Refrigeration apparatus, control method therefor, control device, and storage medium

Abstract

A refrigeration device and a control method, control device and storage medium thereof. The refrigeration device comprises: a refrigeration system comprising a multi-stage compressor, a condenser, a throttling device and an evaporator connected in sequence, the multi-stage compressor comprising a plurality of compression modules connected in sequence, at least one compression module comprising a compression unit and a cooler, the cooler being located on the downstream side of the compression unit and being in communication with the compression unit, and each compression module comprising a compression unit; and a cooling system comprising a cooling flow path, an input end of the cooling flow path being connected to the evaporator and / or the condenser, and an output end of the cooling flow path being connected to the cooler, and being configured to deliver a cooling medium in the evaporator and / or the condenser to the cooler to reduce the superheat of the refrigerant discharged by the cooler. The present scheme can utilize the cooling medium in the system to cool the multi-stage compressor, without the need for an external cooling circulating water system, thereby facilitating the miniaturization of the refrigeration device and reducing costs.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration equipment, in particular to a refrigeration equipment, a control method and device thereof, and a computer readable storage medium. BACKGROUND

[0002] At present, with the increasing concern about the ozone layer destruction and greenhouse gas problems, in order to solve the climate threat caused by the growing market demand, countries around the world have accelerated the pace of new refrigerant research and development. In the centrifugal compressor water vapor refrigeration air conditioning industry, in the process of continuously increasing the pressure ratio, the size of the centrifugal compressor is also limited, which leads to the need to design multi-stage compression (i.e. multi-stage centrifugal compressor) for the centrifugal compressor. During the compression of the refrigerant by the multi-stage centrifugal compressor, the pressure and temperature of the refrigerant are continuously increased. The increase in pressure is our requirement, but the high temperature poses a big problem to the design and operation of the entire multi-stage centrifugal compressor, so the multi-stage centrifugal compressor needs to be cooled.

[0003] Most of the currently used cooling methods use external cooling circulating water systems for indirect cooling, which results in a large overall unit size and high cost. SUMMARY

[0004] The technical problem to be solved by the present application is to provide a refrigeration equipment which can use the cooling medium in the system to cool the multi-stage compressor, without the need for an external cooling circulating water system, thereby facilitating the miniaturization of the refrigeration equipment and reducing the cost.

[0005] The technical solution of the present application to solve the above technical problem is as follows: a refrigeration equipment, comprising: a refrigeration system, comprising a multi-stage compressor, a condenser, a throttling device and an evaporator connected in sequence from head to tail, the multi-stage compressor comprising a plurality of compression modules connected in sequence, at least one of the compression modules comprising a compression unit and a cooler, the cooler being located on the downstream side of the compression unit and being in communication with the compression unit, each of the compression modules comprising the compression unit; and a cooling system comprising a cooling flow path, the input end of the cooling flow path being connected to the evaporator and / or the condenser, the output end of the cooling flow path being connected to the cooler, and being configured to deliver the cooling medium in the evaporator and / or the condenser to the cooler to reduce the superheat of the refrigerant discharged by the cooler.

[0006] The refrigeration equipment provided by the embodiments of the present application is connected in sequence at the head and tail of a multi-stage compressor, a condenser, a throttling device and an evaporator to form a refrigeration cycle. High-temperature and high-pressure refrigerant discharged by the multi-stage compressor enters the condenser to be condensed, and then enters the evaporator after being throttled and depressurized by the throttling device. The refrigerant is evaporated and absorbs heat in the evaporator to become gaseous refrigerant, and flows back to the compressor. The evaporator can be an indoor heat exchanger, which cools the indoor environment by evaporating and absorbing indoor heat. The condenser can be an outdoor heat exchanger, which releases heat to the outdoor environment by condensing and releasing heat.

[0007] Since the temperature of the refrigerant in the evaporator and the temperature of the refrigerant in the condenser are both lower than the temperature of the refrigerant in the compressor, the embodiments of the present application use the cooling flow path to transport the cooling medium in the evaporator and / or the condenser to the cooler to cool the refrigerant discharged by the compression unit on the upstream side adjacent to the cooler. The temperature of the refrigerant discharged after being cooled by the cooler is reduced, thereby reducing the superheat of the refrigerant discharged by the compression module including the compression unit and the cooler, and avoiding the superheat of the refrigerant being too high to affect the normal operation of the subsequent compression module and the refrigeration equipment. Therefore, the refrigeration equipment can use the cooling medium in the system to cool the multi-stage compressor without an external cooling source, thereby facilitating the reduction of the volume and cost of the refrigeration equipment.

[0008] In addition, in the embodiments of the present application, the input end of the cooling flow path can be connected to the evaporator and / or the condenser, and the cooling medium can be directly extracted from the evaporator and / or the condenser. Since the evaporator and the condenser have a large volume and a large amount of internal cooling medium, the extraction of a certain amount of cooling medium has relatively small influence on the pressure of the refrigeration system. However, connecting the input end of the cooling flow path to the pipeline between the condenser and the evaporator has a relatively large influence on the pressure of the refrigeration system, and thus the present scheme is beneficial to improve the reliability of the refrigeration equipment.

[0009] On the basis of the above technical solutions, the present application can also be improved as follows.

[0010] In an exemplary embodiment, the cooler is a direct cooler, and the direct cooler is configured to perform contact heat exchange between the refrigerant discharged by the compression unit and the cooling medium transported by the cooling flow path.

[0011] In an exemplary embodiment, the cooler is an indirect cooler, the indirect cooler is provided with a first heat exchange flow channel and a second heat exchange flow channel, the first heat exchange flow channel is in communication with the adjacent compression unit, and an output end of the cooling flow channel is in communication with an input end of the second heat exchange flow channel; the cooling system further comprises a return branch, an input end of the return branch is in communication with an output end of the second heat exchange flow channel, and an output end of the return branch is connected to the evaporator and / or the condenser; the first heat exchange flow channel and the second heat exchange flow channel are arranged to separate the refrigerant discharged by the compression unit from the cooling medium transported by the cooling flow channel, so that the refrigerant discharged by the compression unit and the cooling medium transported by the cooling flow channel are in non-contact heat exchange.

[0012] In an exemplary embodiment, the indirect cooler is a phase-change cooler, or the indirect cooler is a non-phase-change cooler.

[0013] In an exemplary embodiment, each compression module comprises the compression unit and the cooler, the cooling flow channel comprises a plurality of parallel cooling branches, and the plurality of cooling branches are in one-to-one correspondence with the plurality of coolers.

[0014] In an exemplary embodiment, the cooling system further comprises a control valve arranged in the cooling flow channel and arranged to control the on-off and / or working parameters of the cooling flow channel.

[0015] In an exemplary embodiment, the refrigeration device further comprises a control device arranged to adjust the control valve according to the superheat degree of the refrigerant discharged by the compression unit adjacent to the upstream side of the cooler, so that the superheat degree of the refrigerant discharged by the cooler is within a set superheat degree range.

[0016] In an exemplary embodiment, the cooling system further comprises a pump body in communication with the cooling flow channel and arranged to pump the cooling medium in the evaporator and / or the condenser to the cooler.

[0017] In an exemplary embodiment, an input end of the cooling flow channel is connected to a bottom of the evaporator to transport the liquid cooling medium at the bottom of the evaporator to the cooler.

[0018] In an exemplary embodiment, the refrigeration system is a water refrigeration system, the compressor is a water vapor compressor, and the cooling medium is water; and / or, the refrigeration device is an air conditioner.

[0019] The embodiments of the present application also provide a control method, which is characterized in that the control method is used for the refrigeration device as described in any one of the above embodiments, and the control method comprises:

[0020] determining a degree of superheat of refrigerant discharged from the compression unit adjacent to an upstream side of the cooler;

[0021] adjusting on-off and / or operating parameters of the cooling flow path according to the degree of superheat of refrigerant discharged from the compression unit, so that the degree of superheat of refrigerant discharged from the cooler is within a set degree of superheat range.

[0022] In an exemplary embodiment, each of the compression modules includes the compression unit and the cooler, the cooling flow path includes a plurality of cooling branches in parallel connection, and the plurality of cooling branches are in one-to-one correspondence with the plurality of coolers; the determining of the degree of superheat of refrigerant discharged from the compression unit adjacent to an upstream side of the cooler includes determining the degree of superheat of refrigerant discharged from the compression unit adjacent to an upstream side of each of the coolers; and the adjusting of the on-off and / or operating parameters of the cooling flow path according to the degree of superheat of refrigerant discharged from the compression unit, so that the degree of superheat of refrigerant discharged from the cooler is within a set degree of superheat range, includes adjusting the on-off and / or operating parameters of the corresponding cooling branch according to the degree of superheat of refrigerant discharged from each of the compression units, so that the degree of superheat of refrigerant discharged from each of the coolers is within a set degree of superheat range.

[0023] The embodiments of the present application also provide a control device, including a processor and a memory storing a computer program, and the processor implements the steps of the control method according to the above embodiments when executing the computer program.

[0024] The embodiments of the present application also provide a computer readable storage medium, including a computer program, and the computer program implements the steps of the control method according to the above embodiments when executed by a processor. BRIEF DESCRIPTION OF DRAWINGS

[0025] Figure 1 A structural principle schematic diagram of a refrigeration device is provided for some embodiments of the present application;

[0026] Figure 2 A structural principle schematic diagram of a refrigeration device is provided for some embodiments of the present application;

[0027] Figure 3 A flowchart of a control method is provided for some embodiments of the present application;

[0028] Figure 4 A method principle schematic diagram of a control method is provided for some embodiments of the present application;

[0029] Figure 5 A method principle schematic diagram of a control method is provided for some embodiments of the present application.

[0030] In the drawings, the components represented by the numbers in the list are as follows:

[0031] 1 multi-stage compressor, 11 compression module, 12 compression unit, 121 first-stage compression unit, 122 second-stage compression unit, 13 cooler, 131 first-stage cooler, 132 second-stage cooler;

[0032] 2 condenser, 3 throttling device, 4 evaporator;

[0033] 51 cooling main branch, 52 cooling branch, 53 return branch;

[0034] 6 pump body;

[0035] 7 control valve, 71 first control valve, 72 second control valve.

[0036] wherein, Figure 1 and Figure 2 the arrows in the above figures show the flow direction of the refrigerant / cooling medium. DETAILED DESCRIPTION

[0037] The principles and features of the present application are described below in conjunction with the accompanying drawings, which are provided only for explanation of the present application and are not intended to limit the scope of the present application.

[0038] As shown in Figure 1 and Figure 2 , the present application provides a refrigeration device, comprising: a refrigeration system and a cooling system.

[0039] The refrigeration system comprises a multi-stage compressor 1, a condenser 2, a throttling device 3 and an evaporator 4 connected in sequence. The throttling device 3 can be but is not limited to an expansion valve. The multi-stage compressor 1 comprises a plurality of compression modules 11 connected in sequence. At least one compression module 11 comprises a compression unit 12 and a cooler 13, the cooler 13 being located on the downstream side of the compression unit 12 and being in communication with the compression unit 12. Each compression module 11 comprises a compression unit 12. The compression unit 12 can comprise a compression chamber and an impeller arranged in the compression chamber, the impeller being driven by a motor.

[0040] The cooling system comprises a cooling flow path. The input end of the cooling flow path is connected to the evaporator 4 and / or the condenser 2, and the output end of the cooling flow path is connected to the cooler 13, which is configured to deliver the cooling medium in the evaporator 4 and / or the condenser 2 to the cooler 13 to reduce the superheat of the refrigerant discharged by the cooler 13.

[0041] The refrigeration equipment provided by the embodiments of the present application is connected in sequence at the head and tail of a multi-stage compressor 1, a condenser 2, a throttling device 3 and an evaporator 4 to form a refrigeration cycle. High-temperature and high-pressure refrigerant discharged from the multi-stage compressor 1 enters the condenser 2 to be condensed, then enters the evaporator 4 after being throttled and decompressed by the throttling device 3, and is evaporated to become gaseous refrigerant in the evaporator 4 to flow back to the compressor. The evaporator 4 can be an indoor heat exchanger to cool the indoor environment by evaporating and absorbing indoor heat. The condenser 2 can be an outdoor heat exchanger to release heat to the outdoor environment by condensing and releasing heat.

[0042] Since the temperature of the refrigerant in the evaporator 4 and the temperature of the refrigerant in the condenser 2 are both lower than the temperature of the refrigerant in the compressor, the embodiments of the present application use the cooling flow path to transport the cooling medium in the evaporator 4 and / or the condenser 2 to the cooler 13 to cool the refrigerant discharged from the compression unit 12 on the upstream side adjacent to the cooler 13, so that the temperature of the refrigerant discharged after being cooled by the cooler 13 is reduced, thereby reducing the superheat of the refrigerant discharged from the compression module 11 including the compression unit 12 and the cooler 13, and avoiding that the superheat of the refrigerant is too high to affect the normal operation of the subsequent compression module 11 and the refrigeration equipment. Therefore, the refrigeration equipment can use the cooling medium in the system to cool the multi-stage compressor 1 without an external cooling source, thereby facilitating the reduction of the volume and the cost of the refrigeration equipment.

[0043] In addition, in the embodiments of the present application, the input end of the cooling flow path can be connected to the evaporator 4 and / or the condenser 2 to directly extract the cooling medium from the evaporator 4 and / or the condenser 2. Since the evaporator 4 and the condenser 2 have a large volume and contain a large amount of cooling medium, the extraction of a certain amount of cooling medium has a relatively small impact on the pressure of the refrigeration system. However, connecting the input end of the cooling flow path to the pipeline between the condenser 2 and the evaporator 4 has a relatively large impact on the pressure of the refrigeration system, and thus the present scheme is beneficial to improve the reliability of the refrigeration equipment.

[0044] In some exemplary embodiments, the refrigeration system is a water refrigeration system, the compressor is a water vapor compressor, and the cooling medium is water.

[0045] Due to the particularity of the properties of water vapor refrigerant, the specific volume is large, the pressure ratio is large, the pressure difference is small, and the temperature after compression is high, which brings great difficulties to the design and operation of the entire refrigeration system, and thus inter-stage cooling is required between each two stages of the multi-stage compressor 1. Most of the commonly used cooling methods currently use external cooling water for indirect cooling, which results in a large overall unit volume. Therefore, some manufacturers give up water vapor refrigerant and use conventional refrigerants, which affects the popularization and use of water vapor refrigerant.

[0046] The refrigeration system provided by the embodiment of the present application uses water, a natural refrigerant, as the refrigerant to perform cycle refrigeration, and does not need to externally connect a cooling water circulation system to cool the multi-stage centrifugal compressor, effectively solving the industry pain point of the water refrigeration system in the related art, and being conducive to the popularization and use of water vapor refrigerant.

[0047] In some exemplary embodiments, as shown in Figure 1 and Figure 2 The input end of the cooling flow path is connected to the bottom of the evaporator 4 to deliver the liquid cooling medium at the bottom of the evaporator 4 to the cooler 13.

[0048] Compared with the condenser 2, the refrigerant in the evaporator 4 has a lower temperature, and therefore, cooling the refrigerant in the cooler 13 by using the cooling medium in the evaporator 4 can reduce the amount of the cooling medium, which is conducive to reducing the flow of the cooling flow path.

[0049] For the scheme in which the multi-stage compressor 1 is a water vapor compressor, the evaporator 4 can be a flooded evaporator. During the operation of the flooded evaporator, the upper part is water vapor, and the lower part is water, so the input end of the cooling flow path is connected to the bottom of the evaporator 4, which can deliver the cooling water at the bottom of the evaporator 4 to the cooler 13, thereby achieving a good cooling effect and not easily causing a change in the evaporation pressure in the evaporator 4, and thus being conducive to reliable operation of the evaporator 4.

[0050] Of course, the input end of the cooling flow path can also be connected to the bottom of the condenser 2 to deliver the liquid cooling medium at the bottom of the condenser 2 to the cooler 13.

[0051] Alternatively, the input end of the cooling flow path can also be connected to the bottom of the evaporator 4 and the bottom of the condenser 2 to deliver the liquid cooling medium at the bottom of the evaporator 4 and the condenser 2 to the cooler 13.

[0052] In some exemplary embodiments, the cooler 13 is a direct cooler 13, as shown in Figure 1 The direct cooler 13 is configured to cause the refrigerant discharged by the compression unit 12 into the cooler 13 to contact the cooling medium delivered by the cooling flow path into the cooler 13 to perform contact heat exchange.

[0053] In the present scheme, the refrigerant discharged by the compression unit 12 adjacent to the upstream side of the cooler 13 enters the cooler 13, and the cooling medium delivered by the cooling flow path also enters the cooler 13. The refrigerant discharged by the compression unit 12 directly contacts the cooling medium delivered by the cooling flow path to exchange heat, and becomes refrigerant with a temperature lower than that of the refrigerant discharged by the compression unit 12, and is discharged from the cooler 13. The refrigerant discharged by the compression unit 12 and the cooling medium delivered by the cooling flow path have the same composition but different physical states, and can be cooled by direct contact. In addition, the amount of refrigerant output by the compression module 11 is also increased.

[0054] For example, the refrigerant discharged by the compression unit 12 is gaseous medium, and the cooling medium delivered by the cooling flow path is liquid medium. The direct-type cooler 13 can also be provided with a spraying device, and the end of the cooling flow path can also be provided with an atomizing device connected to the spraying device. The atomizing device atomizes the liquid cooling medium and sprays it into the cooler 13 in the form of water mist, which is beneficial to increasing the contact area between the refrigerant discharged by the compression unit 12 and the cooling medium delivered by the cooling flow path, thereby improving the heat exchange effect. In addition, the atomized cooling medium can realize flash evaporation effect after contacting with the high-temperature and high-pressure gaseous cooling medium, thereby reducing the superheat of the refrigerant discharged by the compression module 11.

[0055] In other exemplary embodiments, the cooler 13 is an indirect-type cooler 13, as shown in Figure 2 The indirect-type cooler 13 is provided with a first heat exchange flow path and a second heat exchange flow path. The first heat exchange flow path is in communication with the adjacent compression unit 12. The output end of the cooling flow path is in communication with the input end of the second heat exchange flow path. The cooling system further comprises a return branch 53, the input end of the return branch 53 is in communication with the output end of the second heat exchange flow path, and the output end of the return branch 53 is connected to the evaporator 4 and / or the condenser 2.

[0056] The first heat exchange flow path and the second heat exchange flow path are arranged to separate the refrigerant discharged by the compression unit 12 from the cooling medium delivered by the cooling flow path, so that the refrigerant discharged by the compression unit 12 and the cooling medium delivered by the cooling flow path exchange heat in a non-contact manner.

[0057] In the scheme, the refrigerant discharged by the compression unit 12 adjacent to the upstream side of the cooler 13 enters the first heat exchange flow channel of the cooler 13, and the cooling medium conveyed by the cooling flow path enters the second heat exchange flow channel of the cooler 13. The refrigerant discharged by the compression unit 12 and the cooling medium conveyed by the cooling flow path are separated and cannot contact each other, and can only perform non-contact heat exchange, so that the refrigerant in the first heat exchange flow channel is lowered in temperature and then discharged by the cooler 13; and the cooling medium in the second heat exchange flow channel absorbs heat and then flows back to the evaporator 4 and / or the condenser 2 through the backflow branch 53. The refrigerant discharged by the compression unit 12 and the cooling medium conveyed by the cooling flow path are the same in composition and can be different in physical state.

[0058] The first heat exchange flow channel and the second heat exchange flow channel only separate the refrigerant discharged by the compression unit 12 and the cooling medium conveyed by the cooling flow path, and the specific shape of the first heat exchange flow channel and the second heat exchange flow channel is not limited. Correspondingly, the types of the indirect cooler 13 are also various, such as a jacket heat exchanger, a plate heat exchanger, or other types of indirect heat exchangers.

[0059] In some embodiments, the indirect cooler 13 is a phase change cooler 13, that is, the cooling medium conveyed by the cooling flow path will undergo a phase change in the cooler 13. Since the latent heat of phase change is large, the heat exchange efficiency is much higher than that of non-phase change. Therefore, the scheme is beneficial to reduce the demand for cooling medium and reduce the flow of the cooling flow path.

[0060] The phase change cooler 13 can be matched with a throttling component to realize phase change, such as a throttling component (such as an expansion valve, a capillary tube, etc.) arranged on the cooling flow path, so that the cooling medium is throttled and depressurized to enter the cooler 13 to undergo a phase change.

[0061] In other embodiments, the indirect cooler 13 is a non-phase change cooler 13, that is, the cooling medium conveyed by the cooling flow path does not undergo a phase change in the cooler 13, and heat exchange is realized by temperature difference. The non-phase change cooler 13 can be matched with a flow valve to adjust the flow to adjust the heat exchange effect.

[0062] In some exemplary embodiments, each compression module 11 includes a compression unit 12 and a cooler 13, as shown in Figure 1 and Figure 2 The cooling flow path includes a plurality of cooling branches 52 in parallel, and the plurality of cooling branches 52 are in one-to-one correspondence with the plurality of coolers 13.

[0063] In this way, the superheat degree of the refrigerant discharged by each compression module 11 can be effectively adjusted, achieving good inter-stage cooling effect, which is conducive to reducing the compression load of the subsequent compression module 11, ensuring that the subsequent compression module 11 can be normally compressed, and also enabling the refrigerant finally discharged by the multi-stage compressor 1 to be within a suitable superheat degree range, thereby improving the overall efficiency of the machine.

[0064] In some exemplary embodiments, the cooling system further comprises a pump body 6, which is in communication with the cooling flow path and is arranged to pump the cooling medium in the evaporator 4 and / or the condenser 2 to the cooler 13, as shown in Figure 1 and Figure 2

[0065] For the scheme in which the cooling flow path comprises a plurality of parallel cooling branches 52, the number of pump bodies 6 can be one or multiple. For example, one pump body 6 can be arranged for each cooling branch 52. Alternatively, the cooling flow path further comprises a cooling main path 51 located on the upstream side of the plurality of cooling branches 52, and only one pump body 6 is arranged on the cooling main path 51, as shown in Figure 1 and Figure 2

[0066] In some exemplary embodiments, the cooling system further comprises a control valve 7, which is arranged in the cooling flow path and is arranged to control the on-off and / or working parameters (such as flow rate, flow speed, etc.) of the cooling flow path, as shown in Figure 1 and Figure 2

[0067] In this way, the superheat degree of the refrigerant discharged by each compression module 11 can be effectively adjusted, achieving good inter-stage cooling effect, which is conducive to reducing the compression load of the subsequent compression module 11, ensuring that the subsequent compression module 11 can be normally compressed, and also enabling the refrigerant finally discharged by the multi-stage compressor 1 to be within a suitable superheat degree range, thereby improving the overall efficiency of the machine.

[0068] For the scheme in which the cooling flow path comprises a plurality of parallel cooling branches 52, the number of pump bodies 6 can be one or multiple. For example, one pump body 6 can be arranged for each cooling branch 52. Alternatively, the cooling flow path further comprises a cooling main path 51 located on the upstream side of the plurality of cooling branches 52, and only one pump body 6 is arranged on the cooling main path 51, as shown in Figure 1 and Figure 2

[0069] In this way, the superheat degree of the refrigerant discharged by each compression module 11 can be effectively adjusted, achieving good inter-stage cooling effect, which is conducive to reducing the compression load of the subsequent compression module 11, ensuring that the subsequent compression module 11 can be normally compressed, and also enabling the refrigerant finally discharged by the multi-stage compressor 1 to be within a suitable superheat degree range, thereby improving the overall efficiency of the machine.

[0070] In some exemplary embodiments, the cooling system further comprises a control valve 7, which is arranged in the cooling flow path and is arranged to control the on-off and / or working parameters (such as flow rate, flow speed, etc.) of the cooling flow path, as shown in ​​​​

[0071] The superheat degree of the refrigerant discharged by the compression unit 12 can be determined according to the refrigerant temperature and the refrigerant pressure at the outlet of the compression unit 12. The superheat degree of the refrigerant discharged by the cooler 13 can be determined according to the refrigerant temperature and the refrigerant pressure at the outlet of the cooler 13.

[0072] As shown in Figure 3 The application also provides a control method for the refrigeration device, the control method comprising:

[0073] Step S202: determining the superheat degree of the refrigerant discharged by the compression unit adjacent to the upstream side of the cooler;

[0074] Step S204: adjusting the on-off and / or working parameter of the cooling flow path according to the superheat degree of the refrigerant discharged by the compression unit, so that the superheat degree of the refrigerant discharged by the cooler is within the set superheat degree range.

[0075] This facilitates automatic control of the superheat degree of the refrigerant discharged by the cooler 13, so that the superheat degree of the refrigerant discharged by the cooler 13 can be within a suitable superheat degree range, thereby ensuring normal operation of the multi-stage compressor 1 and the refrigeration device.

[0076] In some exemplary embodiments, the cooling system further comprises a control valve 7 arranged in the cooling flow path and configured to control the on-off and / or working parameter of the cooling flow path.

[0077] Adjusting the on-off and / or working parameter of the cooling flow path according to the superheat degree of the refrigerant discharged by the compression unit 12 comprises controlling the control valve 7 according to the superheat degree of the refrigerant discharged by the compression unit 12, so as to adjust the on-off and / or working parameter of the cooling flow path.

[0078] This facilitates reasonable control of the superheat degree of the refrigerant discharged by the cooler 13 through the control valve 7 as needed, so that the superheat degree of the refrigerant discharged by the cooler 13 can be within a suitable superheat degree range.

[0079] In some exemplary embodiments, each compression module 11 comprises a compression unit 12 and a cooler 13. The cooling flow path comprises a plurality of cooling branches 52 connected in parallel, and the plurality of cooling branches 52 are in one-to-one correspondence with the plurality of coolers 13.

[0080] Determining the superheat degree of the refrigerant discharged by the compression unit 12 adjacent to the upstream side of the cooler 13 comprises determining the superheat degree of the refrigerant discharged by the compression unit 12 adjacent to the upstream side of each cooler 13.

[0081] The on-off and / or working parameters of the cooling flow path are adjusted according to the superheat degree of the refrigerant discharged by each compression unit 12, so that the superheat degree of the refrigerant discharged by each cooler 13 is within the set superheat degree range.

[0082] In this way, the superheat degree of the refrigerant discharged by each compression module 11 can be effectively and automatically adjusted, achieving good inter-stage cooling effect, which is conducive to reducing the compression load of the subsequent compression module 11, ensuring that the subsequent compression module 11 can normally compress, and also enabling the refrigerant finally discharged by the multi-stage compressor 1 to be within a suitable superheat degree range, so as to improve the overall efficiency of the machine.

[0083] In some exemplary embodiments, adjusting the on-off and / or working parameters of the corresponding cooling flow path according to the superheat degree of the refrigerant discharged by each compression unit 12 includes adjusting the control valve 7 on the corresponding cooling branch 52 according to the superheat degree of the refrigerant discharged by each compression unit 12, so as to adjust the on-off and / or working parameters of the corresponding cooling branch 52.

[0084] In some exemplary embodiments, the set superheat degree range is within the range of 2℃ to 5℃.

[0085] Of course, the set superheat degree range is not limited to the above range, and can be adjusted as needed.

[0086] Among them, the refrigeration equipment provided by the embodiments of the present application can be but is not limited to an air conditioner. The multi-stage compressor 1 can be a two-stage compressor, or can be a more-stage compressor 1. The working principle of the refrigeration equipment will be described below taking the refrigeration equipment as an air conditioner and the compressor as a two-stage compressor as an example.

[0087] As Figure 1 and Figure 2As shown, the air conditioner of the embodiment is a natural refrigerant water refrigeration air conditioning system. The refrigeration device mainly comprises: a primary compression unit 121, a secondary compression unit 122, a primary cooler 131 (i.e. a cooler 13 located on the downstream side of the primary compression unit 121 and adjacent to the primary compression unit 121), a secondary cooler 132 (i.e. a cooler 13 located on the downstream side of the secondary compression unit 122 and arranged adjacent to the second compression unit 12), an evaporator 4, a condenser 2, a throttling device 3, a water pump, a control valve 7 and the like. The primary compression unit 121 and the primary cooler 131 constitute a primary compression module, and the secondary compression unit 122 and the secondary cooler 132 constitute a secondary compression module. The primary compression module and the secondary compression module are two compression modules 11 of a two-stage compressor, and the primary compression module is a primary compression module 11. The secondary compression module is located on the downstream side of the primary compression module and is a final compression module 11.

[0088] The refrigeration system further comprises a cooling main circuit 51, two parallel cooling branch circuits 52 and two control valves 7 (a first control valve 71 and a second control valve 72) respectively arranged in the two cooling branch circuits 52. The water pump is arranged in the cooling main circuit 51. One of the cooling flow paths is the cooling main circuit 51 and the cooler 13. The other cooling flow path communicates the cooling main circuit 51 and the secondary cooler 132.

[0089] The evaporator 4 is a flooded evaporator, which mainly evaporates liquid water, absorbs the heat of the room, and makes the room achieve the effect of cooling. The evaporator 4 evaporates and absorbs part of the heat of the water, and the evaporated water vapor flows into the two-stage centrifugal compressor through the outlet of the evaporator 4. The two-stage centrifugal compressor mainly compresses the water vapor generated by the evaporator 4 to raise the pressure of the water vapor to the required working pressure. The primary cooler 131 and the secondary cooler 132 respectively cool the superheated water vapor compressed by the primary compression unit 121 and the secondary compression unit 122 to keep the superheat degree between 2°C and 5°C. The condenser 2 mainly condenses the water vapor discharged by the two-stage compressor, exchanges the heat of the water vapor to the outdoor, and condenses the water vapor into subcooled water, which flows out of the condenser 2. The throttling device 3 mainly reduces the pressure of the subcooled water generated by the condenser 2 to the pressure condition of the evaporation temperature, so that it flows into the evaporator 4 to evaporate and reach the expected evaporation temperature and the expected refrigeration effect.

[0090] The primary cooler 131 and the secondary cooler 132 mainly cool the water vapor compressed by the primary compression unit 121 and the secondary compression unit 122 by introducing cold water from the bottom of the evaporator 4. The cooler 13 can have two embodiments.

[0091] As shown in FIG. 1, the primary cooler 131 and the secondary cooler 132 are arranged on the downstream side of the primary compression unit 121 and the secondary compression unit 122, respectively. Figure 1As shown, the first embodiment is direct contact cooling, i.e., the cooler 13 is a direct cooler 13, which uses cold water to reduce the pressure flash evaporation and mix with the superheated water vapor to reduce the superheat. The principle is to pressurize the cold water by a water pump to form a certain pressure of cold water, and then the high-pressure cold water is converted into water mist by the control valve 7 and the atomizing device and sprayed into the cooler 13, the water mist absorbs heat and evaporates, absorbs a large amount of heat of the water vapor, reduces the superheat of the water vapor, and controls the superheat at 2-5°C, and then enters the secondary compression unit 122 to increase the pressure of the water vapor again, and the superheat of the compressed water vapor is reduced again by the same method. The cooling water is supplemented by the evaporator 4, and in the entire system, the cooling water circulates and cools, and reaches dynamic balance with the entire system.

[0092] As shown in FIG. 1, Figure 2 The second embodiment is indirect cooling, i.e., the cooler 13 is an indirect cooler 13. Indirect cooling can also be divided into two types, one is water vapor evaporation indirect cooling (i.e., phase change cooling), and the other is non-evaporation indirect cooling (i.e., non-phase change cooling). The cold water is drawn from the bottom of the evaporator 4, the flow is adjusted by the water pump and the control valve 7, and the water vapor is cooled to 2-5°C by the jacketed heat exchanger, the plate heat exchanger or other types of indirect heat exchanger. If it is evaporation indirect cooling, the control valve 7 can be an expansion valve, and at this time the flow can be small due to the large latent heat of evaporation of water. If it is non-evaporation indirect cooling, the control valve 7 can be a flow valve, and at this time the flow is large. The flow is dynamically adjusted according to the superheat of the two compression units 12 until it is within the preset superheat range.

[0093] The condenser 2 mainly condenses the water vapor at the outlet of the two-stage compression unit 12 after inter-stage cooling, and a subcooling section is also provided at the tail of the condenser 2 to further cool the saturated liquid to become subcooled water, which is not limited in form and can be a finned tube condenser 2, a spray condenser 2, a jacketed condenser 2, etc.

[0094] The throttling device 3 mainly reduces the pressure of the high-pressure subcooled water at the outlet of the condenser 2. Since the water refrigeration system is operated in a negative pressure environment, the pressure difference is very small, so the form of the throttling device 3 is not limited to an expansion valve, a hole baffle, a liquid level column, a capillary tube, etc.

[0095] As shown in FIG. 1, Figure 1 and Figure 2As shown, during the whole system operation, the flooded evaporator 4 evaporates, part of which absorbs the heat in the room, and part of which absorbs the heat of the remaining water, at this time, it shows the state of upper gas and lower liquid, the water vapor flows out from the upper outlet of the evaporator 4, at this time, the pressure and temperature of the refrigerant are P1 and T1, and T1 should have a certain superheat. Then the water vapor flows into the primary compression unit 121, and the water vapor is compressed by the primary compression unit 121, and after compression, it is discharged from the primary compression unit 121, at this time, the pressure and temperature of the water vapor are increased to P2 and T2. At this time, the superheat of the water vapor is high, in order to ensure the normal compression in the following, it is necessary to reduce the temperature, at this time, the cold water in the bottom of the evaporator 4 is introduced, and the superheat is reduced to the preset range by the water pump and the control valve 7 using the direct spray flash evaporation form of embodiment one or the indirect cooling form of embodiment two, the preset range can be 2-5℃, at this time, the pressure and temperature of the water vapor are P2 and T3 (T3 < T2). After reduction, it flows into the secondary compression unit 122, and after passing through the secondary compression unit 122, the pressure and temperature continue to increase to P3 and T4, at this time, the pressure reaches the target design pressure, and the temperature superheat is large, and the same form is adopted, the cold water in the bottom of the evaporator 4 is introduced, and the superheat is reduced to the preset range by the water pump and the control valve 7 using the direct spray flash evaporation form of embodiment one or the indirect cooling form of embodiment two, the preset range can be 2-5℃, at this time, the pressure and temperature of the water vapor are P3 and T5 (T5 < T4). Then it flows into the condenser 2 to be condensed into liquid water, and then the liquid water is further supercooled into supercooled water (pressure and temperature are T6 and P6). The supercooled water flows into the evaporator 4 after pressure reduction by the throttling device 3, evaporates in the evaporator 4, and then continues to flow into the multi-stage compressor 1, thereby completing the refrigeration cycle.

[0096] The working process principle of the refrigeration equipment using the cooler 13 of embodiment one is as shown in Figure 4 The working process principle of the refrigeration equipment using the cooler 13 of embodiment one is as shown in Figure 5

[0097] Therefore, the refrigeration equipment and the control method thereof provided in the embodiments of the present application, the inter-stage cooling scheme of the multi-stage compressor adopts a system closed cooling scheme, without the need of an external cooling source, the cooling water adopts the cold water in the bottom of the system evaporator, and the superheat of the water vapor after compression of the primary compression unit and the secondary compression unit is reduced by using methods such as direct contact spray flash evaporation cooling, indirect evaporation cooling or indirect non-evaporation cooling, the system has good integrity, stable operation, high efficiency and good cooling effect. The inter-stage cooling scheme can reduce the size and cost of the whole unit, and improve the overall efficiency of the system.

[0098] ​The embodiment of the present application further provides a control device, comprising a processor and a memory storing a computer program, and the processor implements the steps of the control method of the above embodiment when executing the computer program, thus having all the beneficial effects of the above, which will not be repeated here.

[0099] The processor can be an integrated circuit chip having a processing capability of signals. The processor can be a general processor, including a central processing unit (CPU), a network processor (NP), etc.; or can be a digital signal processor (DSP), an application specific integrated circuit (ASIC), a field programmable gate array (FPGA) or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components. The disclosed methods, steps and logical block diagrams in the embodiments of the present application can be implemented or executed by the processor. The general processor can be a microprocessor or the processor can also be any conventional processor.

[0100] The embodiment of the present application further provides a computer readable storage medium, comprising a computer program, and the computer program is executed by the processor to implement the steps of the control method of the above embodiment, thus having all the beneficial effects of the above, which will not be repeated here.

[0101] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application.

[0102] In addition, the terms "first", "second" are only for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined with "first", "second" can explicitly or implicitly include at least one of the features. In the description of the present application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise specifically limited.

[0103] In the present application, unless specifically defined otherwise, the terms "mounting", "connected", "connecting", "fixed", "fixedly connected" and the like should be understood broadly, for example, can be fixedly connected, or can be detachably connected, or can be integrated; can be mechanically connected, or can be electrically connected; can be directly connected, or can be indirectly connected through an intermediate medium; can be the internal communication of two elements or the interaction relationship between two elements, unless specifically defined otherwise. For those skilled in the art, the specific meanings of the above terms in the present application can be understood according to the specific circumstances.

[0104] In the present application, unless specifically defined otherwise, the first feature is "on" or "under" the second feature can be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature "above", "over" and "on" the second feature can be that the first feature is directly above or obliquely above the second feature, or only indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature "below", "under" and "under" the second feature can be that the first feature is directly below or obliquely below the second feature, or only indicates that the horizontal height of the first feature is less than that of the second feature.

[0105] In the description of the present application, the description of the terms "one embodiment", "some embodiments", "example", "specific example" or "some examples" means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present application, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any appropriate manner in any one or more embodiments or examples. In addition, different embodiments or examples described in the present application and the features of different embodiments or examples can be combined and combined by those skilled in the art without contradiction.

[0106] Although the embodiments of the present application have been shown and described above, it can be understood that the above embodiments are exemplary and cannot be understood as limiting the present application, and those skilled in the art can make changes, modifications, replacements and variations to the above embodiments within the scope of the present application.

[0107] In any one or more of the example embodiments described above, the functions described can be implemented in hardware, software, firmware, or any combination thereof. If implemented in software, the functions can be stored on or transmitted over as one or more instructions or code on a computer-readable medium and executed by a hardware-based processing unit. Computer-readable media can include computer-readable storage media, which corresponds to a tangible medium such as data storage media, or communication media including any medium that facilitates transfer of a computer program from one place to another, e.g., according to a communication protocol. In this manner, computer- readable media generally can correspond to non-transitory computer- readable storage media or communication media (e.g., electromagnetic signals, radio waves, etc.). Data storage media can be any available media that can be accessed by one or more computers or one or more processors to retrieve instructions, code, and / or data structures for implementation of the techniques described in this disclosure. A computer program product can include a computer-readable medium.

[0108] By way of example, and not limitation, such computer-readable storage media can include RAM, ROM, EEPROM, CD-ROM or other optical disk storage, magnetic disk storage, or other magnetic storage devices, flash memory, or any other storage medium that can be used to store desired program code in the form of instructions or data structures and that can be accessed by a computer. Also, any

[0109] Instructions can be executed by one or more processors, such as one or more digital signal processors (DSPs), general purpose microprocessors, application specific integrated circuits (ASICs), field programmable logic arrays (FPGAs), or other equivalent integrated or discrete logic circuitry. Accordingly, the term "processor," as used herein can refer to any of the foregoing structure or any other structure suitable for implementation of the techniques described herein. In addition, in some aspects, the functionality described herein can be provided within dedicated hardware and / or software modules configured for encoding and decoding, or incorporated in a combined codec. Also, the techniques could be fully implemented in one or more circuits or logic elements.

[0110] The technical solutions of the embodiments of the present disclosure can be implemented in a wide variety of devices or apparatuses, including a wireless mobile phone, an integrated circuit (IC) or a set of ICs (e.g., a chip set). Various components, modules, or units described in the embodiments of the present disclosure can be configured to implement functions of the apparatus configured to perform the described techniques, but are not necessarily required to be implemented by different hardware units. Rather, as described above, the various units can be combined in a codec hardware unit or provided by a set of one or more processors, including the one or more processors described above, in connection with suitable software and / or firmware.

Claims

1. A refrigeration device, characterized in that, include: A refrigeration system includes a multi-stage compressor, a condenser, a throttling device, and an evaporator connected in sequence. The multi-stage compressor includes multiple compression modules connected in sequence. At least one compression module includes a compression unit and a cooler. The cooler is located downstream of the compression unit and communicates with the compression unit. Each compression module includes the compression unit. and A cooling system, including a cooling flow path, wherein the input end of the cooling flow path is connected to the evaporator and / or the condenser, and the output end of the cooling flow path is connected to the cooler, configured to deliver a cooling medium in the evaporator and / or the condenser to the cooler to reduce the superheat of the refrigerant discharged from the cooler; The cooler is an indirect cooler, which includes a first heat exchange channel and a second heat exchange channel. The first heat exchange channel is connected to the adjacent compression unit, and the output end of the cooling channel is connected to the input end of the second heat exchange channel. The cooling system also includes a return branch, the input end of which is connected to the output end of the second heat exchange channel, and the output end of which is connected to the evaporator and / or the condenser. The first and second heat exchange channels are configured to separate the refrigerant discharged from the compression unit from the cooling medium transported by the cooling channel, allowing the refrigerant discharged from the compression unit to exchange heat with the cooling medium transported by the cooling channel in a non-contact manner. The input end of the cooling flow path is connected to the bottom of the evaporator to deliver the liquid cooling medium at the bottom of the evaporator to the cooler.

2. The refrigeration equipment according to claim 1, characterized in that, The indirect cooler is a phase change cooler; or, the indirect cooler is a non-phase change cooler.

3. The refrigeration equipment according to claim 1 or 2, characterized in that, Each of the compression modules includes the compression unit and the cooler. The cooling flow path includes multiple parallel cooling branches, and each of the multiple cooling branches is connected to a corresponding cooler.

4. The refrigeration equipment according to claim 1 or 2, characterized in that, The cooling system also includes: A control valve is located in the cooling flow path and is configured to control the on / off state and / or operating parameters of the cooling flow path.

5. The refrigeration equipment according to claim 4, characterized in that, Also includes: The control device is configured to adjust the control valve according to the superheat of the refrigerant discharged from the compression unit adjacent to the upstream side of the cooler, so that the superheat of the refrigerant discharged from the cooler is within a set superheat range.

6. The refrigeration equipment according to claim 1 or 2, characterized in that, The cooling system also includes: The pump body is connected to the cooling flow path and is configured to pump the cooling medium in the evaporator and / or the condenser to the cooler.

7. The refrigeration equipment according to claim 1 or 2, characterized in that, The refrigeration system is a water-cooled system, the compressor is a steam compressor, and the cooling medium is water; and / or The refrigeration equipment is an air conditioner.

8. A control method, characterized in that, For a refrigeration device as described in any one of claims 1 to 7, the control method comprises: Determine the superheat of the refrigerant discharged from the compression unit adjacent to the upstream side of the cooler; Adjust the on / off state and / or operating parameters of the cooling flow path according to the superheat of the refrigerant discharged from the compression unit, so that the superheat of the refrigerant discharged from the cooler is within the set superheat range.

9. The control method according to claim 8, characterized in that, Each of the compression modules includes the compression unit and the cooler. The cooling flow path includes multiple parallel cooling branches, and each of the multiple cooling branches is connected to a corresponding cooler. Determining the superheat of the refrigerant discharged from the compression unit adjacent to the upstream side of the cooler includes: determining the superheat of the refrigerant discharged from the compression unit adjacent to the upstream side of the cooler; The step of adjusting the on / off state and / or operating parameters of the cooling flow path according to the superheat of the refrigerant discharged from the compression unit, so that the superheat of the refrigerant discharged from the cooler is within a set superheat range, includes: adjusting the on / off state and / or operating parameters of the corresponding cooling branch according to the superheat of the refrigerant discharged from each compression unit, so that the superheat of the refrigerant discharged from each cooler is within a set superheat range.

10. A control device, characterized in that, It includes a processor and a memory storing a computer program, wherein the processor executes the computer program to implement the steps of the control method as described in claim 8 or 9.

11. A computer-readable storage medium comprising a computer program, characterized in that, When the computer program is executed by the processor, it implements the steps of the control method as described in claim 8 or 9.

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