CN114353401A

CN114353401A - Refrigerant recovery control method and device and refrigerant recovery system

Info

Publication number: CN114353401A
Application number: CN202111570435.6A
Authority: CN
Inventors: 杨巨沁; 张新明; 王成; 周涯宸
Original assignee: Ningbo Aux Electric Co Ltd; Ningbo Aux Intelligent Commercial Air Conditioning Manufacturing Co Ltd
Current assignee: Aux Air Conditioning Co Ltd; Ningbo Aux Electric Co Ltd
Priority date: 2021-12-21
Filing date: 2021-12-21
Publication date: 2022-04-15
Anticipated expiration: 2041-12-21
Also published as: CN114353401B

Abstract

The invention provides a refrigerant recovery control method, a refrigerant recovery control device and a refrigerant recovery system, and relates to the technical field of refrigerant recovery. The refrigerant recovery control method can control the compressor to adjust the running frequency according to the real-time exhaust pressure value of the compressor and the real-time temperature value of the condenser, so that the real-time exhaust pressure value of the compressor approaches to the preset pressure value, the refrigerant recovery efficiency is improved to be optimal, and excessive consumption of energy can be prevented. The refrigerant recovery control device and the refrigerant recovery system provided by the invention can execute the refrigerant recovery control method. The refrigerant recovery control method, the refrigerant recovery control device and the refrigerant recovery system can solve the technical problem that energy is excessively consumed and energy is not beneficial to energy conservation in the prior art for improving the recovery efficiency of the refrigerant.

Description

Refrigerant recovery control method and device and refrigerant recovery system

Technical Field

The invention relates to the technical field of refrigerant recovery, in particular to a refrigerant recovery control method, a refrigerant recovery control device and a refrigerant recovery system.

Background

The application and development of the refrigerant recovery equipment are slow, besides the environmental awareness of workers is not enough, an important reason is that many refrigerant recovery equipment have various defects of low recovery speed, low efficiency and the like in the practical application process at present, while the recovery equipment with relatively high recovery speed has the problems of large volume, inconvenience in carrying and the like, but some refrigerant recovery equipment have small volume and the recovery speed of portable equipment is relatively slow.

However, in the prior art, in order to improve the recovery efficiency of the refrigerant, an operator is usually required to control the compressor by his own experience, so as to achieve the purpose of improving the recovery efficiency of the refrigerant; however, the control method based on this is generally disadvantageous in energy saving because excessive energy consumption is likely to occur.

Disclosure of Invention

The invention solves the technical problem how to improve the energy consumption caused by the excessive recovery efficiency of the refrigerant and the energy conservation in the prior art.

In order to solve the above problems, the present invention provides a refrigerant recovery control method, which is applied to a refrigerant recovery system, wherein the refrigerant recovery system comprises a recovery pipeline, one end of the recovery pipeline is connected to a system to be recovered, and the other end of the recovery pipeline is connected to a recovery container; the recovery pipeline is provided with a compressor and a condenser, the compressor is used for extracting a gaseous refrigerant in the system to be recovered when in operation and guiding the refrigerant to the condenser so as to guide the refrigerant to the recovery container;

the refrigerant recovery control method comprises the following steps:

receiving a real-time exhaust pressure value, wherein the real-time exhaust pressure value represents the real-time pressure of a refrigerant in an exhaust pipe of the compressor;

receiving a real-time temperature value, wherein the real-time temperature value represents the real-time temperature of the middle part of the condenser;

and controlling the compressor to determine the operation frequency according to the real-time exhaust pressure value, the preset pressure value, the real-time temperature value and the preset temperature value, so that the real-time exhaust pressure value approaches to the preset pressure value.

Compared with the prior art, the refrigerant recovery control method provided by the invention has the beneficial effects that:

in the process of refrigerant recovery, the operating frequency of the compressor influences the temperature of the refrigerant, and then influences the temperature of the middle part of the condenser, and based on the temperature, the recovery speed of the refrigerant is related to the temperature of the middle part of the condenser. Under the condition that the temperature of the middle part of the condenser reaches a preset temperature value, the recovery speed of the refrigerant reaches the best speed; if the operation frequency of the compressor is continuously increased to increase the temperature of the middle part of the condenser, the recovery speed of the refrigerant is not increased, and excessive energy consumption is caused, which is not beneficial to energy conservation. In addition, the discharge pressure of the compressor reaches a preset pressure value under the condition that the middle part of the condenser reaches a preset temperature value. The control precision of controlling the operation frequency of the compressor only through the temperature of the middle part of the condenser is low, so that the operation frequency of the compressor is controlled through the real-time temperature value of the middle part of the condenser and the real-time exhaust pressure value of the compressor, the recovery speed of the refrigerant can be adjusted to the optimal speed, and the excessive consumption of energy sources is prevented. Namely, the refrigerant recovery control method provided by the invention can solve the technical problem that energy is excessively consumed and energy is not beneficial to energy conservation in order to improve the recovery efficiency of the refrigerant in the prior art.

In order to prevent the detection error and the detection lag condition from affecting the control precision of the compressor, optionally, the step of controlling the compressor to determine the operating frequency according to the real-time exhaust pressure value, the preset pressure value, the real-time temperature value and the preset temperature value includes:

calculating a first pressure threshold value and a second pressure threshold value according to the preset pressure value, wherein the first pressure threshold value is larger than the second pressure threshold value;

calculating a first temperature threshold and a second temperature threshold according to a preset temperature value, wherein the first temperature threshold is larger than the second temperature threshold;

and controlling the compressor to determine the operating frequency according to the real-time exhaust pressure value, the real-time temperature value, the first pressure threshold value, the second pressure threshold value, the first temperature threshold value and the second temperature threshold value.

Optionally, the step of controlling the compressor to adjust the operating frequency according to the real-time exhaust pressure value, the real-time temperature value, the first pressure threshold, the second pressure threshold, the first temperature threshold, and the second temperature threshold includes:

comparing at least one of the first pressure threshold and the second pressure threshold with the real-time exhaust pressure value to judge the magnitude relation among the first pressure threshold, the second pressure threshold and the real-time exhaust pressure value;

comparing at least one of the first temperature threshold and the second temperature threshold with the real-time temperature value to judge the magnitude relation among the first temperature threshold, the second temperature threshold and the real-time temperature value;

controlling the compressor to adjust the operating frequency or controlling the compressor to maintain the current operating frequency according to the magnitude relation among the first pressure threshold, the second pressure threshold and the real-time exhaust pressure value and the magnitude relation among the first temperature threshold, the second temperature threshold and the real-time temperature value;

after controlling the compressor to adjust the operation frequency, controlling the compressor to operate for a first preset time, returning to re-execute the step of comparing at least one of the first pressure threshold value and the second pressure threshold value with the real-time exhaust pressure value, and the step of comparing at least one of the first temperature threshold value and the second temperature threshold value with the real-time temperature value.

Through adjustment for many times, the running frequency of the compressor can be accurately adjusted to the condition that the refrigerant recovery speed can reach the best and the energy is not excessively consumed.

Optionally, the step of controlling the compressor to adjust the operating frequency or controlling the compressor to maintain the current operating frequency according to the magnitude relationship between the first pressure threshold, the second pressure threshold and the real-time exhaust pressure value and the magnitude relationship between the first temperature threshold, the second temperature threshold and the real-time temperature value includes:

if the real-time exhaust pressure value is greater than the first pressure threshold value, or the real-time temperature value is greater than the first temperature threshold value, controlling the compressor to reduce the operating frequency until the real-time exhaust pressure value is less than or equal to the preset pressure value and the real-time temperature value is less than or equal to the preset temperature value;

if the real-time exhaust pressure value is smaller than the second pressure threshold value, or the real-time temperature value is smaller than the second temperature threshold value, controlling the compressor to increase the operating frequency until the real-time exhaust pressure value is larger than or equal to the preset pressure value and the real-time temperature value is larger than or equal to the preset temperature value;

and if the real-time exhaust pressure value is smaller than or equal to the first pressure threshold value and larger than or equal to the second pressure threshold value, controlling the compressor to maintain the current operating frequency to operate until the recovery of the refrigerant is finished.

Optionally, the step of controlling the compressor to reduce the operating frequency comprises:

controlling the running frequency of the compressor to reduce a first frequency value every second preset time;

the step of controlling the compressor to increase the operating frequency comprises:

controlling the running frequency of the compressor to increase by a second frequency value every third preset time;

and the second preset time is less than the third preset time.

In order to prevent the operation frequency of the compressor from fluctuating repeatedly, optionally, the refrigerant recovery control method further includes:

counting for one time when the compressor is continuously controlled to finish raising the running frequency once and finish lowering the running frequency once;

and if the counting reaches the preset times, controlling the compressor to operate at the increased operating frequency until the recovery of the refrigerant is finished after controlling the compressor to increase the operating frequency.

Optionally, the step of calculating the first pressure threshold and the second pressure threshold according to the preset pressure value includes:

adding a first preset value to the preset pressure value to obtain a first pressure threshold value;

subtracting a second preset value from the preset pressure value to obtain a second pressure threshold value;

the step of calculating a first temperature threshold and a second temperature threshold according to the preset temperature value comprises the following steps:

adding a third preset value to the preset temperature value to obtain the first temperature threshold value;

and subtracting a fourth preset value from the preset temperature value to obtain the second temperature threshold value.

Optionally, before receiving the real-time exhaust pressure value, the refrigerant recovery control method further includes:

judging whether the running time of the compressor reaches a fourth preset time or not;

if yes, executing a step of receiving a real-time exhaust pressure value;

if not, controlling the compressor to be started, controlling the running frequency of the compressor to increase a third frequency value every fifth preset time until the running frequency of the compressor is greater than or equal to the preset pressure value, and then executing the step of receiving the real-time exhaust pressure value.

A refrigerant recovery control device is applied to a refrigerant recovery system, the refrigerant recovery system comprises a recovery pipeline, one end of the recovery pipeline is connected to a system to be recovered, and the other end of the recovery pipeline is connected to a recovery container; the recovery pipeline is provided with a compressor and a condenser, the compressor is used for extracting a gaseous refrigerant in the system to be recovered when in operation and guiding the refrigerant to the condenser so as to guide the refrigerant to the recovery container;

the refrigerant recovery control device includes:

the first receiving module is used for receiving a real-time exhaust pressure value, and the real-time exhaust pressure value represents the real-time pressure of a refrigerant in an exhaust pipe of the compressor;

the second receiving module is used for receiving a real-time temperature value, and the real-time temperature value represents the temperature of the middle part of the condenser;

and the control module is used for controlling the compressor to determine the running frequency according to the real-time exhaust pressure value, the preset pressure value, the real-time temperature value and the preset temperature value, so that the real-time exhaust pressure value approaches to the preset pressure value.

A refrigerant recovery system comprises a recovery pipeline, wherein one end of the recovery pipeline is connected to a system to be recovered, and the other end of the recovery pipeline is connected to a recovery container; the recovery pipeline is provided with a compressor and a condenser, the compressor is used for extracting a gaseous refrigerant in the system to be recovered when in operation and guiding the refrigerant to the condenser so as to guide the refrigerant to the recovery container; the refrigerant recovery system also comprises a pressure detection device, a temperature detection device and a controller; the pressure detection device is arranged on an exhaust pipe of the compressor so as to detect a real-time exhaust pressure value of the exhaust pipe; the temperature detection device is arranged in the middle of the condenser to detect a real-time temperature value of the condenser; the pressure detection device and the temperature detection device are both electrically connected with a controller, and the controller is used for receiving the real-time exhaust pressure value and the real-time temperature value and executing the refrigerant recovery control method.

The refrigerant recovery control device and the refrigerant recovery system provided by the invention can execute the refrigerant recovery control method, and the beneficial effects of the refrigerant recovery control device and the refrigerant recovery system relative to the prior art are the same as the beneficial effects of the refrigerant recovery control method relative to the prior art, and are not repeated herein.

Drawings

Fig. 1 is a schematic structural diagram of a refrigerant recovery system provided in an embodiment of the present application;

fig. 2 is a graph showing a relationship between a discharge pressure of a compressor and a refrigerant recovery speed;

fig. 3 is a graph showing a relationship between a temperature of a middle portion of a condenser and a refrigerant recovery speed;

fig. 4 is a flowchart of a refrigerant recovery control method provided in the embodiment of the present application;

fig. 5 is a flowchart of another part of the refrigerant recovery control method provided in the embodiment of the present application;

fig. 6 is a flowchart of step S30 in the refrigerant recovery control method according to the embodiment of the present application;

fig. 7 is a flowchart of step S33 in the refrigerant recovery control method according to the embodiment of the present application;

fig. 8 is a flowchart of step S333 in the refrigerant recovery control method provided in the embodiment of the present application;

fig. 9 is a flowchart of a part of a refrigerant recovery control method provided in the embodiment of the present application;

fig. 10 is a schematic diagram illustrating functional modules of a refrigerant recovery control device according to an embodiment of the present disclosure.

Description of reference numerals:

10-refrigerant recovery system; 11-a system to be recovered; 100-a recovery line; 110-a compressor; 120-laval nozzle; 130-a condenser; 140-a first solenoid valve; 200-a liquid refrigerant recovery branch; 210 a second solenoid valve; 300-mixing branch; 400-a recovery vessel; 500-a pressure boosting device; 20-refrigerant recovery control device; 21-a first receiving module; 22-a second receiving module; 23-control module.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.

In the process of recycling part of the refrigeration system, the refrigerant in the refrigeration system needs to be recycled. The refrigerant recovery system 10 may be used to recover the refrigerant in the refrigeration system. The refrigeration system has a system to be recovered 11 containing a refrigerant, and the system to be recovered 11 may be a compressor 110 of the refrigeration system, a refrigerant circulation circuit, or other containers containing a refrigerant. The refrigerant recovery system 10 is connected to the system to be recovered 11, so as to guide the refrigerant in the system to be recovered 11 to the recovery container 400 in the refrigerant recovery system 10, thereby completing the recovery of the refrigerant.

Referring to fig. 1, the refrigerant recovery system 10 includes a recovery pipeline 100, a recovery container 400 and a liquid refrigerant recovery branch 200, wherein one end of the recovery pipeline 100 and one end of the liquid refrigerant recovery branch 200 are both connected to the recovery container 400; the other end of the recovery pipeline 100 is used for connecting to the system to be recovered 11, so as to recover the gaseous refrigerant in the system to be recovered 11; the other end of the liquid refrigerant recycling branch 200 is also used for connecting to the system 11 to be recycled, so as to recycle the liquid refrigerant in the system 11 to be recycled. The recovery pipeline 100 is provided with a compressor 110, a laval nozzle 120, a condenser 130 and a first electromagnetic valve 140, and in the process of recovering the gaseous refrigerant in the recovery pipeline 100, the gaseous refrigerant sequentially passes through the compressor 110, the laval nozzle 120, the condenser 130 and the first electromagnetic valve 140, and then is introduced into the recovery container 400. In addition, a second solenoid valve is disposed on the liquid refrigerant recovery branch 200, and the second solenoid valve is configured to selectively open or close the liquid refrigerant recovery branch 200. In the embodiment of the present application, the refrigerant recycling system 10 further includes a mixing branch 300, wherein one end of the mixing branch 300 is connected to the recycling pipeline 100, and the other end is connected to the liquid refrigerant recycling branch 200. It should be noted that the end of the mixing branch 300 connected to the recovery line 100 is located between the laval nozzle 120 and the condenser 130; one end of the mixing branch 300 connected to the liquid refrigerant recovery branch 200 is located between the second solenoid valve and the system to be recovered 11.

In general, the system to be recovered 11 stores liquid refrigerant and gaseous refrigerant, and during the refrigerant recovery process, the recovery pipeline 100 recovers gaseous refrigerant by the pumping action of the compressor 110; the liquid refrigerant recycling branch 200 may be connected to a lower position of the system 11 to be recycled, and the liquid refrigerant may be recycled by a flowing action of the liquid refrigerant itself. Of course, in order to improve the recovery efficiency, the refrigerant is recovered quickly and efficiently. The refrigerant recovery system 10 may further include a pressure increasing device 500, where the pressure increasing device 500 is used to connect the system 11 to be recovered to charge gas into the system 11 to be recovered, so as to ensure that the pressure in the system 11 to be recovered is stable or raised, so as to facilitate the gaseous refrigerant and the liquid refrigerant in the system 11 to be recovered to be led out of the system 11 to be recovered, and thus, the purpose of improving the refrigerant recovery efficiency can be achieved.

In the process of recovering the gaseous refrigerant, the laval nozzle 120 forms a low pressure at the end thereof, so that the mixing branch 300 is connected to the end of the recovery pipeline 100 to form a low pressure, and at this time, the mixing branch 300 can be conducted and the second electromagnetic valve can be closed, so that the liquid refrigerant is converged into the recovery pipeline 100 from the mixing branch 300, and the liquid refrigerant can be mixed with other refrigerants, thereby recovering the mixed refrigerant.

Of course, the recovery speed of the liquid refrigerant is generally higher than that of other refrigerants, and the liquid refrigerant is volatilized during the refrigerant recovery process, so that other refrigerants at the volatilized part are formed.

Referring to fig. 2 and 3, fig. 2 shows a relationship curve between the discharge pressure of the compressor 110 and the refrigerant recovery speed; fig. 3 shows a relationship between the temperature of the middle portion of the condenser 130 and the refrigerant recovery speed. As can be seen from fig. 2 and 3, in the process of recovering the pure gas refrigerant, the operating frequency of the compressor 110 affects the temperature of the refrigerant, and thus affects the temperature of the middle portion of the condenser 130, and the recovery rate of the refrigerant is related to the temperature of the middle portion of the condenser 130. In addition, under the condition that the temperature of the middle part of the condenser 130 reaches a preset temperature value, the recovery speed of the refrigerant reaches the best speed; if the operation frequency of the compressor 110 is continuously increased to increase the temperature of the middle portion of the condenser 130, the refrigerant recovery rate is not increased, and excessive energy consumption is caused, which is not favorable for energy saving. In addition, in the case where the middle of the condenser 130 reaches a preset temperature value, the discharge pressure of the compressor 110 reaches a preset pressure value. And the control accuracy of controlling the operating frequency of the compressor 110 only by the temperature of the middle portion of the condenser 130 is low. Therefore, the operation frequency of the compressor 110 is controlled by the real-time temperature value of the middle portion of the condenser 130 and the real-time exhaust pressure value of the compressor 110, so that the recovery speed of the refrigerant can be adjusted to an optimal speed, and the excessive consumption of energy can be prevented.

In order to ensure that the recovery can be completed quickly in the recovery process of the gaseous refrigerant and avoid the excessive consumption of energy, the refrigerant recovery system 10 in the application is provided. The refrigerant recovery system 10 further includes a pressure detection device, a temperature detection device, and a controller. Wherein, the pressure detection device is arranged at the exhaust pipe of the compressor 110, so as to detect the real-time exhaust pressure value of the compressor 110; the temperature detecting means is disposed at the middle of the condenser 130 to detect a real-time temperature value at the middle of the condenser 130. And the pressure detection device and the temperature detection device are electrically connected with the controller and used for sending the detected real-time exhaust pressure value and real-time temperature value to the controller. The controller may then determine an operating frequency of the compressor 110 according to the obtained real-time discharge pressure value and the real-time temperature value, and control the operation of the compressor 110 at the determined operating frequency.

The controller may be an integrated circuit chip having signal processing capabilities. The controller may be a general-purpose processor, and may include a Central Processing Unit (CPU), a single chip Microcomputer (MCU), a Micro Controller Unit (MCU), a Complex Programmable Logic Device (CPLD), a Field Programmable Gate Array (FPGA), an Application Specific Integrated Circuit (ASIC), an embedded ARM, and other chips, where the controller may implement or execute the methods, steps, and Logic blocks disclosed in the embodiments of the present invention.

In a possible implementation manner, the refrigerant recycling system 10 may further include a memory for storing program instructions executable by the controller, for example, the refrigerant recycling control device 20 provided in the embodiment of the present application, and the refrigerant recycling control device 20 provided in the embodiment of the present application includes at least one of the program instructions stored in the memory in a form of software or firmware. The Memory may be a stand-alone external Memory including, but not limited to, Random Access Memory (RAM), Read Only Memory (ROM), Programmable Read-Only Memory (PROM), Erasable Read-Only Memory (EPROM), electrically Erasable Read-Only Memory (EEPROM). The memory may also be integrated with the controller, for example, the memory may be integrated with the controller on the same chip.

It should be noted that, in the case that only gaseous refrigerant exists in the system to be recovered 11 at first, the refrigerant in the system to be recovered 11 is recovered by the refrigerant recovery system 10 at this time, so that pure gaseous refrigerant recovery can be formed; in addition, under the condition that the liquid refrigerant and the gaseous refrigerant exist in the system to be recovered 11, but the recovery of the liquid refrigerant is inconvenient at this time, or the liquid refrigerant recovery branch 200 cannot normally operate, the recovery of the gaseous refrigerant in the system to be recovered 11 is also performed only through the recovery pipeline 100, and at this time, the recovery of the gaseous refrigerant can also be regarded as forming pure gaseous refrigerant recovery. In the above situations, the above method for adjusting the operating frequency of the compressor 110 according to the real-time discharge pressure value of the compressor 110 and the real-time temperature of the middle portion of the condenser 130 may also be adopted, so as to solve the technical problem that energy is excessively consumed and energy saving is not facilitated in the prior art in order to improve the recovery efficiency of the refrigerant.

Based on the refrigerant recovery system 10 provided above, in order to improve the technical problem that energy is excessively consumed and energy saving is not facilitated due to the improvement of the refrigerant recovery efficiency in the prior art, the present application also provides a refrigerant recovery control method, which can be executed by the refrigerant recovery system 10 provided in the present application, so as to achieve the above object.

Referring to fig. 4, the refrigerant recycling control method includes:

and step S10, receiving the real-time exhaust pressure value.

And step S20, receiving the real-time temperature value.

The real-time exhaust pressure value is detected by the pressure detection device and then is sent to the controller by the pressure detection device. The real-time temperature value is detected by the temperature detection device and then sent to the controller by the temperature detection device. Here, "real-time" indicates that, in the refrigerant recovery process, the pressure detection device continuously detects the discharge pressure of the compressor 110, the temperature detection device continuously detects the temperature of the middle portion of the condenser 130, and the pressure detection device and the temperature detection device continuously send a real-time discharge pressure value and a real-time temperature value to the controller; in other words, the real-time discharge pressure value indicates the current discharge pressure of the compressor 110, and the real-time temperature value indicates the current temperature of the middle portion of the condenser 130.

Optionally, referring to fig. 5, before the step S10, in order to ensure that the compressor 110 can execute the refrigerant recovery control method provided by the present application, the refrigerant recovery control method may further include:

and step S05, determining whether the operation time of the compressor 110 reaches a fourth preset time.

It should be noted that, in the above-mentioned situations, if there are refrigerants in gas-liquid two states in the system to be recovered 11, the refrigerant can be recovered by mixing and recovering the gas-liquid refrigerant and the liquid refrigerant, and the recovery of the pure gas refrigerant is performed when the liquid refrigerant is recovered; the refrigerant recovery control method can be applied to the process of recovering pure gaseous refrigerants. However, in the case that only the gaseous refrigerant exists in the system to be recovered 11 at first and the recovery of the liquid refrigerant is inconvenient, the recovery of the pure gaseous refrigerant may be directly performed, and then the compressor 110 is in the standby state at this time, which is inconvenient to directly perform the refrigerant recovery control method provided by the present application. Based on this, by determining whether the operation time of the compressor 110 reaches the fourth preset time, the current state of the compressor 110 can be accurately determined, and the compressor 110 can be conveniently controlled to execute the refrigerant recovery control method.

And step S06, if yes, executing the step of receiving the real-time exhaust temperature value.

In other words, if the operation time of the compressor 110 reaches the fourth preset time, it indicates that the compressor 110 is in the operation state at this time, and thus the refrigerant recovery control method may be directly performed.

Step S07, if not, the compressor 110 is controlled to be turned on, and the operating frequency of the compressor 110 is controlled to increase the third frequency value every fifth preset time until the operating frequency of the compressor 110 is greater than or equal to the preset pressure value, and then the step of receiving the real-time exhaust pressure value is performed.

That is, in the case where the compressor 110 does not directly start to perform the refrigerant recovery control method, the compressor 110 may be controlled to perform the up-conversion operation until the operation frequency of the compressor 110 is increased to a value at which the discharge pressure of the compressor 110 reaches the preset pressure value, and then the step S10 may be performed.

Optionally, the value of the fourth preset time provided above may be set according to the time required for the liquid refrigerant to complete recycling, and of course, may also be selected according to the time required for the compressor 110 to operate to a stable state. For example, the time required for completing the recovery of the liquid refrigerant is set, and the value range of the fourth preset time may be 1h to 6h, in other words, the value of the fourth preset time may be 1h, 2h, 3h, 4h, 5h, or 6h, and the like; for another example, the fourth preset time may be set according to the time required for the compressor 110 to operate to the steady state, and the value of the fourth preset time may range from 10min to 30min, in other words, the value of the fourth preset time may be 10min, 12min, 15min, 18min, 20min, 25min, or 30min, and the like. The value of the fifth preset time may range from 5s to 20s, in other words, the value of the fifth preset time may range from 5s, 6s, 7s, 8s, 9s, 10s, 11s, 12s, 13s, 14s, 15s, 16s, 17s, 18s, 19s, or 20 s. In addition, the value of the third frequency value may be 1Hz to 3Hz, in other words, the value of the third frequency value may be 1Hz, 2Hz, 3Hz, or the like.

Referring to fig. 4, in step S30, the compressor 110 is controlled to determine the operation frequency according to the real-time exhaust pressure value, the preset pressure value, the real-time temperature value, and the preset temperature value.

Wherein, the "determination" indicates that the controller may adjust the operating frequency of the compressor 110 according to the real-time exhaust pressure value, the preset pressure value, the real-time temperature value, and the preset temperature value, so as to increase or decrease the operating frequency of the compressor 110; of course, the current operating frequency of the compressor 110, i.e., the current operating state of the compressor 110, may also be maintained.

The step S30 is to determine the operating frequency of the compressor 110 by the controller, so that the real-time exhaust pressure value approaches to the preset pressure value, thereby ensuring the best recovery speed of the refrigerant and avoiding excessive energy consumption, thereby achieving the two purposes of refrigerant recovery efficiency and energy saving.

The preset pressure value and the preset temperature value may be obtained through experiments performed by developers before the refrigerant recovery system 10 leaves a factory, and may be set in the controller. Based on the above, the refrigerant recovery speed can be optimized when the temperature of the middle portion of the condenser 130 reaches the preset temperature value, and meanwhile, the discharge pressure of the compressor 110 reaches the preset pressure value when the temperature of the middle portion of the condenser 130 reaches the preset temperature value. In other words, if the temperature of the middle portion of the condenser 130 reaches the preset temperature value and the discharge pressure of the compressor 110 reaches the preset pressure value, it indicates that the refrigerant recovery speed is optimal, and excessive energy consumption is also avoided. Therefore, the operation frequency of the compressor 110 is adjusted according to the preset pressure value and the preset temperature value to adjust the real-time exhaust temperature value and the real-time temperature value, so that the real-time exhaust pressure value approaches the preset pressure value, and the technical problem that in the prior art, energy is excessively consumed to avoid energy saving in order to improve the recovery efficiency of the refrigerant can be solved.

Optionally, the range of the preset pressure value may be 2.93MPa to 2.97MPa, in other words, the value of the preset pressure value may be 2.93MPa, 2.94MPa, 2.95MPa, 2.96MPa, or 2.97MPa, and the like. The predetermined temperature value may range from 48 ℃ to 56 ℃, in other words, the predetermined temperature value may be 48 ℃, 49 ℃, 50 ℃, 51 ℃, 52 ℃, 53 ℃, 54 ℃, 55 ℃, or 56 ℃. It should be noted that the values of the preset pressure value and the preset temperature value may be selected according to the actual displacement of the compressor 110, for example, when the displacement of the compressor 110 is 27.5ML, the value of the preset pressure value may be 2.95MPa, and the value of the preset temperature value may be 52 ℃.

In other words, the operation frequency of the compressor 110 affects the temperature of the refrigerant during the refrigerant recovery process, and thus affects the temperature of the middle portion of the condenser 130, and the refrigerant recovery rate is related to the temperature of the middle portion of the condenser 130. In addition, under the condition that the temperature of the middle part of the condenser 130 reaches a preset temperature value, the recovery speed of the refrigerant reaches the best speed; if the operation frequency of the compressor 110 is continuously increased to increase the temperature of the middle portion of the condenser 130, the refrigerant recovery rate is not increased, and excessive energy consumption is caused, which is not favorable for energy saving. In addition, in the case where the middle of the condenser 130 reaches a preset temperature value, the discharge pressure of the compressor 110 reaches a preset pressure value. The control accuracy for controlling the operation frequency of the compressor 110 only by the temperature of the middle portion of the condenser 130 is low, so that the operation frequency of the compressor 110 is controlled by the real-time temperature value of the middle portion of the condenser 130 and the real-time exhaust pressure value of the compressor 110, the recovery speed of the refrigerant can be adjusted to the optimal speed, and the excessive consumption of energy can be prevented. Namely, the refrigerant recovery control method provided by the invention can solve the technical problem that energy is excessively consumed and energy is not beneficial to energy conservation in order to improve the recovery efficiency of the refrigerant in the prior art.

Optionally, referring to fig. 6, in some embodiments of the present application, step S30 may include:

and step S31, calculating a first pressure threshold value and a second pressure threshold value according to the preset pressure value.

Wherein the first pressure threshold is greater than the second pressure threshold.

And step S32, calculating a first temperature threshold value and a second temperature threshold value according to the preset temperature value.

Wherein the first temperature threshold is greater than the second temperature threshold.

Step S33, controlling the compressor 110 to determine the operation frequency according to the real-time exhaust pressure value, the real-time temperature value, the first pressure threshold value, the second pressure threshold value, the first temperature threshold value and the second temperature threshold value.

It should be noted that since the detection of the discharge pressure of the compressor 110 has a certain error and a certain hysteresis, and similarly, the detection of the temperature of the middle portion of the condenser 130 has a certain error and a certain hysteresis, in order to prevent the control accuracy from being lowered due to the detection error and the hysteresis, the first pressure threshold, the second pressure threshold, the first temperature threshold, and the second temperature threshold may be determined by the preset pressure value and the preset temperature value, and thus the control determination may be performed by the interval formed by the first pressure threshold and the second pressure threshold and the interval formed by the first temperature threshold and the second temperature threshold, so that the effective control may be ensured, and the control accuracy may be improved.

Alternatively, the manner of calculating the first pressure threshold and the second pressure threshold may be as follows: and subtracting the second preset value from the preset pressure value to obtain a second pressure threshold value. The manner of calculating the first and second temperature thresholds may be as follows: and subtracting a fourth preset value from the preset temperature value to obtain a second temperature threshold value.

The value of the first predetermined value may be in a range of 0.05MPa to 0.2MPa, in other words, the value of the first predetermined value may be 0.05MPa, 0.06MPa, 0.07MPa, 0.08MPa, 0.09MPa, 0.1MPa, 0.11MPa, 0.12MPa, 0.13MPa, 0.14MPa, 0.15MPa, 0.16MPa, 0.17MPa, 0.18MPa, 0.19MPa, or 0.2MPa, etc. The second predetermined value may be in a range of 0.05MPa to 0.2MPa, or in other words, 0.05MPa, 0.06MPa, 0.07MPa, 0.08MPa, 0.09MPa, 0.1MPa, 0.11MPa, 0.12MPa, 0.13MPa, 0.14MPa, 0.15MPa, 0.16MPa, 0.17MPa, 0.18MPa, 0.19MPa, or 0.2 MPa. The first preset value and the second preset value may be the same value. The third predetermined value can range from 0.2 ℃ to 1 ℃, in other words, the third predetermined value can range from 0.2 ℃, 0.3 ℃, 0.4 ℃, 0.5 ℃, 0.6 ℃, 0.7 ℃, 0.8 ℃, 0.9 ℃ or 1 ℃ and the like. The fourth predetermined value can range from 0.2 ℃ to 1 ℃, in other words, the fourth predetermined value can range from 0.2 ℃, 0.3 ℃, 0.4 ℃, 0.5 ℃, 0.6 ℃, 0.7 ℃, 0.8 ℃, 0.9 ℃ or 1 ℃ and the like. The third preset value and the fourth preset value can be the same value.

It should be understood that in other embodiments of the present application, the first pressure threshold and the second pressure threshold may be calculated in other manners, for example, by multiplying a preset pressure value by a specific coefficient. Similarly, the first temperature threshold and the second temperature threshold may be calculated in other manners, for example, by multiplying a preset temperature value by a specific coefficient.

In an embodiment of the present application, referring to fig. 7, step S33 may include:

and step S331, comparing at least one of the first pressure threshold value and the second pressure threshold value with a real-time exhaust pressure value.

Step S331 aims at determining a magnitude relationship between two values of the first pressure threshold and the second pressure threshold and the real-time exhaust pressure value.

Step S332, comparing at least one of the first temperature threshold value and the second temperature threshold value with the real-time temperature value.

Step S332 is intended to determine the magnitude relationship between the real-time temperature value and the two values of the first temperature threshold and the second temperature threshold.

It should be noted that, at least one of the first pressure threshold value and the second pressure threshold value is described as an example compared with the real-time exhaust pressure value. Wherein "at least one" indicates that, in some cases, after comparing one of the first pressure threshold and the second pressure threshold with the real-time exhaust pressure value, the magnitude relationship between the real-time exhaust pressure value and the first pressure threshold and the second pressure threshold can be obtained; for example, the first pressure threshold is less than the real-time exhaust pressure value, and the second pressure threshold is greater than the real-time exhaust pressure value. In other cases, the first pressure threshold and the second pressure threshold are compared with the real-time exhaust pressure value to obtain a magnitude relationship between the first pressure threshold, the second pressure threshold and the real-time exhaust pressure value, for example, the first pressure threshold is greater than the real-time exhaust pressure value and the second pressure threshold is less than the real-time exhaust pressure value.

Step S333, controlling the compressor 110 to adjust the operating frequency according to the magnitude relationship between the first pressure threshold, the second pressure threshold and the real-time exhaust pressure value, and the magnitude relationship between the first temperature threshold, the second temperature threshold and the real-time temperature value, or controlling the compressor 110 to maintain the current operating frequency.

After the magnitude relationship among the first pressure threshold, the second pressure threshold, and the real-time exhaust pressure value and the magnitude relationship among the first temperature threshold, the second temperature threshold, and the real-time temperature value are obtained in steps S331 and S332, the state of the current refrigerant recovery speed can be determined, so that the operation frequency of the compressor 110 can be determined to ensure that the refrigerant recovery speed is optimal and excessive energy consumption is avoided.

Alternatively, referring to fig. 8, step S333 may include:

step S301, if the real-time exhaust pressure value is greater than the first pressure threshold value, or the real-time temperature value is greater than the first temperature threshold value, the compressor 110 is controlled to reduce the operating frequency until the real-time exhaust pressure value is less than or equal to the preset pressure value and the real-time temperature value is less than or equal to the preset temperature value.

Alternatively, in step S301, the manner of controlling the compressor 110 to reduce the operating frequency is: the operating frequency of the compressor 110 is controlled to decrease the first frequency value every second preset time. The value of the second preset time may range from 20s to 30s, in other words, the value of the second preset time may be 20s, 21s, 22s, 23s, 24s, 25s, 26s, 27s, 28s, 29s, or 30 s. In addition, the value of the first frequency value may be 1Hz to 3Hz, in other words, the value of the first frequency value may be 1Hz, 2Hz, or 3Hz, and the like.

In the process of reducing the frequency of the compressor 110, there is a certain hysteresis for the change of the discharge pressure of the compressor 110 and the temperature of the middle part of the condenser 130, so that the reduction of the operation frequency by controlling the compressor 110 in an intermittent manner can prevent the reduction of the control accuracy caused by the too fast adjustment speed of the operation frequency.

Step S302, if the real-time exhaust pressure value is smaller than the second pressure threshold, or the real-time temperature value is smaller than the second temperature threshold, the compressor 110 is controlled to increase the operating frequency until the real-time exhaust pressure value is greater than or equal to the preset pressure value and the real-time temperature value is greater than or equal to the preset temperature value.

Alternatively, in step S302, the manner of controlling the compressor 110 to increase the operating frequency is: the operating frequency of the compressor 110 is controlled to increase by the second frequency value every third preset time. The value of the third preset time may range from 30s to 40s, in other words, the value of the third preset time may be 30s, 31s, 32s, 33s, 34s, 35s, 36s, 37s, 38s, 39s, or 40s, and the like. The value of the second frequency value may be 1Hz to 3Hz, in other words, the value of the second frequency value may be 1Hz, 2Hz, or 3Hz, and the like.

It should be noted that, since the temperature of the condenser 130 in the up-conversion state of the compressor 110 is increased faster than the temperature of the condenser 130 in the down-conversion state of the compressor 110, the third preset time is set to be longer than the second preset time, so that the operating frequency of the compressor 110 is prevented from fluctuating due to too fast temperature increase. In addition, in some embodiments of the present application, the first frequency value and the second frequency value may take the same value.

Step S303, if the real-time exhaust pressure value is less than or equal to the first pressure threshold and greater than or equal to the second pressure threshold, controlling the compressor 110 to maintain the current operating frequency until the refrigerant is recovered.

It should be noted that, when the real-time discharge pressure value is greater than the first pressure threshold value, or the real-time temperature value is greater than the first temperature threshold value, it indicates that the refrigerant recovery speed at this time is already optimal, but since the operating frequency of the compressor 110 is too high, the energy is excessively consumed, and therefore, the operating frequency of the compressor 110 needs to be reduced to prevent the excessive consumption of the energy. In order to prevent the condition that the recovery speed of the refrigerant is reduced due to the fact that the real-time exhaust pressure value is too small due to the over-adjustment and the real-time temperature value is too small due to the over-adjustment, the adjustment is suspended when the operation frequency of the compressor 110 is controlled to be reduced to enable the real-time exhaust pressure value to be less than or equal to the preset pressure value and the real-time temperature value to be less than or equal to the preset temperature value, so that the recovery speed of the refrigerant is prevented from being reduced.

In addition, when the real-time exhaust pressure value is smaller than the second pressure threshold value, or the real-time temperature value is smaller than the second temperature threshold value, it indicates that the refrigerant recovery speed at this time has not reached the optimal speed, and based on this, the operation frequency of the compressor 110 needs to be increased to increase the refrigerant recovery speed. In order to prevent excessive energy consumption caused by the increase of the operating frequency of the compressor 110 due to excessive regulation, the adjustment is suspended when the operating frequency of the compressor 110 is controlled to be increased such that the real-time discharge pressure value is greater than or equal to the preset pressure value and the real-time temperature value is greater than or equal to the preset temperature value, so as to prevent excessive energy consumption caused by the increase of the operating frequency of the compressor 110.

Certainly, when the real-time exhaust pressure value is less than or equal to the first pressure threshold and greater than or equal to the second pressure threshold, it indicates that the real-time exhaust pressure value is already in a state approaching to the preset pressure value, so that the compressor 110 can be controlled to maintain the current operation state until the refrigerant recovery is completed, and the problem that energy is excessively consumed and is not beneficial to energy saving can be solved while the refrigerant recovery efficiency is ensured to be improved.

After the operating frequency of the compressor 110 is adjusted, in order to ensure the control accuracy, the refrigerant recovery control method may further include:

step S334, after controlling the compressor 110 to adjust the operation frequency, controlling the compressor 110 to operate for a first preset time, returning to re-perform the step of comparing at least one of the first pressure threshold and the second pressure threshold with the real-time exhaust pressure value, and the step of comparing at least one of the first temperature threshold and the second temperature threshold with the real-time temperature value.

In other words, after the operation frequency of the compressor 110 is adjusted in step S333, in order to determine whether the operation frequency of the compressor 110 is adjusted, the process may return to step S301 and step S302 again to determine the real-time exhaust pressure value and the real-time temperature value, thereby determining the refrigerant recovery rate and whether the energy consumption is excessive.

In addition, if the real-time exhaust pressure value and the real-time temperature value do not reach the approximate preset pressure value and the approximate preset temperature value, the operation frequency of the compressor 110 may be adjusted again, in other words, the step S333 is repeatedly executed, so that the operation frequency of the compressor 110 is adjusted in place, thereby ensuring that the recovery speed of the refrigerant can be adjusted to the optimum, and effectively preventing the excessive energy consumption. Therefore, the operation frequency of the compressor 110 can be precisely adjusted to achieve the condition that the refrigerant recovery speed is optimal and energy is not excessively consumed through multiple times of adjustment.

Of course, in some cases, after the step S333 is repeatedly executed for a plurality of times, the operation frequency of the compressor 110 cannot reach a state where the real-time discharge pressure value is between the first pressure threshold and the second pressure threshold, at this time, referring to fig. 9, in order to prevent the operation frequency of the compressor 110 from fluctuating repeatedly, the refrigerant recovery control method may further include:

step S1, count once for each time the compressor 110 is continuously controlled to complete the raising of the operating frequency and complete the lowering of the operating frequency.

In other words, in the case where step S301 and step S302 are continuously performed and the execution of step S301 is completed and the execution of step S302 is completed, one counting is performed.

Step S2, if the count reaches the preset number, after controlling the compressor 110 to increase the operating frequency, controlling the compressor 110 to operate at the increased operating frequency until the refrigerant is recovered.

Optionally, the value of the preset number of times may be 1 to 5 times, in other words, the preset number of times may be 1, 2, 3, 4, or 5 times.

In the case where the count reaches the preset number of times, it indicates that the operation frequency of the compressor 110 has been repeatedly adjusted a plurality of times. After that, if the compressor 110 executes step S301, it may proceed to step S334; if the compressor 110 performs the step S301, the operation of the compressor 110 may be controlled at the operation frequency after the operation frequency of the compressor 110 is adjusted in the step S302. At the moment, the refrigerant recovery speed can be ensured to be optimal, so that the refrigerant can be rapidly recovered; meanwhile, the damage of the compressor 110 caused by repeated shifting of the operating frequency of the compressor 110 can be avoided.

In summary, in the refrigerant recovery system 10 and the refrigerant recovery control method provided in the embodiment of the present application, during the refrigerant recovery process, the operating frequency of the compressor 110 affects the temperature of the refrigerant, and thus affects the temperature of the middle portion of the condenser 130, based on which the recovery speed of the refrigerant is related to the temperature of the middle portion of the condenser 130. In addition, under the condition that the temperature of the middle part of the condenser 130 reaches a preset temperature value, the recovery speed of the refrigerant reaches the best speed; if the operation frequency of the compressor 110 is continuously increased to increase the temperature of the middle portion of the condenser 130, the refrigerant recovery rate is not increased, and excessive energy consumption is caused, which is not favorable for energy saving. In addition, in the case where the middle of the condenser 130 reaches a preset temperature value, the discharge pressure of the compressor 110 reaches a preset pressure value. The control accuracy for controlling the operation frequency of the compressor 110 only by the temperature of the middle portion of the condenser 130 is low, so that the operation frequency of the compressor 110 is controlled by the real-time temperature value of the middle portion of the condenser 130 and the real-time exhaust pressure value of the compressor 110, the recovery speed of the refrigerant can be adjusted to the optimal speed, and the excessive consumption of energy can be prevented. Namely, the refrigerant recovery control method provided by the invention can solve the technical problem that energy is excessively consumed and energy is not beneficial to energy conservation in order to improve the recovery efficiency of the refrigerant in the prior art.

Referring to fig. 10, fig. 10 is a schematic diagram illustrating functional modules of a refrigerant recovery control device 20 according to an embodiment of the present disclosure, in order to execute possible steps of the refrigerant recovery control method according to the embodiments. The refrigerant recovery control device 20 is applied to the refrigerant recovery system 10, and the refrigerant recovery control device 20 according to the embodiment of the present application is used for executing the refrigerant recovery control method. It should be noted that the basic principle and the technical effects of the refrigerant recovery control device 20 provided in the present embodiment are substantially the same as those of the above embodiments, and for the sake of brief description, no part of the present embodiment is mentioned, and reference may be made to the corresponding contents in the above embodiments.

The refrigerant recovery control device 20 includes a first receiving module 21, a second receiving module 22, and a control module 23.

The first receiving module 21 is configured to receive a real-time discharge pressure value, where the real-time discharge pressure value indicates a real-time pressure of a refrigerant in a discharge pipe of the compressor 110.

Optionally, the first receiving module 21 may be configured to execute step S10 in the above-mentioned respective diagrams to achieve the corresponding technical effect.

The second receiving module 22 is adapted to receive a real-time temperature value indicative of a real-time temperature of the middle portion of the condenser 130.

Optionally, the second receiving module 22 may be configured to execute step S20 in the above-mentioned respective figures to achieve the corresponding technical effect.

Alternatively, the first receiving module 21 and the second receiving module 22 may be the same module.

The control module 23 is configured to control the compressor 110 to determine an operating frequency according to the real-time exhaust pressure value, the preset pressure value, the real-time temperature value, and the preset temperature value, so that the real-time exhaust pressure value approaches the preset pressure value.

Optionally, the control module 23 is configured to execute step S30 and its sub-steps in the above-mentioned figures to achieve the corresponding technical effect.

Of course, the control module 23 can also execute the steps S1, S2, S05, S06, and the like in the above-mentioned respective figures, and achieve the corresponding technical effects.

In the embodiments provided in the present application, it should be understood that the disclosed apparatus and method can be implemented in other ways. The apparatus embodiments described above are merely illustrative, and for example, the flowchart and block diagrams in the figures illustrate the architecture, functionality, and operation of possible implementations of apparatus, methods and computer program products according to various embodiments of the present invention. In this regard, each block in the flowchart or block diagrams may represent a module, segment, or portion of code, which comprises one or more executable instructions for implementing the specified logical function(s). It should also be noted that, in some alternative implementations, the functions noted in the block may occur out of the order noted in the figures. For example, two blocks shown in succession may, in fact, be executed substantially concurrently, or the blocks may sometimes be executed in the reverse order, depending upon the functionality involved. It will also be noted that each block of the block diagrams and/or flowchart illustration, and combinations of blocks in the block diagrams and/or flowchart illustration, can be implemented by special purpose hardware-based systems which perform the specified functions or acts, or combinations of special purpose hardware and computer instructions.

In addition, the functional modules in the embodiments of the present invention may be integrated together to form an independent part, or each module may exist separately, or two or more modules may be integrated to form an independent part.

The functions, if implemented in the form of software functional modules and sold or used as a stand-alone product, may be stored in a computer readable storage medium. Based on such understanding, the technical solution of the present invention may be embodied in the form of a software product, which is stored in a storage medium and includes instructions for causing a computer device (which may be a personal computer, a server, or a network device) to execute all or part of the steps of the method according to the embodiments of the present invention. And the aforementioned storage medium includes: a U-disk, a removable hard disk, a Read-Only Memory (ROM), a Random Access Memory (RAM), a magnetic disk or an optical disk, and other various media capable of storing program codes.

Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.

Claims

1. A refrigerant recovery control method is applied to a refrigerant recovery system and is characterized in that the refrigerant recovery system comprises a recovery pipeline, one end of the recovery pipeline is connected to a system to be recovered, and the other end of the recovery pipeline is connected to a recovery container; the recovery pipeline is provided with a compressor and a condenser, the compressor is used for extracting a gaseous refrigerant in the system to be recovered when in operation and guiding the refrigerant to the condenser so as to guide the refrigerant to the recovery container;

the refrigerant recovery control method comprises the following steps:

2. The refrigerant recovery control method according to claim 1, wherein the step of controlling the compressor to determine the operating frequency according to the real-time exhaust pressure value, the preset pressure value, the real-time temperature value, and the preset temperature value includes:

3. The refrigerant recovery control method according to claim 2, wherein the step of controlling the compressor to adjust the operating frequency according to the real-time discharge pressure value, the real-time temperature value, the first pressure threshold, the second pressure threshold, the first temperature threshold, and the second temperature threshold includes:

4. The refrigerant recovery control method according to claim 3, wherein the step of controlling the compressor to adjust the operating frequency or controlling the compressor to maintain the current operating frequency according to the magnitude relationship between the first pressure threshold, the second pressure threshold, and the real-time discharge pressure value and the magnitude relationship between the first temperature threshold, the second temperature threshold, and the real-time temperature value comprises: if the real-time exhaust pressure value is greater than the first pressure threshold value, or the real-time temperature value is greater than the first temperature threshold value, controlling the compressor to reduce the operating frequency until the real-time exhaust pressure value is less than or equal to the preset pressure value and the real-time temperature value is less than or equal to the preset temperature value;

5. The refrigerant recovery control method according to claim 4, wherein the step of controlling the compressor to reduce the operating frequency includes:

and the second preset time is less than the third preset time.

6. The refrigerant recovery control method according to claim 4, further comprising:

7. The refrigerant recovery control method according to claim 2, wherein the step of calculating the first pressure threshold and the second pressure threshold according to the preset pressure value includes:

8. The refrigerant recovery control method according to any one of claims 1 to 7, further comprising, before receiving the real-time discharge pressure value:

if yes, executing a step of receiving a real-time exhaust pressure value;

9. A refrigerant recovery control device is applied to a refrigerant recovery system and is characterized in that the refrigerant recovery system comprises a recovery pipeline, one end of the recovery pipeline is connected to a system to be recovered, and the other end of the recovery pipeline is connected to a recovery container; the recovery pipeline is provided with a compressor and a condenser, the compressor is used for extracting a gaseous refrigerant in the system to be recovered when in operation and guiding the refrigerant to the condenser so as to guide the refrigerant to the recovery container;

the refrigerant recovery control device includes:

the second receiving module is used for receiving a real-time temperature value, and the real-time temperature value represents the real-time temperature of the middle part of the condenser;

10. A refrigerant recovery system is characterized by comprising a recovery pipeline, wherein one end of the recovery pipeline is connected to a system to be recovered, and the other end of the recovery pipeline is connected to a recovery container; the recovery pipeline is provided with a compressor and a condenser, the compressor is used for extracting a gaseous refrigerant in the system to be recovered when in operation and guiding the refrigerant to the condenser so as to guide the refrigerant to the recovery container; the refrigerant recovery system also comprises a pressure detection device, a temperature detection device and a controller; the pressure detection device is arranged on an exhaust pipe of the compressor so as to detect a real-time exhaust pressure value of the exhaust pipe; the temperature detection device is arranged in the middle of the condenser to detect a real-time temperature value of the condenser; the pressure detection device and the temperature detection device are both electrically connected with a controller, and the controller is used for receiving the real-time exhaust pressure value and the real-time temperature value and executing the refrigerant recovery control method according to any one of claims 1 to 8.