CN117366898A - Refrigerating device and control method thereof - Google Patents

Refrigerating device and control method thereof Download PDF

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Publication number
CN117366898A
CN117366898A CN202210772024.3A CN202210772024A CN117366898A CN 117366898 A CN117366898 A CN 117366898A CN 202210772024 A CN202210772024 A CN 202210772024A CN 117366898 A CN117366898 A CN 117366898A
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CN
China
Prior art keywords
temperature
low
stage
stage compressor
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202210772024.3A
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Chinese (zh)
Inventor
刘煜森
孙永升
赵向辉
李大伟
郑皓宇
张书锋
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Qingdao Haier Special Refrigerator Co Ltd
Qingdao Haier Smart Technology R&D Co Ltd
Haier Smart Home Co Ltd
Original Assignee
Qingdao Haier Special Refrigerator Co Ltd
Qingdao Haier Smart Technology R&D Co Ltd
Haier Smart Home Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Qingdao Haier Special Refrigerator Co Ltd, Qingdao Haier Smart Technology R&D Co Ltd, Haier Smart Home Co Ltd filed Critical Qingdao Haier Special Refrigerator Co Ltd
Priority to CN202210772024.3A priority Critical patent/CN117366898A/en
Publication of CN117366898A publication Critical patent/CN117366898A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/025—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures using primary and secondary refrigeration systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

The invention provides a refrigerating device and a control method thereof, wherein the refrigerating device comprises a box body, a controller, a high-temperature-stage refrigerating circulation loop and a low-temperature-stage refrigerating circulation loop, the high-temperature-stage refrigerating circulation loop comprises a high-temperature-stage compressor, a high-temperature-stage evaporator and an evaporation part, a first refrigerant circulates in the high-temperature-stage refrigerating circulation loop, and the high-temperature-stage compressor is a variable-frequency compressor; the low-temperature-stage refrigeration cycle loop comprises a low-temperature-stage compressor and a condensation part, wherein a second refrigerant flows in the low-temperature-stage refrigeration cycle loop, and the second refrigerant flowing through the condensation part exchanges heat with the first refrigerant flowing through the evaporation part; the high-temperature-stage refrigeration cycle loop is used for cooling a first storage compartment in the box body, and the low-temperature-stage refrigeration cycle loop is used for cooling a second storage compartment in the box body; the controller is used for controlling the rotating speed of the high-temperature-level compressor according to the temperature in the second storage compartment when the low-temperature-level compressor is started. The invention can avoid the overlarge operation pressure of the refrigerating system when the low-temperature-level compressor is started.

Description

Refrigerating device and control method thereof
Technical Field
The invention relates to the technical field of refrigeration equipment, in particular to a refrigeration device and a control method of the refrigeration device.
Background
Along with the improvement of the living standard of people, the transportation is more and more convenient, the concept of healthy life is deep in the mind, food materials in different areas and even different countries gradually enter market supermarkets and enter home dining tables, but the storage conditions and the fresh-keeping requirements of different food materials are different, and even the freshness of the food materials can be changed along with the change of the storage conditions, so that the food materials are required to be stored in different temperature areas in a classified mode.
Many refrigeration devices having storage compartments with different storage temperatures are currently on the market, however, the operating pressure of the refrigeration system is excessive due to the large amount of cooling required for the storage compartments with lower temperature zones.
Disclosure of Invention
In order to solve the technical problems, the invention aims to provide a refrigerating device and a control method of the refrigerating device, so as to solve the problem that the operating pressure of a refrigerating system is large when the existing refrigerating device supplies cold to a storage compartment in a low-temperature area.
In order to achieve one of the above objects, an embodiment of the present invention provides a refrigeration apparatus, comprising,
the high-temperature-stage refrigeration cycle loop comprises a high-temperature-stage compressor, a high-temperature-stage evaporator and an evaporation part, wherein a first refrigerant flows in the high-temperature-stage refrigeration cycle loop, and the high-temperature-stage compressor is a variable-frequency compressor;
the low-temperature-stage refrigeration cycle loop comprises a low-temperature-stage compressor, a low-temperature-stage evaporator and a condensation part, wherein a second refrigerant flows in the low-temperature-stage refrigeration cycle loop, and the second refrigerant flowing through the condensation part exchanges heat with the first refrigerant flowing through the evaporation part;
the box body is provided with a first storage compartment and a second storage compartment, the high-temperature-level refrigeration cycle loop is used for cooling the first storage compartment, and the low-temperature-level refrigeration cycle loop is used for cooling the second storage compartment;
the controller is respectively connected with the high-temperature-level compressor and the low-temperature-level compressor and is used for controlling the temperature T in the second storage compartment according to the starting time of the low-temperature-level compressor 2 And controlling the rotating speed Rg of the high-temperature-stage compressor.
As a further improvement of an embodiment of the present invention, T 2 Positively correlated with Rg.
As a further improvement of one embodiment of the present invention, when the low-temperature-stage compressor is started, if T 2 >-20 ℃, rg = 4000rpm;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Rg=2500 rpm at-20 deg.c;
if T 2 <-40 ℃, rg = 1300rpm.
As a further improvement of an embodiment of the present invention, the low-temperature-stage compressor is a variable-frequency compressor, and the controller is further configured to, according to the temperature T in the second storage compartment 2 And controlling the rotating speed Rd of the low-temperature-stage compressor.
As a further improvement of an embodiment of the invention, the controller is also adapted to,
starting the low-temperature-stage compressor, and controlling the low-temperature-stage compressor to run at a first preset rotating speed Rd1 within a preset time t 1;
after a preset time t1, controlling the low-temperature-stage compressor to run at a second preset rotating speed Rd 2;
wherein, the minimum rotation speed Rmin and Rd1 of the low-temperature-stage compressor are less than or equal to 0.7Rd2.
As a further improvement of an embodiment of the present invention, the controller is further configured to 2 Positively correlated with t1.
As a further improvement of one embodiment of the present invention, when the low-temperature-stage compressor is started, if T 2 >-20 ℃, t1=6 min;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 T1=4 min at-20 ℃;
if T 2 <-40 ℃, t1=2 min.
In order to achieve one of the above objects, an embodiment of the present invention also provides a control method of a refrigeration apparatus, the control method including,
when the low-temperature-level compressor is started, if the temperature T in the second storage compartment is lower than the temperature T 2 >-20 ℃, controlling the rotational speed Rg = 4000rpm of the high temperature stage compressor;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Controlling Rg=2500 rpm when the temperature is less than or equal to minus 20 ℃;
if T 2 <-40 ℃, then Rg = 1300rpm is controlled.
As a further improvement of an embodiment of the present invention, the control method further includes, from the start of the low-temperature-stage compressor, controlling the low-temperature-stage compressor to operate at a first preset rotational speed Rd1 within a preset time t 1;
after a preset time t1, controlling the low-temperature-stage compressor to run at a second preset rotating speed Rd 2;
wherein, the minimum rotation speed Rmin and Rd1 of the low-temperature-stage compressor are less than or equal to 0.7Rd2.
As a further improvement of an embodiment of the present invention, the control method further includes that the low-temperature stage compressor is startedIf T 2 >-20 ℃, then t1=6 min;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Controlling t1=4 min at the temperature of less than or equal to-20 ℃;
if T 2 <-40 ℃, then t1=2 min.
Compared with the prior art, the invention has the following beneficial effects: according to the refrigerating device and the control method of the refrigerating device, the operation pressure of the refrigerating system is prevented from being too high when the low-temperature-level compressor is started, and the high-temperature-level evaporator can cool the first storage compartment when the first refrigerant circulates in the high-temperature-level refrigerating circulation loop; the second refrigerant flowing through the condensation part exchanges heat with the first refrigerant flowing through the evaporation part, and the first refrigerant in the evaporation part can absorb heat of the second refrigerant flowing through the condensation part, so that the temperature of the second refrigerant in the condensation part can be further reduced, the low-temperature-stage refrigeration cycle is precooled, and the low-temperature-stage refrigeration cycle can realize lower temperature.
Drawings
Fig. 1 is a schematic structural diagram of an cascade compression refrigeration system according to embodiment 1 of the present invention;
fig. 2 is a schematic structural diagram of an cascade compression refrigeration system according to embodiment 2 of the present invention;
fig. 3 is a schematic structural diagram of an cascade compression refrigeration system according to embodiment 3 of the present invention;
fig. 4 is a schematic structural diagram of an cascade compression refrigeration system according to embodiment 4 of the present invention;
FIG. 5 is a schematic diagram of an cascade compression refrigeration system according to embodiment 5 of the invention;
fig. 6 is a schematic structural diagram of an cascade compression refrigeration system according to embodiment 6 of the invention.
Detailed Description
The present invention will be described in detail below with reference to specific embodiments shown in the drawings.
In the various illustrations of the invention, certain dimensions of structures or portions may be exaggerated relative to other structures or portions for convenience of illustration, and thus serve only to illustrate the basic structure of the inventive subject matter.
It will be understood that, although the terms first, second, etc. may be used herein to describe various elements or structures, these described elements should not be limited by these terms. These terms are only used to distinguish one such descriptive object from another.
The refrigerating device provided by the embodiment of the invention comprises a box body and a door body, wherein the box body is internally provided with a storage compartment, the door body is used for opening or closing the storage compartment, and the refrigerating device further comprises a refrigerating system which is arranged in the box body and supplies cold to the storage compartment. Specifically, the refrigerating device can be set as a refrigerator, a freezer and the like so as to meet the requirements of different users and different application scenes.
Example 1
In this embodiment, the case has a first storage compartment and a second storage compartment, where the first storage compartment may be a refrigeration compartment or a freezing compartment, and the second storage compartment may be a temperature-changing compartment or a cryogenic compartment. The refrigeration system employs an cascade compression refrigeration system 100 that includes a high temperature stage refrigeration cycle 1 and a low temperature stage refrigeration cycle 2.
For convenience of description, in this embodiment, the high-temperature-stage refrigeration cycle 1 is used to cool the first storage compartment, and the low-temperature-stage refrigeration cycle 2 is used to cool the second storage compartment. Of course, the two may be interchanged.
Of course, in other embodiments, other storage compartments besides the first storage compartment and the second storage compartment may be provided according to actual needs.
Referring to fig. 1, the high-temperature-stage refrigeration cycle 1 includes a high-temperature-stage compressor 11, a high-temperature-stage evaporator 15, and an evaporation unit 12, a first refrigerant flows through the high-temperature-stage refrigeration cycle 1, and the high-temperature-stage compressor 11 is a variable-frequency compressor.
The low-temperature-stage refrigeration cycle 2 includes a low-temperature-stage compressor 22, a low-temperature-stage evaporator 24, and a condensation unit 21, and a second refrigerant flows through the low-temperature-stage refrigeration cycle 2, and the second refrigerant flowing through the condensation unit 21 exchanges heat with the first refrigerant flowing through the evaporation unit 12.
Thus, when the first refrigerant circulates in the high-temperature-stage refrigeration cycle 1, the high-temperature-stage evaporator 15 cools the first storage compartment; by exchanging heat between the second refrigerant flowing through the condensation portion 21 and the first refrigerant flowing through the evaporation portion 12, the first refrigerant in the evaporation portion 12 can absorb heat of the second refrigerant flowing through the condensation portion 21, so that the temperature of the second refrigerant in the condensation portion 21 can be further reduced, the low-temperature-stage refrigeration cycle 2 can be pre-cooled, and the low-temperature-stage refrigeration cycle 2 can achieve a lower temperature.
The first refrigerant and the second refrigerant may be the same refrigerant or different refrigerants.
In addition, the "high temperature" and "low temperature" in the "high temperature-stage refrigeration cycle 1" and the "low temperature-stage refrigeration cycle 2" are relatively speaking, and the evaporation temperature of the first refrigerant flowing through the high temperature-stage refrigeration cycle 1 is relatively higher than the evaporation temperature of the second refrigerant flowing through the low temperature-stage refrigeration cycle 2.
The refrigerating device also comprises a first temperature sensor arranged in the first storage room and a second temperature sensor arranged in the second storage room, that is, the first temperature sensor detects the temperature T in the first storage room 1 The second temperature sensor detects the temperature T in the second storage room 2 The method comprises the steps of carrying out a first treatment on the surface of the That is, the temperature detected by the first temperature sensor is the temperature T in the first storage compartment 1 The temperature detected by the second temperature sensor is the temperature T in the second storage room 2 。
Further, the refrigeration device further comprises a controller which is respectively connected with the first temperature sensor and the second temperature sensor, acquires the temperatures detected by the first temperature sensor and the second temperature sensor, and is used for controlling the operation states of the high-temperature-stage compressor 11 and the low-temperature-stage compressor 22 according to the temperatures detected by the first temperature sensor and the second temperature sensor.
The controller is respectively connected with the high-temperature-stage compressor 11 and the low-temperature-stage compressor 22 and is used for controlling the pressure according to the low temperatureThe temperature T in the second storage compartment when the compressor 22 is started 2 The rotation speed Rg of the high-temperature-stage compressor 11 is controlled.
Further, T 2 Positively correlated with Rg. I.e. the temperature T in the second compartment when the low-temperature-stage compressor 22 is started 2 The lower the rotation speed Rg of the high-temperature-stage compressor 11 is controlled, the smaller.
Specifically, if T is the case when the low temperature stage compressor 22 is started 2 >-20 ℃, rg = 4000rpm;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Rg=2500 rpm at-20 deg.c;
if T 2 <-40 ℃, rg = 1300rpm.
That is, the temperature T in the second storage compartment when the low-temperature-stage compressor 22 is started 2 The larger the rotation speed Rg of the high-temperature stage compressor 11 is controlled to be smaller, so that the operation pressure of the refrigeration system at the time of starting the low-temperature stage compressor 22 can be prevented from being excessively large.
Preferably, the low-temperature stage compressor 22 is a variable-frequency compressor, and the controller is further configured to control the temperature T of the second storage compartment 2 The rotational speed Rd of the low temperature stage compressor 22 is controlled so as not to excessively increase the operation pressure of the refrigeration system.
In particular, the controller is also used for controlling,
starting from the start of the low-temperature-stage compressor 22, controlling the low-temperature-stage compressor 22 to operate at a first preset rotation speed Rd1 within a preset time t 1;
after a preset time t1, controlling the low-temperature-stage compressor 22 to run at a second preset rotating speed Rd 2;
wherein, the minimum rotation speed Rmin and Rd1 of the low-temperature-stage compressor 22 are less than or equal to 0.7Rd2.
That is, by controlling the low temperature stage compressor 22 to operate at the lower rotational speed Rd1 for the preset time t2 at the initial start-up period, the excessive operation pressure of the refrigeration system at the initial start-up period of the low temperature stage compressor 22 is avoided; after the preset time t2, the low-temperature-stage refrigeration cycle 2 is stably operated, and then the low-temperature-stage compressor 22 is controlled to operate at a second preset rotation speed Rd2, wherein Rmin Rd1 is less than or equal to 0.7Rd2, so that on one hand, the low-temperature-stage refrigeration cycle 2 can provide a certain amount of cold for the second storage compartment at the initial stage of starting the low-temperature-stage compressor 22, and on the other hand, the operation pressure of the refrigeration system at the initial stage of starting the low-temperature-stage compressor 22 can be prevented from being excessively high.
Further, T 2 Positively correlated with t1. I.e. the temperature T of the second storage compartment at start-up of the low-temperature stage compressor 22 2 The lower the time t1 the low temperature stage compressor 22 is operated at the second preset rotational speed Rd2 is, the smaller.
Further, the controller is further configured to determine a temperature T of the second storage compartment based on the start-up of the low-temperature-stage compressor 22 2 The low temperature stage compressor 22 is controlled to operate at a second preset rotational speed Rd2 for a time t1.
Specifically, if T is the case when the low temperature stage compressor 22 is started 2 >-20 ℃, t1=6 min;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 T1=4 min at-20 ℃;
if T 2 <-40 ℃, t1=2 min.
That is, according to the temperature T in the second storage compartment at the start-up of the low-temperature-stage compressor 22 2 The amount of time the low temperature stage compressor 22 is operated at the lower rotational speed Rd2 at the initial start-up stage is controlled, so that the refrigeration efficiency and the refrigeration system operating pressure can be equalized. Specifically, the low temperature stage compressor 22 is started at T 2 The smaller the control low temperature stage compressor 22 is started up initially, the shorter the time to run at the lower speed Rd2.
Further, the controller is also used for controlling the operation of the device,
T 2 >the preset starting temperature T of the second storage compartment 2 open When the high-temperature-stage compressor 11 is started, the high-temperature-stage compressor is controlled;
after a preset time t2, the low temperature stage compressor 22 is controlled to start.
That is, when the second storage compartment needs to be refrigerated, the high-temperature-stage compressor 11 is controlled to be started first, so that the first refrigerant flowing through the evaporation portion 12 can absorb the heat of the second refrigerant flowing through the condensation portion 21, and thus the temperature of the second refrigerant in the condensation portion 21 can be further reduced, the low-temperature-stage refrigeration cycle 2 is pre-cooled, after a preset time t2, the low-temperature-stage compressor 22 is controlled to be started again, and thus the problem that the condensation pressure of the low-temperature-stage refrigeration cycle 2 is large due to the excessive heat dissipation of the condensation portion 21 at the moment when the low-temperature-stage compressor 22 is started can be solved, and the low-temperature-stage refrigeration cycle 2 can be further cooled.
Preferably, t2=5 to 30min, so that the condensation unit 21 can sufficiently dissipate heat.
An embodiment of the present invention also provides a control method of the refrigerating apparatus as described above, which includes,
if T when the low-temperature stage compressor 22 is started 2 >-20 ℃, rg = 4000rpm;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Rg=2500 rpm at-20 deg.c;
if T 2 <-40 ℃, rg = 1300rpm.
That is, the temperature T in the second storage compartment when the low-temperature-stage compressor 22 is started 2 The larger the rotation speed Rg of the high-temperature stage compressor 11 is controlled to be smaller, so that the operation pressure of the refrigeration system at the time of starting the low-temperature stage compressor 22 can be prevented from being excessively large.
Further, the control method further comprises,
starting from the start of the low-temperature-stage compressor 22, controlling the low-temperature-stage compressor 22 to operate at a first preset rotation speed Rd1 within a preset time t 1;
after a preset time t1, controlling the low-temperature-stage compressor 22 to run at a second preset rotating speed Rd 2;
wherein, the minimum rotation speed Rmin and Rd1 of the low-temperature-stage compressor 22 are less than or equal to 0.7Rd2.
That is, by controlling the low temperature stage compressor 22 to operate at the lower rotational speed Rd1 for the preset time t1 at the initial start-up period, the excessive operation pressure of the refrigeration system at the initial start-up period of the low temperature stage compressor 22 is avoided; after the preset time t1, the low-temperature-stage refrigeration cycle 2 is controlled to run at a second preset rotation speed Rd2 after being stably run, wherein Rmin Rd1 is less than or equal to 0.7Rd2, on one hand, the low-temperature-stage refrigeration cycle 2 can provide a certain amount of cold for the second storage compartment at the initial stage of starting the low-temperature-stage compressor 22, and on the other hand, the operation pressure of the refrigeration system at the initial stage of starting the low-temperature-stage compressor 22 can be prevented from being excessively large.
Further, the control method further comprises,
if T when the low-temperature stage compressor 22 is started 2 >-20 ℃, t1=6 min;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 T1=4 min at-20 ℃;
if T 2 <-40 ℃, t1=2 min.
That is, according to the temperature T in the second storage compartment at the start-up of the low-temperature-stage compressor 22 2 The amount of time the low temperature stage compressor 22 is operated at the lower rotational speed Rd2 at the initial start-up stage is controlled, so that the refrigeration efficiency and the refrigeration system operating pressure can be equalized. Specifically, the low temperature stage compressor 22 is started at T 2 The smaller the control low temperature stage compressor 22 is started up initially, the shorter the time to run at the lower speed Rd2.
Further, the control method further comprises,
the temperature T in the second storage room 2 >It presets the starting temperature T 2 open When the high-temperature-stage compressor 11 is started, the high-temperature-stage compressor is controlled;
after a preset time t2, the low temperature stage compressor 22 is controlled to start.
That is, when the second storage compartments all need to be refrigerated, the high-temperature-stage compressor 11 is controlled to be started first, so that the first refrigerant flowing through the evaporation portion 12 can absorb the heat of the second refrigerant flowing through the condensation portion 21, and thus the temperature of the second refrigerant in the condensation portion 21 can be further reduced, the low-temperature-stage refrigeration cycle 2 is pre-cooled, after a preset time t2, the low-temperature-stage compressor 22 is controlled to be started again, and thus the problem that the condensation pressure of the low-temperature-stage refrigeration cycle 2 is large due to the excessive heat dissipation of the condensation portion 21 at the moment when the low-temperature-stage compressor 22 is started can be solved, and the low-temperature-stage refrigeration cycle 2 can be further cooled.
Preferably, t2=5 to 30min, so that the condensation unit 21 can sufficiently dissipate heat.
Referring to fig. 1, further, the high-temperature-stage refrigeration cycle 1 further includes a high-temperature-stage condenser 14 and a parallel branch circuit, the parallel branch circuit is disposed between the high-temperature-stage condenser 14 and the evaporation portion 12, the parallel branch circuit includes a switching valve 17 disposed at an inlet thereof, and a first cooling branch circuit and a second cooling branch circuit disposed in parallel, the first cooling branch circuit includes a first throttling device 161 and a high-temperature-stage evaporator 15 disposed in series, and the second cooling branch circuit includes a second throttling device 162. A switching valve 17 is selectively in communication with at least one of the first or second cooling branch.
Further, the high-temperature-stage refrigeration cycle 1 further includes a high-temperature-stage air return pipe 13 disposed between the high-temperature-stage compressor 11 and the evaporation portion 12, and the first refrigerant flowing through the first throttling device 161 and the second throttling device 162 exchanges heat with the first refrigerant flowing through the high-temperature-stage air return pipe 13, so that the first refrigerant in the high-temperature-stage air return pipe 13 can be used for cooling the first refrigerant in the first throttling device 161 and the second throttling device 162, increasing the refrigerating capacity, increasing the suction temperature of the high-temperature-stage compressor 11, increasing the temperature of the high-temperature-stage compressor 11 to about Wen Zuo, increasing the refrigerating efficiency of the high-temperature-stage compressor 11, and increasing the working efficiency of the high-temperature-stage refrigeration cycle 1, so that the first storage compartment can realize a temperature range of-30 to 10 ℃.
Preferably, the first throttling means 161 and the second throttling means 162 are capillary tubes.
The high-temperature-stage muffler 13 is respectively and thermally connected with the first throttling device 161 and the second throttling device 162 in a mutually sleeved or abutting mode, so that the heat exchange efficiency of the first refrigerant flowing in the first throttling device and the second throttling device is facilitated, and the energy utilization rate is improved.
Further, the high-temperature-stage refrigeration cycle 1 further includes a high-temperature-stage dry filter 18 provided between the high-temperature-stage condenser 14 and the parallel branch, and a liquid-storage bag 19 provided between the evaporation portion 12 and the high-temperature-stage muffler 13.
The low-temperature-stage refrigeration cycle 2 further includes a low-temperature-stage throttling device 23 and a first return air pipe section 25, and the condensing portion 21 is provided between the low-temperature-stage compressor 22 and the low-temperature-stage throttling device 23.
Further, the second refrigerant flowing through the first air return pipe section 25 exchanges heat with the second refrigerant flowing through the low-temperature-stage throttling device 23, so that the second refrigerant flowing through the first air return pipe section 25 can absorb heat of the second refrigerant flowing through the low-temperature-stage throttling device 23, the temperature of the second refrigerant flowing to the suction inlet of the low-temperature-stage compressor 22 is increased, the suction temperature of the low-temperature-stage compressor 22 is increased, the energy utilization rate of the low-temperature-stage refrigeration cycle 2 is increased, and the energy efficiency of the whole refrigeration device is improved.
Preferably, the low-temperature-stage throttling device 23 is a capillary tube, and the first air return pipe section 25 and the low-temperature-stage throttling device 23 are mutually sleeved or abutted, so that the heat exchange efficiency of the second refrigerant flowing in the two is facilitated, and the energy utilization rate is improved.
Further, the low-temperature-stage refrigeration cycle 2 further includes a second air return pipe section 26 and a heat release pipe section 27, the second air return pipe section 26 is provided between the low-temperature-stage evaporator 24 and the low-temperature-stage compressor 22, the heat release pipe section 27 is provided between the low-temperature-stage compressor 22 and the condensing portion 21, and the second refrigerant flowing through the second air return pipe section 26 exchanges heat with the second refrigerant flowing through the heat release pipe section 27. Therefore, the second refrigerant flowing through the second air return pipe section 26 can absorb the heat of the second refrigerant flowing through the heat release pipe section 27, the suction temperature of the low-temperature-stage compressor 22 is increased, the cold energy of the second refrigerant flowing from the heat release pipe section 27 to the condensation part 21 is reduced, the low-temperature-stage refrigeration cycle 2 can achieve lower temperature, the temperature of the second storage compartment can be adjusted within the temperature range of-60 to-20 ℃, the energy utilization rate of the low-temperature-stage refrigeration cycle 2 is increased, and the energy efficiency of the whole refrigeration device is improved.
Preferably, the second return air pipe section 26 is located between the first return air pipe section 25 and the low temperature stage compressor 22, so that the energy utilization rate of the low temperature stage refrigeration cycle 2 can be maximally improved.
The second air return pipe section 26 and the heat release pipe section 27 are mutually sleeved or abutted, so that the heat exchange efficiency of the second refrigerant flowing in the two is facilitated, and the energy utilization rate is improved.
Further, the low-temperature-stage refrigeration cycle 2 further includes a low-temperature-stage radiating pipe 28 provided between the low-temperature-stage compressor 22 and the radiator pipe section 27, and a low-temperature-stage drier-filter 29 provided between the condensing portion 21 and the low-temperature-stage throttling device 23. The second refrigerant flowing out of the low-temperature stage compressor 22 can be radiated by the low-temperature stage radiating pipe 28, so that the low-temperature stage refrigeration cycle 2 can achieve a lower temperature; the second refrigerant flowing out of the condensation unit 21 can be dried and filtered by the low-temperature-stage dry filter 29.
Example 2
Referring to fig. 2, a second embodiment of the present invention is shown, which differs from example 1 only in that:
the parallel branch further comprises a third throttling device 163 arranged in parallel with the second throttling device 162, and the switching valve 17 is selectively communicated with at least one of the first cooling branch, the second cooling branch and the third throttling device 163. In addition, the first refrigerant flowing through the third throttling device 163 does not exchange heat with the first refrigerant flowing through the high-temperature-stage muffler 13.
In this way, when the low-temperature-stage compressor 22 is started, the first refrigerant can flow through the third throttling device 163, and compared with the first refrigerant flowing through the second throttling device 162, the starting pressure of the refrigerating system at the moment when the low-temperature-stage compressor 22 is started can be further reduced, and the reduction of the flow rate of the first refrigerant in the second throttling device 162 caused by the heat exchange between the first refrigerant flowing into the high-temperature-stage muffler 13 and the second throttling device 162 can be avoided.
Preferably, the third throttling means 163 is a capillary tube.
The second embodiment is identical to the embodiment 1 except for the differences described above, and will not be described again here.
Example 3
Referring to fig. 3, a third embodiment of the present invention is shown, which differs from example 1 only in that:
the first cooling branch comprises a first throttling device 161, the second cooling branch comprises a second throttling device 162 and an evaporation part 12 which are arranged in series, the high-temperature-stage evaporator 15 is arranged between the parallel branch and the high-temperature-stage compressor 11, and the high-temperature-stage muffler 13 is arranged between the high-temperature-stage evaporator 15 and the high-temperature-stage compressor 11.
The third embodiment is the same as that of example 1 except for the differences described above, and will not be described again.
Example 4
Referring to fig. 4, a fourth embodiment of the present invention is shown, which differs from example 3 only in that:
the parallel branch further comprises a third throttling device 163 arranged in parallel with the second throttling device 162, and the switching valve 17 is selectively communicated with at least one of the first cooling branch, the second cooling branch and the third throttling device 163. In addition, the first refrigerant flowing through the third throttling device 163 does not exchange heat with the first refrigerant flowing through the high-temperature-stage muffler 13.
In this way, when the low-temperature-stage compressor 22 is started, the first refrigerant can flow through the third throttling device 163, and compared with the first refrigerant flowing through the second throttling device 162, the starting pressure of the refrigerating system at the moment when the low-temperature-stage compressor 22 is started can be further reduced, and the reduction of the flow rate of the first refrigerant in the second throttling device 162 caused by the heat exchange between the first refrigerant flowing into the high-temperature-stage muffler 13 and the second throttling device 162 can be avoided.
Preferably, the third throttling means 163 is a capillary tube.
The fourth embodiment is the same as the embodiment 3 except for the above differences, and will not be described here again.
Example 5
Referring to fig. 5, a fifth embodiment of the present invention is shown, which differs from example 1 only in that:
the first cooling branch comprises a first throttling device 161 and a high-temperature-stage evaporator 15 which are arranged in series, the second cooling branch comprises a second throttling device 162 and an evaporation part 12 which are arranged in series, and a high-temperature-stage muffler 13 is arranged between the parallel branch and the high-temperature-stage compressor 11.
The fifth embodiment is the same as the embodiment 1 except for the above differences, and will not be described here again.
Example 6
Referring to fig. 6, a sixth embodiment of the present invention is shown, which differs from example 5 only in that:
the parallel branch further comprises a third throttling means 163 arranged in parallel with the second throttling means 162, and the switching valve 17 is selectively in communication with at least one of the first cold supply branch, the second throttling means 162, the third throttling means 163. In addition, the first refrigerant flowing through the third throttling device 163 does not exchange heat with the first refrigerant flowing through the high-temperature-stage muffler 13.
In this way, when the low-temperature-stage compressor 22 is started, the first refrigerant can flow through the third throttling device 163, and compared with the first refrigerant flowing through the second throttling device 162, the starting pressure of the refrigerating system at the moment when the low-temperature-stage compressor 22 is started can be further reduced, and the reduction of the flow rate of the first refrigerant in the second throttling device 162 caused by the heat exchange between the first refrigerant flowing into the high-temperature-stage muffler 13 and the second throttling device 162 can be avoided.
Preferably, the third throttling means 163 is a capillary tube.
The sixth embodiment is the same as the embodiment 5 except for the above differences, and will not be described here again.
Compared with the prior art, the refrigerating device and the control method of the refrigerating device have the beneficial effects that: not only can the operation pressure of the refrigerating system be prevented from being too high when the low-temperature-stage compressor 22 is started, but also the high-temperature-stage evaporator 12 can cool the first storage compartment when the first refrigerant circulates in the high-temperature-stage refrigerating cycle circuit 1; by exchanging heat between the second refrigerant flowing through the condensation portion 21 and the first refrigerant flowing through the evaporation portion 12, the first refrigerant in the evaporation portion 12 can absorb heat of the second refrigerant flowing through the condensation portion 21, so that the temperature of the second refrigerant in the condensation portion 21 can be further reduced, the low-temperature-stage refrigeration cycle 2 can be pre-cooled, and the low-temperature-stage refrigeration cycle 2 can achieve a lower temperature.
It should be understood that although the present disclosure describes embodiments, not every embodiment is provided with a separate embodiment, and that this description is for clarity only, and that the skilled artisan should recognize that the embodiments may be combined as appropriate to form other embodiments that will be understood by those skilled in the art.
The above list of detailed descriptions is only specific to practical embodiments of the present invention, and they are not intended to limit the scope of the present invention, and all equivalent embodiments or modifications that do not depart from the spirit of the present invention should be included in the scope of the present invention.

Claims (10)

1. A refrigerating device is characterized by comprising,
the high-temperature-stage refrigeration cycle loop comprises a high-temperature-stage compressor, a high-temperature-stage evaporator and an evaporation part, wherein a first refrigerant flows in the high-temperature-stage refrigeration cycle loop, and the high-temperature-stage compressor is a variable-frequency compressor;
the low-temperature-stage refrigeration cycle loop comprises a low-temperature-stage compressor, a low-temperature-stage evaporator and a condensation part, wherein a second refrigerant flows in the low-temperature-stage refrigeration cycle loop, and the second refrigerant flowing through the condensation part exchanges heat with the first refrigerant flowing through the evaporation part;
the box body is provided with a first storage compartment and a second storage compartment, the high-temperature-level refrigeration cycle loop is used for cooling the first storage compartment, and the low-temperature-level refrigeration cycle loop is used for cooling the second storage compartment;
the controller is respectively connected with the high-temperature-level compressor and the low-temperature-level compressor and is used for controlling the temperature T in the second storage compartment according to the starting time of the low-temperature-level compressor 2 And controlling the rotating speed Rg of the high-temperature-stage compressor.
2. A refrigeration unit as set forth in claim 1 wherein T 2 Positively correlated with Rg.
3. The refrigeration apparatus of claim 2 wherein, when said low temperature stage compressor is started, if T 2 >-20 ℃, rg = 4000rpm;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Rg=2500 rpm at-20 deg.c;
if T 2 <-40 ℃, rg = 1300rpm.
4. A refrigeration unit as recited in claim 3 wherein said low-temperature-stage compressor is a variable-frequency compressor, said controller further being configured to control said compressor in response to a temperature T in said second compartment 2 And controlling the rotating speed Rd of the low-temperature-stage compressor.
5. The refrigeration unit of claim 4 wherein said controller is further configured to,
starting the low-temperature-stage compressor, and controlling the low-temperature-stage compressor to run at a first preset rotating speed Rd1 within a preset time t 1;
after a preset time t1, controlling the low-temperature-stage compressor to run at a second preset rotating speed Rd 2;
wherein, the minimum rotation speed Rmin and Rd1 of the low-temperature-stage compressor are less than or equal to 0.7Rd2.
6. The refrigeration unit as recited in claim 5 wherein T 2 Positively correlated with t1.
7. A refrigerating apparatus as recited in claim 6, wherein,
when the low-temperature-stage compressor is started, if T 2 >-20 ℃, t1=6 min;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 T1=4 min at-20 ℃;
if T 2 <-40 ℃, t1=2 min.
8. A control method of a refrigeration apparatus according to claim 1, wherein the control method comprises,
when the low-temperature-level compressor is started, if the temperature T in the second storage compartment is lower than the temperature T 2 >-20 ℃, controlling the rotational speed Rg = 4000rpm of the high temperature stage compressor;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Controlling Rg=2500 rpm when the temperature is less than or equal to minus 20 ℃;
if T 2 <-40 ℃, then Rg = 1300rpm is controlled.
9. A control method of a refrigeration apparatus according to claim 8, wherein said control method further comprises,
starting the low-temperature-stage compressor, and controlling the low-temperature-stage compressor to run at a first preset rotating speed Rd1 within a preset time t 1;
after a preset time t1, controlling the low-temperature-stage compressor to run at a second preset rotating speed Rd 2;
wherein, the minimum rotation speed Rmin and Rd1 of the low-temperature-stage compressor are less than or equal to 0.7Rd2.
10. A control method of a refrigeration unit as recited in claim 9, wherein said control method further comprises,
when the low-temperature-stage compressor is started, if T 2 >-20 ℃, then t1=6 min;
if the temperature is less than or equal to minus 40 ℃ and less than or equal to T 2 Controlling t1=4 min at the temperature of less than or equal to-20 ℃;
if T 2 <-40 ℃, then t1=2 min.
CN202210772024.3A 2022-06-30 2022-06-30 Refrigerating device and control method thereof Pending CN117366898A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210772024.3A CN117366898A (en) 2022-06-30 2022-06-30 Refrigerating device and control method thereof

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210772024.3A CN117366898A (en) 2022-06-30 2022-06-30 Refrigerating device and control method thereof

Publications (1)

Publication Number Publication Date
CN117366898A true CN117366898A (en) 2024-01-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Link
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