operation mode is 25-45%; the first proportion corresponding to the semi-internal dehumidification operation mode is 15% -30%.

Optionally, the first proportion corresponding to the full internal dehumidification mode of operation is between 30% and 40%. Optionally, the full internal dehumidification mode of operation corresponds to a first fraction of 35%.

Optionally, the first proportion corresponding to the semi-internal dehumidification mode of operation is 20% to 28%. Optionally, the semi-internal dehumidification mode of operation corresponds to a first fraction of 25%.

And S130, controlling the air source heat pump drying system to operate according to the target operation parameters.

According to the control method of the air source heat pump drying system, the drying requirements for different materials are met through the preset corresponding relation between the operation mode and the operation parameters, and the applicable scenes of the system are increased.

The control method of the embodiment of the present disclosure is specifically described in conjunction with the air source heat pump drying system shown in fig. 5, which includes an internal refrigeration cycle unit 11 and an internal/external refrigeration cycle unit 13. As shown in fig. 10, the control method includes the steps of:

s101, determining a target drying material, grain or tobacco.

S102, drying materials according to a grain target, wherein the target air supply temperature is 55 ℃, and determining that the target operation mode is a complete internal dehumidification operation mode I. Or, according to the tobacco target drying material, the target air supply temperature is 55 ℃, and the target operation mode is determined to be the semi-internal dehumidification operation mode I.

S103, acquiring target operation parameters corresponding to the target operation mode according to the preset corresponding relation between the operation mode and the operation parameters.

For example, the operating parameters (i.e., the target operating parameters i) corresponding to the total internal dehumidification mode i include: starting the internal refrigeration cycle unit 11, starting the internal/external refrigeration cycle unit 13, and controlling the first parallel branch 131 to be conducted and the second parallel branch 133 to be cut off; the first return air accounts for 35 percent of the first proportion of the return air; the unit operating parameters are not limited too much here and can be adjusted by conventional means.

For example, the operating parameters (i.e., the target operating parameter ii) corresponding to the semi-internal dehumidification mode i include: starting the internal refrigeration cycle unit 11, starting the internal/external refrigeration cycle unit 13, and controlling the first parallel branch 131 to be cut off and the second parallel branch 133 to be conducted; the first return air accounts for 25 percent of the first proportion of the return air; the unit operating parameters are not limited too much here and can be adjusted by conventional means.

And S104, controlling the air source heat pump drying system to operate according to the target operation parameter I or the target operation parameter II.

Of course, the embodiments of the present disclosure are not limited to the above-mentioned drying of grains and tobacco, and other materials that need to be dried, such as vegetables and fruits, may also be dried by using the air source heat pump drying system and the control method thereof of the embodiments of the present disclosure.

As shown in fig. 11, an embodiment of the present disclosure provides a control method of an air source heat pump drying system, further including:

s210, air supply temperature is obtained.

The temperature of the air supply is detected by a temperature detection device such as a temperature sensor provided at an air supply outlet (a position communicating with the main air supply flow path 32) of the drying zone B.

And S220, acquiring the return air temperature and the first inlet air temperature of the air inlet side of the evaporator under the condition that the air supply temperature does not fall into the target air supply temperature interval.

The target blowing temperature interval is [ T ]^O-δ₁，T^O+δ₂]，T^OIs a target supply air temperature, delta₁The allowable float temperature, δ, for the first setting₂Allowing floating temperature for a second setting, e.g. delta₁And delta₂The value range of (A) is 0-0.5 ℃. Delta₁And delta₂May or may not be equal.

The target air supply temperature is determined according to the target drying material, for example, the target air supply temperature of the grain and the tobacco is 55 ℃.

δ₁And delta₂The value of (A) is determined according to the sensitivity of the target drying material to the air supply temperature. If the sensitivity of the target drying material to the air supply temperature is high, delta₁And delta₂Is small, e.g. delta₁And delta₂The value range of (A) is 0-0.2 ℃. If the sensitivity of the target drying material to the air supply temperature is low, delta₁And delta₂Can be increased, e.g., by₁And delta₂The value range of (A) is 0.3-0.5 ℃.Avoiding frequent adjustment of the air source heat pump drying system.

The return air temperature is obtained by a temperature detection device such as a temperature sensor provided at a return air inlet (a position communicating with the main return air flow path 31) of the drying zone B. Optionally, the return air temperature is dry and wet bulb temperature.

The first intake air temperature is acquired by a temperature detection device such as a temperature sensor provided on the intake air side of the evaporator.

And S230, obtaining the dew point temperature according to the return air temperature.

And calculating to obtain the corresponding dew point temperature according to the return air temperature, wherein the calculation method can be realized by adopting a conventional method.

And S240, under the condition that the first inlet air temperature is higher than the first preset temperature, controlling and increasing the return air quantity of the second return air in the second air flow path 22. Wherein the first preset temperature is greater than the dew point temperature.

Optionally, the first preset temperature is the sum of the dew point temperature and a preset value, and the preset value is greater than or equal to 1 and less than or equal to 5. Optionally, the preset value is greater than or equal to 1.5 and less than or equal to 3. Optionally, the preset value is 2.

Under the condition that first inlet air temperature is greater than first preset temperature, it shows that the amount of wind through the evaporimeter is bigger than normal this moment, and the refrigeration ability of evaporimeter is not enough, under the unchangeable condition of total return air volume, reduces the return air volume of the first way return air through the evaporimeter, reduces first proportion promptly to the refrigeration ability of matching the evaporimeter makes the evaporimeter ability exert fullest, reaches better dehumidification efficiency.

Specifically, the control increases the return air amount of the second return air in the second air flow path 22, including increasing the opening degree of an air valve provided on the second air flow path 22.

Alternatively, in this step S240, it is also possible to control to increase the frequency of the compressor 101 of the internal refrigeration cycle unit 11 at the same time. The refrigerating capacity of the evaporator is improved.

Alternatively, in this step S240, the fan rotation speed of the first fan 211 in the first air flow path 21 may be controlled to be reduced at the same time. The return air quantity of the first return air passing through the evaporator is reduced, namely, the first proportion is reduced.

As shown in fig. 12, an embodiment of the present disclosure provides a control device for an air source heat pump drying system, which includes a processor (processor)500 and a memory (memory) 501. Optionally, the apparatus may also include a Communication Interface 502 and a bus 503. The processor 500, the communication interface 502, and the memory 501 may communicate with each other via a bus 503. Communication interface 502 may be used for information transfer. The processor 500 may call logic instructions in the memory 501 to execute the control method for the air source heat pump drying system of the above embodiment.

In addition, the logic instructions in the memory 501 may be implemented in the form of software functional units and may be stored in a computer readable storage medium when the logic instructions are sold or used as independent products.

The memory 501 is a computer-readable storage medium, and can be used for storing software programs, computer-executable programs, such as program instructions/modules corresponding to the methods in the embodiments of the present disclosure. The processor 500 executes functional applications and data processing by executing program instructions/modules stored in the memory 501, that is, implements the control method for the air source heat pump drying system in the above embodiment.

The memory 501 may include a storage program area and a storage data area, wherein the storage program area may store an operating system, an application program required for at least one function; the storage data area may store data created according to the use of the terminal device, and the like. Further, the memory 501 may include a high-speed random access memory and may also include a nonvolatile memory.

The embodiment of the disclosure provides an electronic device, which comprises the control device for the air source heat pump drying system.

The embodiment of the disclosure provides a computer-readable storage medium, which stores computer-executable instructions configured to execute the control method for the air source heat pump drying system.

The disclosed embodiments provide a computer program product comprising a computer program stored on a computer readable storage medium, the computer program comprising program instructions which, when executed by a computer, cause the computer to perform the above-described control method for an air source heat pump drying system.

The computer-readable storage medium described above may be a transitory computer-readable storage medium or a non-transitory computer-readable storage medium.

The technical solution of the embodiments of the present disclosure may be embodied in the form of a software product, where the computer software product is stored in a storage medium and includes one or more instructions to enable a computer device (which may be a personal computer, a server, or a network device) to execute all or part of the steps of the method of the embodiments of the present disclosure. And the aforementioned storage medium may be a non-transitory storage medium comprising: a U-disk, a removable hard disk, a Read-Only Memory (ROM), a Random Access Memory (RAM), a magnetic disk or an optical disk, and other various media capable of storing program codes, and may also be a transient storage medium.

The above description and drawings sufficiently illustrate embodiments of the disclosure to enable those skilled in the art to practice them. Other embodiments may incorporate structural, logical, electrical, process, and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. Furthermore, the words used in the specification are words of description only and are not intended to limit the claims. As used in the description of the embodiments and the claims, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. Similarly, the term "and/or" as used in this application is meant to encompass any and all possible combinations of one or more of the associated listed. Furthermore, the terms "comprises" and/or "comprising," when used in this application, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof. Without further limitation, an element defined by the phrase "comprising an …" does not exclude the presence of other like elements in a process, method or apparatus that comprises the element. In this document, each embodiment may be described with emphasis on differences from other embodiments, and the same and similar parts between the respective embodiments may be referred to each other. For methods, products, etc. of the embodiment disclosures, reference may be made to the description of the method section for relevance if it corresponds to the method section of the embodiment disclosure.

Those of skill in the art would appreciate that the various illustrative elements and algorithm steps described in connection with the embodiments disclosed herein may be implemented as electronic hardware or combinations of computer software and electronic hardware. Whether such functionality is implemented as hardware or software may depend upon the particular application and design constraints imposed on the solution. Skilled artisans may implement the described functionality in varying ways for each particular application, but such implementation decisions should not be interpreted as causing a departure from the scope of the disclosed embodiments. It can be clearly understood by the skilled person that, for convenience and brevity of description, the specific working processes of the system, the apparatus and the unit described above may refer to the corresponding processes in the foregoing method embodiments, and are not described herein again.

In the embodiments disclosed herein, the disclosed methods, products (including but not limited to devices, apparatuses, etc.) may be implemented in other ways. For example, the above-described apparatus embodiments are merely illustrative, and for example, the division of the units may be merely a logical division, and in actual implementation, there may be another division, for example, multiple units or components may be combined or integrated into another system, or some features may be omitted, or not executed. In addition, the shown or discussed mutual coupling or direct coupling or communication connection may be an indirect coupling or communication connection through some interfaces, devices or units, and may be in an electrical, mechanical or other form. The units described as separate parts may or may not be physically separate, and parts displayed as units may or may not be physical units, may be located in one place, or may be distributed on a plurality of network units. Some or all of the units can be selected according to actual needs to implement the present embodiment. In addition, functional units in the embodiments of the present disclosure may be integrated into one processing unit, or each unit may exist alone physically, or two or more units are integrated into one unit.

The flowchart and block diagrams in the figures illustrate the architecture, functionality, and operation of possible implementations of systems, methods and computer program products according to embodiments of the present disclosure. In this regard, each block in the flowchart or block diagrams may represent a module, segment, or portion of code, which comprises one or more executable instructions for implementing the specified logical function(s). In some alternative implementations, the functions noted in the block may occur out of the order noted in the figures. For example, two blocks shown in succession may, in fact, be executed substantially concurrently, or the blocks may sometimes be executed in the reverse order, depending upon the functionality involved. In the description corresponding to the flowcharts and block diagrams in the figures, operations or steps corresponding to different blocks may also occur in different orders than disclosed in the description, and sometimes there is no specific order between the different operations or steps. For example, two sequential operations or steps may in fact be executed substantially concurrently, or they may sometimes be executed in the reverse order, depending upon the functionality involved. Each block of the block diagrams and/or flowchart illustrations, and combinations of blocks in the block diagrams and/or flowchart illustrations, can be implemented by special purpose hardware-based systems that perform the specified functions or acts, or combinations of special purpose hardware and computer instructions.

The above description and drawings sufficiently illustrate embodiments of the disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. An air source heat pump drying system, comprising:

a plurality of refrigeration cycle units, each of which has a plurality of condensers arranged in parallel and each of which has a plurality of evaporators arranged in parallel; a part of the evaporators are arranged outdoors;

one end of the first air flow path is communicated with the air return opening of the drying area and is set to enable the first return air to flow through the indoor evaporator and then flow through the condensers and then be sent out;

one end of the second air flow path is communicated with the air return opening of the drying area and is set to enable the second path of return air to flow into the first path of return air after passing through the indoor evaporator;

the return air of the air source heat pump drying system comprises a first path of return air and a second path of return air.

2. The air-source heat pump drying system of claim 1, further comprising:

a heat recovery unit including a heat absorbing portion and a heat releasing portion, the heat absorbing portion being in heat exchange communication with the heat releasing portion;

the heat absorbing part is disposed in the first air flow path on the air inflow side of the indoor evaporator, and the heat discharging part is disposed in the first air flow path on the air outflow side of the indoor evaporator.

3. The air-source heat pump drying system of claim 2, wherein the heat absorbing part and/or the heat releasing part are/is arranged obliquely so as to turn the flowing direction of the air flowing through the heat absorbing part and/or the heat releasing part.

4. The air-source heat pump drying system of claim 2, wherein the heat recovery unit comprises a heat pipe heat exchanger, a wind-wind heat exchanger, or a wind-water-wind heat exchanger.

5. The air-source heat pump drying system of any one of claims 1 to 4, wherein the evaporator is located outside a refrigeration cycle unit, further comprising:

the auxiliary evaporator is arranged indoors and is communicated with the evaporator positioned outdoors in parallel;

and the valves are respectively arranged on the parallel branch of the auxiliary evaporator and the parallel branch of the outdoor evaporator, and the outdoor evaporator and/or the auxiliary evaporator are connected into the refrigeration cycle unit by controlling the opening or closing of the valves.

6. The air-source heat pump drying system of any one of claims 1 to 4, further comprising:

the main return air flow path is provided with a return air inflow end communicated with the drying area, and a return air outflow end communicated with a first inflow end of the first air flow path and a second inflow end of the second air flow path;

the main air supply flow path is communicated with the drying area, and an air supply inflow end is communicated with a first outflow end of the first air flow path and a second outflow end of the second air flow path;

wherein the plurality of condensers are located in the main air supply flow path.

7. A control method for the air source heat pump drying system of any one of claims 1 to 6, characterized by comprising:

determining a target operation mode according to the target drying material;

acquiring target operation parameters corresponding to the target operation mode according to a preset corresponding relation between the operation mode and the operation parameters;

and controlling the air source heat pump drying system to operate at the target operation parameter.

8. The control method according to claim 7, characterized by further comprising:

acquiring the air supply temperature;

under the condition that the air supply temperature does not fall into a target air supply temperature interval, acquiring the return air temperature and a first inlet air temperature of the air inlet side of the evaporator;

obtaining a dew point temperature according to the return air temperature;

under the condition that the first air inlet temperature is higher than a first preset temperature, controlling and increasing the return air quantity of a second path of return air in the second air flow path; wherein the first preset temperature is greater than the dew point temperature.

9. The control method of claim 7 wherein the operating modes include a full internal dehumidification mode of operation, a full external drying mode of operation, and a semi-internal dehumidification mode of operation, the operating parameters including a first proportion of first return air to total return air;

the first proportion corresponding to the complete internal dehumidification operation mode is 25-45%;

the first proportion corresponding to the semi-internal dehumidification operation mode is 15% -30%.

10. A control apparatus for an air source heat pump drying system, comprising a processor and a memory storing program instructions, wherein the processor is configured to perform the control method for an air source heat pump drying system of claim 7, 8 or 9 when executing the program instructions.