Refrigeration system

Abstract

The invention provides a refrigerating system. The refrigerating system comprises a compressor, a lubricant storage device, a heating device and a power device. The lubricant storage device is in fluid communication with the compressor through a lubricant pipeline, and lubricant circulation is formed, so that lubricant in the compressor can flow into the lubricant storage device from the compressor, and lubricant in the lubricant storage device can flow into the compressor. The heating device is configured to heat the lubricant in the lubricant storage device. And the power device is configured to enable the lubricant in the lubricant pipeline to flow into the lubricant storage device and enable the lubricant in the lubricant storage device to flow into the lubricant pipeline. The refrigerating system is simple in structure, and the temperature in the refrigerant pipeline can be effectively kept, so that quick starting of the refrigerating system is achieved.

Description

Technical Field

[0001] The present application relates to the field of refrigeration systems. Background Art

[0002] The refrigeration system comprises a compressor and a lubricant storage device, wherein the compressor and the lubricant storage device are fluidically connected to form a lubricant circulation.

[0003] After the refrigeration system is shut down, when the ambient temperature of the lubricant storage device is low, the refrigeration system sometimes fails to start and needs to be started multiple times. Summary of the invention

[0004] Exemplary embodiments of the present application may address at least some of the above-mentioned problems.

[0005] The present application provides a refrigeration system, which includes a compressor, a lubricant storage device, a heating device and a power device. The lubricant storage device is in fluid communication with the compressor through a lubricant pipeline and forms a lubricant circulation, so that the lubricant in the compressor can flow from the compressor into the lubricant storage device and the lubricant in the lubricant storage device can flow into the compressor. The heating device is configured to heat the lubricant in the lubricant storage device. The power device is configured to make the lubricant in the lubricant pipeline flow into the lubricant storage device and make the lubricant in the lubricant storage device flow into the lubricant pipeline.

[0006] According to the refrigeration system, it also includes a control device. The control device is connected to the power device in communication, so as to control the opening and closing of the power device. The control device starts the power device according to the shutdown time t1 of the power device. The shutdown time t1 is related to the amount of refrigerant in the lubricant pipeline that changes from gas to liquid.

[0007] According to the refrigeration system, the shutdown duration t1 of the power device is determined based on the following factors: the ratio of the heat W1 that can be released by the lubricant in the lubricant storage device and the heat W2 absorbed by the condensed refrigerant in the lubricant pipeline from liquid to gas per unit time.

[0008] According to the refrigeration system, the ratio of the heat W1 that can be released by the lubricant in the lubricant storage device to the heat W2 absorbed by the condensed refrigerant in the lubricant pipeline when changing from liquid to gas per unit time is determined based on at least the following factors: the evaporation saturation temperature Te of the refrigerant, the ambient temperature To, the compressor corrected heat transfer coefficient Ka, the properties of the refrigerant and the properties of the lubricant.

[0009] According to the refrigeration system, the compressor modified heat transfer coefficient Ka is determined based on at least the following factors: the manufacturing material, size and specific structure of the compressor.

[0010] According to the refrigeration system, the heat W1 that can be released by the lubricant in the lubricant storage device is determined based on at least the following factors: the lubricant temperature Ty in the lubricant storage device, the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device, the total amount of lubricant Qy in the lubricant storage device and the specific heat Cy of the lubricant.

[0011] According to the refrigeration system, the heat W1 that can be released by the lubricant in the lubricant storage device satisfies:

[0012] W1=(Ty-Ts)*Qy*Cy.

[0013] According to the refrigeration system, the heat W2 absorbed by the condensed refrigerant in the lubricant pipeline when it changes from liquid to gas per unit time is determined based on at least the following factors: the condensation rate Qt of the refrigerant, the specific heat Cr of the refrigerant, the lubricant temperature Ty in the lubricant storage device, the saturated gaseous enthalpy value hv of the refrigerant, and the saturated liquid enthalpy value hl of the refrigerant.

[0014] According to the refrigeration system, the heat W2 absorbed by the refrigerant from liquid to gas in unit time satisfies:

[0015] W2=Qt*(Cr(Ty-To)+(hv-hl)).

[0016] According to the refrigeration system, the condensation rate Qt of the refrigerant is determined based on the following factors: the ratio of the heat dissipation W3 of the compressor and the heat dissipation W4 of the unit mass of gaseous refrigerant at temperature Te converted into liquid refrigerant at temperature To.

[0017] According to the refrigeration system, the heat dissipation W3 of the compressor satisfies:

[0018] W3 = Ka*(Te-To);

[0019] The heat dissipation W4 of a unit mass of gaseous refrigerant at temperature Te turning into liquid refrigerant at temperature To satisfies:

[0020] W4=(hv-hl)+Cr(Te-To);

[0021] Among them, the value range of the compressor corrected heat transfer coefficient Ka is: 0.001≤Ka≤0.2.

[0022] According to the refrigeration system, the operating time of the power device is related to the time during which the fluid in the lubricant line is replaced by the fluid in the lubricant storage device.

[0023] According to the refrigeration system, it also includes a lubricant temperature detection device, which is configured to detect the temperature of the lubricant in the lubricant storage device. The control device is in communication with the lubricant temperature detection device and is configured to: when the temperature Ty of the lubricant detected by the lubricant temperature detection device is less than or equal to the power setting temperature Tm, the control device shuts down the power device.

[0024] According to the refrigeration system, it also includes a lubricant pressure detection device. The lubricant pressure detection device is configured to detect the pressure in the lubricant storage device. The control device is in communication connection with the lubricant pressure detection device. The power setting temperature Tm is related to the refrigerant saturation temperature Ts corresponding to the pressure detected by the lubricant pressure detection device.

[0025] According to the refrigeration system, it also includes an evaporator and an evaporator pressure detection device. The evaporator is in fluid communication with the compressor. The evaporator pressure detection device is configured to detect the evaporation pressure in the evaporator. The control device is in communication connection with the evaporator pressure detection device. The evaporation saturation temperature Te of the refrigerant is the evaporation saturation temperature corresponding to the evaporation pressure in the evaporator detected by the evaporator pressure detection device.

[0026] The refrigeration system of the present application has a simple structure and can effectively maintain the temperature in the refrigerant pipeline, thereby achieving rapid startup of the refrigeration system. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] The features and advantages of the present application may be better understood by reading the following detailed description with reference to the accompanying drawings, in which like reference numerals refer to like components throughout, wherein:

[0028] Figure 1 is a system diagram of the refrigeration system of the present application;

[0029] Figure 2A is a control system diagram of the refrigeration system of the present application;

[0030] Figure 2B is an embodiment of a table corresponding to refrigerant pressure and saturation temperature;

[0031] Figure 3 yes Figure 2A A schematic internal structure diagram of the control device shown;

[0032] Figure 4 It is used to control Figure 1 and Figure 2A The control flow chart of the refrigeration system is shown. DETAILED DESCRIPTION

[0033] Various specific embodiments of the present application will be described below with reference to the accompanying drawings which constitute a part of this specification. It should be understood that in the following drawings, the same parts use the same figure numbers.

[0034] Various specific embodiments of the present application will be described below with reference to the accompanying drawings that form a part of this specification. It should be understood that although terms indicating directions, such as "upper", "lower", "left", "right", "inner", "outer", etc., are used in this application to describe various example structural parts and elements of the present application, these terms are used here only for the purpose of convenience of description, and these terms are determined based on the exemplary orientations shown in the accompanying drawings. Since the embodiments disclosed in the present application can be set in different directions, these terms indicating directions are only for illustration and should not be regarded as limitations.

[0035] Figure 1 is a system diagram of the refrigeration system of this application. Figure 1 As shown, the refrigeration system includes a compressor 102, a condenser 103, a throttling device 105, an evaporator 107 and a refrigerant pipeline. Specifically, the refrigerant pipeline fluidly connects the compressor 102, the condenser 103, the throttling device 105 and the evaporator 107 in sequence, and forms a refrigeration cycle. Specifically, the refrigerant pipeline includes a first refrigerant pipeline 131, a second refrigerant pipeline 132, a third refrigerant pipeline 133 and a fourth refrigerant pipeline 134. The first refrigerant pipeline 131 connects the refrigerant outlet of the compressor 102 with the inlet of the condenser 103. The second refrigerant pipeline 132 connects the outlet of the condenser 103 with the inlet of the throttling device 105. The third refrigerant pipeline 133 connects the outlet of the throttling device 105 with the inlet of the evaporator 107. The fourth refrigerant pipeline 134 connects the outlet of the evaporator 107 with the refrigerant inlet of the compressor 102.

[0036] like Figure 1As shown, when the refrigeration system is started, the refrigerant is compressed into a high-temperature and high-pressure refrigerant in the compressor 102. The high-temperature and high-pressure refrigerant (i.e., gaseous refrigerant) flowing out of the compressor 102 flows through the first refrigerant pipe 131 and enters the condenser 103. In the condenser 103, the high-temperature and high-pressure refrigerant exchanges heat with the fluid with a lower temperature on the air side, thereby becoming a high-temperature and high-pressure refrigerant (i.e., liquid refrigerant). The high-temperature and high-pressure refrigerant flows through the second refrigerant pipe 132 and flows to the throttling device 105. The high-temperature and high-pressure refrigerant becomes a low-temperature and low-pressure refrigerant after flowing through the throttling device 105, and then flows through the third refrigerant pipe 133 and flows into the evaporator 107. In the evaporator 107, the low-temperature and low-pressure refrigerant exchanges heat with the fluid with a higher temperature on the user side, thereby reducing the temperature of the user side fluid to provide the user with a lower temperature fluid (for example, for providing air conditioning cold water). The low-temperature and low-pressure refrigerant becomes a low-temperature and low-pressure gas refrigerant after heat exchange with the user side fluid in the evaporator 107. The low-temperature and low-pressure gas refrigerant re-enters the compressor 102 through the fourth refrigerant pipe 134. Thus, the refrigeration cycle is completed.

[0037] like Figure 1 As shown, the refrigeration system further includes a lubricant storage device 104, a heating device 122, a power device 124 and a lubricant pipeline. Specifically, the lubricant pipeline includes a first lubricant pipeline 141 and a second lubricant pipeline 142. The lubricant storage device 104 is configured to store lubricant. The heating device 122 is configured to heat the lubricant in the lubricant storage device 104. In the present application, the heating device 122 is disposed in the lubricant storage device 104, thereby heating the lubricant in the lubricant storage device 104. The first lubricant pipeline 141 connects the lubricant outlet of the compressor 102 and the inlet of the heating device 122. The second lubricant pipeline 142 connects the outlet of the heating device 122 and the lubricant inlet of the compressor 102. The lubricant pipeline connects the compressor 102 and the lubricant storage device 104 fluidly, and forms a lubricant circulation, so that the lubricant in the compressor 102 can flow from the compressor 102 to the lubricant storage device 104 and the lubricant in the lubricant storage device 104 can flow into the compressor 102. The power device 124 is configured to allow the lubricant in the lubricant line to flow into the lubricant storage device 104, and to allow the lubricant in the lubricant storage device 104 to flow into the lubricant line. In the present application, the power device 124 is disposed in the lubricant storage device 104. When the refrigeration system is started, the power device 124 is started, so that the lubricant can enter the compressor 102 and then return to the lubricant storage device 104. When the refrigeration system is turned off, the heating device 122 can be started to increase the temperature of the lubricant, and the power device 124 can be started, so that the lubricant in the lubricant line flows into the lubricant storage device 104, and the lubricant in the lubricant storage device 104 flows into the lubricant line.

[0038] It should be noted that, although the power device 124 in the present application is disposed in the lubricant storage device 104 , in other embodiments, the power device 124 may be disposed at any point in the lubricant circulation.

[0039] Figure 2A : is a control system diagram of the refrigeration system of this application. Figure 2A As shown, the refrigeration system further includes a control device 202, a lubricant temperature detection device 204, a lubricant pressure detection device 205, and an ambient temperature detection device 206. The lubricant temperature detection device 204 is configured to detect the temperature Ty of the lubricant in the lubricant storage device 104. The lubricant pressure detection device 205 is configured to detect the pressure in the lubricant storage device 104. In this embodiment, the lubricant temperature detection device 204 and the lubricant pressure detection device 205 are arranged in the lubricant storage device 104. The ambient temperature detection device 206 is arranged in the environment where the refrigeration system (for example, the compressor 102) is located, and is configured to detect the temperature To of the environment where the refrigeration system is located. The control device 202 is connected to the lubricant temperature detection device 204, the lubricant pressure detection device 205, and the ambient temperature detection device 206 through the connection line 216, the connection line 217, and the connection line 218, respectively, and is configured to receive signals sent by the lubricant temperature detection device 204, the lubricant pressure detection device 205, and the ambient temperature detection device 206.

[0040] In addition, the control device 202 is connected to the heating device 122 through the connection 212, and is configured to control the opening and closing of the heating device 122. Specifically, the control device 202 is configured to: when the current lubricant temperature Ty detected by the lubricant temperature detection device 204 is less than or equal to the first heating setting temperature Tn1, the control device 202 starts the heating device 122, and when the current lubricant temperature detected by the lubricant temperature detection device 204 is greater than the second heating setting temperature Tn2, the control device 202 turns off the heating device 122. The first heating setting temperature Tn1 is related to the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device 104. The second heating setting temperature Tn2 is equal to or greater than the first heating setting temperature Tn1. As an example, the first heating setting temperature Tn1 is the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device 104 + 30 ° C, and the second heating setting temperature Tn2 is 7 ° C higher than the first heating setting temperature Tn1.

[0041] like Figure 2AAs shown, the control device 202 is connected to the power device 124 through the connection 214, and is configured to control the opening and closing of the power device 124. The operating time of the control device 202 is related to the time when the fluid in the lubricant pipeline is replaced by the fluid in the lubricant storage device 104. Specifically, the control device 202 is configured to: when the current lubricant temperature Ty detected by the lubricant temperature detection device 204 is less than or equal to the power setting temperature Tm, the control device 202 turns off the power device 124. When the current lubricant temperature Ty detected by the lubricant temperature detection device 204 is less than or equal to the power setting temperature Tm, it means that the current temperature of the lubricant in the lubricant storage device 104 is not enough to replace the lubricant in the lubricant pipeline and change the lubricant flowing into the lubricant storage device 104 from liquid to gas, so the control device 202 turns off the power device 124 at this time. The power setting temperature Tm is related to the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device 104. In the embodiment of the present application, the power setting temperature Tm is greater than the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device 104. As an example, the power setting temperature Tm is 16°C higher than the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device 104.

[0042] In addition, the control device 202 is further configured to start the power device 124 according to the shutdown time t1 of the power device 124. Specifically, the shutdown time t1 is related to the amount of refrigerant in the lubricant pipeline that changes from gas to liquid. In the embodiment of the present application, the shutdown time t1 is determined based on the following factors: the ratio of the heat W1 that can be released by the lubricant in the lubricant storage device 104 to the heat W2 absorbed by the condensed refrigerant in the lubricant pipeline when it changes from liquid to gas per unit time.

[0043] like Figure 2A As shown, the refrigeration system further includes an evaporator pressure detection device 208. The evaporator pressure detection device 208 is disposed in the evaporator 107 and is configured to detect the evaporation pressure of the evaporator 107. The control device 202 is communicatively connected to the evaporator pressure detection device 208 via a connection line 220, and is configured to receive a signal from the evaporator pressure detection device 208. The control device 202 is also configured to obtain a corresponding evaporation saturation temperature Te of the refrigerant based on the signal from the evaporator pressure detection device 208.

[0044] Figure 2Bis an embodiment of a table of correspondence between refrigerant pressure and saturation temperature. After the pressure of the refrigerant is detected, its corresponding saturation temperature can be obtained by looking up the table. For example, based on the current pressure in the lubricant storage device 104, the corresponding refrigerant saturation temperature is obtained by looking up the table. For example, based on the current pressure in the evaporator pressure detection device 208, the corresponding evaporation saturation temperature of the refrigerant is obtained by looking up the table.

[0045] In the present application, the ratio of the heat W1 that can be released by the lubricant in the lubricant storage device 104 to the heat W2 absorbed by the condensed refrigerant in the lubricant pipeline when changing from liquid to gas per unit time is determined based on at least the following factors: the evaporation saturation temperature Te of the refrigerant corresponding to the evaporation pressure of the evaporator 107 detected by the evaporator pressure detection device 208, the ambient temperature To detected by the ambient temperature detection device 206, the compressor corrected heat transfer coefficient Ka, the properties of the refrigerant and the properties of the lubricant.

[0046] In the present application, the amount of heat W1 that can be released by the lubricant in the lubricant storage device 104 is determined based on at least the following factors: the lubricant temperature Ty detected by the lubricant temperature detection device 204, the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device 104 detected by the lubricant pressure detection device 205, the total amount of lubricant Qy in the lubricant storage device 104, and the specific heat Cy of the lubricant. Specifically, the amount of heat W1 that can be released by the lubricant satisfies:

[0047] W1=(Ty-Ts)*Qy*Xy.

[0048] In the present application, the amount of heat W2 absorbed by the condensed refrigerant in the lubricant pipeline from liquid to gas per unit time is determined based on at least the following factors: the condensation rate Qt of the refrigerant, the specific heat Cr of the refrigerant, the lubricant temperature Ty detected by the lubricant temperature detection device 204, the saturated gaseous enthalpy value hv of the refrigerant, and the saturated liquid enthalpy value hl of the refrigerant. Specifically, the amount of heat W2 absorbed by the condensed refrigerant in the lubricant pipeline from liquid to gas per unit time satisfies:

[0049] W2=Qt*(Cr(Ty-To)+(hv-hl)).

[0050] The refrigerant condensation rate Qt is determined based on the ratio of the heat dissipation W3 of the compressor 102 and the heat dissipation W4 of a unit mass of gaseous refrigerant at a temperature Te converted into liquid refrigerant at a temperature To.

[0051] Specifically, the heat dissipation W3 of the compressor 102 satisfies:

[0052] W3 = Ka*(Te-To).

[0053] The compressor modified heat transfer coefficient Ka is determined based on at least the following factors: the material, size and specific structure of the compressor 102. The value range of the compressor modified heat transfer coefficient Ka is: 0.001≤Ka≤0.2, wherein the unit of the compressor modified heat transfer coefficient Ka is Kw / °C. As an example, when the thermal conductivity of the material of the compressor 102 is high, the size of the compressor 102 is large or the structure of the compressor 102 is complex, the value of Ka is large.

[0054] The heat dissipation W4 of a unit mass of gaseous refrigerant at temperature Te turning into liquid refrigerant at temperature To satisfies:

[0055] W4=(hv-hl)+Cr(Te-To).

[0056] Figure 3 yes Figure 2A The schematic internal structure diagram of the control device 202 is shown in FIG. Figure 3 As shown, the control device 202 includes a bus 341, a processor 342, an input device 343, an output device 344, and a memory 345 having a control program 346. The various components in the control device 202, including the processor 342, the input device 343, the output device 344, and the memory 345 are communicatively connected to the bus 341, so that the processor 342 can control the operation of the input device 343, the output device 344, and the memory 345. Specifically, the memory 345 is used to store programs, instructions, and data, and the processor 342 reads programs, instructions, and data from the memory 345, and can write data to the memory 345. By executing the programs and instructions read from the memory 345, the processor 342 controls the operation of the input device 343 and the output device 344. The input device 343 receives external signals and data through the connections 216, 217, 218, and 220, including the lubricant temperature detected by the lubricant temperature detection device 204, the lubricant pressure detected by the lubricant pressure detection device 205, the ambient temperature detected by the ambient temperature detection device 206, and the evaporation pressure detected by the evaporator pressure detection device 208. The output device 344 sends control signals to the heating device 122 and the power device 124 through the connection 212 and the connection 214, respectively, so as to control the opening and closing of the heating device 122 and the power device 124, respectively.

[0057] In the embodiment of the present application, the Figure 4The program of the flowchart shown in is stored in the memory 345 of the control device 202. The control device 202 controls the refrigeration system by executing the program stored in the control device 202 by the processor 342. The memory 345 also stores: a table of refrigerant pressure and saturation temperature, a compressor modified heat transfer coefficient Ka, a total amount of lubricant Qy in the lubricant storage device 104, a specific heat of the refrigerant Cr, a specific heat of the lubricant Cy, a refrigerant saturated gas enthalpy value hv and a refrigerant saturated liquid enthalpy value hl, etc. As an example, the table of refrigerant pressure and saturation temperature can be found in Figure 2B , the corrected heat transfer coefficient Ka of the compressor is 0.1 Kw / ℃, the total amount of lubricant Qy in the lubricant storage device 104 is 80 kg, the specific heat Cr of the refrigerant is 0.92 kJ / kg / ℃, the specific heat Cy of the lubricant is 1.951 kJ / kg / ℃, the saturated gas enthalpy value hv of the refrigerant is 392 kJ / kg and the saturated liquid enthalpy value hl of the refrigerant is 216 kJ / kg.

[0058] In addition, Figure 2A Specific data such as the specific values ​​detected by the lubricant temperature detection device 204, the lubricant pressure detection device 205, the ambient temperature detection device 206 and the evaporator pressure detection device 208 and the shutdown time point of the power device 124 are also stored in the memory 345.

[0059] Figure 4 It is used to control Figure 1 and Figure 2A The control flow chart of the refrigeration system is shown in Figure 1. Figure 4 As shown, when the refrigeration system is turned off, the processor 342 transfers the operation to step 402.

[0060] In step 402, the processor 342 activates the power plant 124. The processor 342 then transfers the operation to step 404.

[0061] In step 404, the processor 342 obtains the temperature Ty of the lubricant in the lubricant storage device 104 through the lubricant temperature detection device 204, obtains the refrigerant saturation temperature Ts under the corresponding pressure through the pressure in the lubricant storage device 104 detected by the lubricant pressure detection device 205 and the refrigerant pressure and saturation temperature correspondence table, and determines the power setting temperature Tm through the refrigerant saturation temperature Ts. Subsequently, the processor 342 transfers the operation to step 406.

[0062] In step 406, the processor 342 determines whether the current lubricant temperature Ty is less than or equal to the power setting temperature Tm. If the current lubricant temperature Ty is greater than the power setting temperature Tm, the processor 342 returns the operation to step 404. If the current lubricant temperature Ty is less than or equal to the power setting temperature Tm, it means that the temperature of the refrigerant in the lubricant storage device 104 is not enough to replace the liquid refrigerant in the lubricant pipeline and change it from liquid to gas, so the processor 342 returns the operation to step 408.

[0063] In step 408, the processor 342 shuts down the power plant 124. The processor 342 then transfers the operation to step 412.

[0064] In step 412, the processor 342 obtains the ambient temperature To through the ambient temperature detection device 206, and obtains the evaporation saturation temperature Te of the refrigerant under the corresponding pressure through the evaporation pressure of the evaporator 107 detected by the evaporator pressure detection device 208 and the corresponding table of the pressure and saturation temperature of the refrigerant. Subsequently, the processor 342 transfers the operation to step 414.

[0065] In step 414, the processor 342 calculates t1 through the compressor corrected heat transfer coefficient Ka, the total amount of lubricant Qy in the lubricant storage device 104, the specific heat Cr of the refrigerant, the specific heat Cy of the lubricant, the saturated gas enthalpy value hv of the refrigerant and the saturated liquid enthalpy value hl of the refrigerant, the current lubricant temperature Ty, the current ambient temperature To, the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device 104, and the evaporation saturation temperature Te of the refrigerant corresponding to the evaporation pressure of the evaporator 107, which are stored in the memory 345. Specifically, t1 satisfies:

[0066]

[0067] W1=(Ty-Ts)*Qy*Cy;

[0068] W2=Qt*(Cr(Ty-To)+(hv-hl));

[0069]

[0070] W3 = Ka*(Te-To);

[0071] W4=(hv-hl)+Cr(Te-To).

[0072] The processor 342 then moves the operation to step 416 .

[0073] In step 416, the processor 342 determines whether the time length t of shutting down the power device 124 is greater than or equal to the shutdown time length t1. If the time length t of shutting down the power device 124 is less than the shutdown time length t1, the processor 342 waits for a period of time (e.g., 5 seconds) and continues to return to step 416 for determination. If the time length t of shutting down the power device 124 is greater than or equal to the shutdown time length t1, the processor 342 transfers the operation to step 418.

[0074] In step 418, the processor 342 determines whether the refrigeration system is on. If the refrigeration system is on, then the process ends. If the refrigeration system is still off, the processor 342 transfers the operation to step 402 and starts the power plant 124 in step 402.

[0075] It should be noted that, in one embodiment, when the evaporation saturation temperature Te of the refrigerant corresponding to the evaporation pressure of the evaporator 107 detected by the evaporator pressure detection device 208 is close to the ambient temperature To detected by the ambient temperature detection device 206, the value of the shutdown time t1 will approach infinity. Therefore, when the shutdown time t1 is greater than 86400s, the processor 342 will assign 86400s to the shutdown time t1. In other words, when the shutdown time t1 is greater than 86400s, the shutdown time t1 is 86400s.

[0076] In the prior art, after the refrigeration system is shut down, when the ambient temperature of the lubricant storage device is low, the refrigeration system sometimes fails to start and needs to be started multiple times. The inventors of the present application found that this is because when the ambient temperature is low, the refrigerant in the lubricant pipeline becomes liquid. When the refrigeration system is started, the liquid refrigerant enters the lubricant storage device, lowering the temperature of the lubricant in the lubricant storage device, causing the temperature of the lubricant entering the compressor to be too low, thereby causing the compressor to fail to start.

[0077] The refrigeration system of the present application has a simple structure and can effectively maintain the temperature in the refrigerant pipeline, thereby realizing rapid startup of the refrigeration system. Specifically, in the present application, the refrigeration system includes a lubricant storage device, a power device and a heating device. The lubricant in the lubricant pipeline can flow into the lubricant storage device through the power device and be heated by the heating device. The lubricant in the lubricant storage device can replace the lubricant in the lubricant pipeline to flow into the compressor, thereby ensuring the startup of the compressor. The refrigeration system of the present application does not need to set auxiliary heating equipment / insulation facilities for the compressor and the lubricant pipeline, and has a simple structure. In addition, the refrigeration system of the present application can reduce the frequent start and stop of the power device and save electricity. Specifically, in the present application, the control device controls the startup of the power device by the shutdown time t1. The shutdown time t1 is related to the amount of refrigerant in the lubricant pipeline that changes from gas to liquid, thereby preventing the liquid refrigerant in the lubricant pipeline from entering the lubricant storage device to reduce the temperature of the lubricant in the lubricant storage device too much.

[0078] Although the present disclosure has been described in conjunction with the examples of the embodiments summarized above, various alternatives, modifications, changes, improvements and / or substantially equivalent solutions, whether known or currently or foreseeable in the near future, may be apparent to those of ordinary skill in the art. In addition, the technical effects and / or technical problems described in this specification are exemplary rather than restrictive; so the disclosure in this specification may be used to solve other technical problems and have other technical effects and / or may solve other technical problems. Therefore, the examples of the embodiments of the present disclosure as stated above are intended to be illustrative rather than restrictive. Various changes may be made without departing from the spirit or scope of the present disclosure. Therefore, the present disclosure is intended to include all known or earlier developed alternatives, modifications, changes, improvements and / or substantially equivalent solutions.

Claims

1. A refrigeration system, characterized in that: The refrigeration system comprises: Compressor (102); a lubricant storage device (104), the lubricant storage device (104) being in fluid communication with the compressor (102) through a lubricant pipeline and forming a lubricant circulation, so that the lubricant in the compressor (102) can flow from the compressor (102) into the lubricant storage device (104) and the lubricant in the lubricant storage device (104) can flow into the compressor (102); a heating device (122), the heating device (122) being configured to heat the lubricant in the lubricant storage device (104); and A power device (124) is configured to make the lubricant in the lubricant pipeline flow into the lubricant storage device (104), and to make the lubricant in the lubricant storage device (104) flow into the lubricant pipeline.

2. The refrigeration system according to claim 1, characterized in that: The refrigeration system further comprises: A control device (202), the control device (202) being in communication with the power device (124) so ​​as to control the opening and closing of the power device (124); Wherein, the control device (202) starts the power device (124) according to the shutdown time t1 of the power device (124); The outage duration t1 is related to the amount of refrigerant in the lubricant pipeline that changes from gas to liquid.

3. The refrigeration system according to claim 2, characterized in that: The shutdown time t1 of the power device (124) is determined based on the following factors: the ratio of the heat W1 that can be released by the lubricant in the lubricant storage device (104) and the heat W2 absorbed by the condensed refrigerant in the lubricant pipeline when it changes from liquid to gas per unit time.

4. The refrigeration system according to claim 3, characterized in that: The ratio of the heat W1 that can be released by the lubricant in the lubricant storage device (104) to the heat W2 absorbed by the condensed refrigerant in the lubricant pipeline per unit time when it changes from liquid to gas is determined based on at least the following factors: The evaporation saturation temperature Te of the refrigerant, the ambient temperature To, the compressor corrected heat transfer coefficient Ka, the properties of the refrigerant and the properties of the lubricant.

5. The refrigeration system according to claim 4, characterized in that: The compressor modified heat transfer coefficient Ka is determined based on at least the following factors: the manufacturing material, size and specific structure of the compressor (102).

6. The refrigeration system according to claim 3, characterized in that: The amount of heat W1 that can be released by the lubricant in the lubricant storage device (104) is determined based on at least the following factors: the lubricant temperature Ty in the lubricant storage device (104), the refrigerant saturation temperature Ts corresponding to the pressure in the lubricant storage device (104), the total amount of lubricant Qy in the lubricant storage device (104), and the specific heat Cy of the lubricant.

7. The refrigeration system according to claim 6, characterized in that: The heat W1 that can be released by the lubricant in the lubricant storage device (104) satisfies: W1=(Ty-Ts)*Qy*Cy.

8. The refrigeration system according to claim 3, characterized in that: The heat W2 absorbed by the condensed refrigerant in the lubricant pipeline when it changes from liquid to gas per unit time is determined based on at least the following factors: the condensation rate Qt of the refrigerant, the specific heat Cr of the refrigerant, the lubricant temperature Ty in the lubricant storage device (104), the saturated gaseous enthalpy value hv of the refrigerant, and the saturated liquid enthalpy value hl of the refrigerant.

9. The refrigeration system according to claim 8, characterized in that: The heat W2 absorbed by the refrigerant from liquid to gas in unit time satisfies: W2=Qt*(Cr(Ty-To)+(hv-hl)).

10. The refrigeration system according to claim 9, characterized in that: The condensation rate Qt of the refrigerant is determined based on the following factors: the ratio of the heat dissipation W3 of the compressor (102) and the heat dissipation W4 of a unit mass of gaseous refrigerant at a temperature Te converted into liquid refrigerant at a temperature To.

11. The refrigeration system according to claim 10, characterized in that: The heat dissipation W3 of the compressor (102) satisfies: W3 = Ka*(Te-To); The heat dissipation W4 of a unit mass of gaseous refrigerant at temperature Te becoming liquid refrigerant at temperature To satisfies: W4=(hv-hl)+Cr(Te-To); Among them, the value range of the compressor corrected heat transfer coefficient Ka is: 0.001≤Ka≤0.

2.

12. The refrigeration system according to claim 2, characterized in that: The operating period of the power plant (124) is related to the period of time during which the fluid in the lubricant line is replaced by the fluid in the lubricant storage device (104).

13. The refrigeration system according to claim 12, characterized in that: The refrigeration system further comprises: a lubricant temperature detection device (204), the lubricant temperature detection device (204) being configured to detect the temperature of the lubricant in the lubricant storage device (104); The control device (202) is in communication with the lubricant temperature detection device (204) and is configured to: When the lubricant temperature Ty detected by the lubricant temperature detection device (204) is less than or equal to the power setting temperature Tm, the control device (202) turns off the power device (124).

14. The refrigeration system according to claim 13, characterized in that: The refrigeration system further comprises: a lubricant pressure detection device (205), the lubricant pressure detection device (205) being configured to detect the pressure in the lubricant storage device (104); The control device (202) is communicatively connected with the lubricant pressure detection device (205); The power setting temperature Tm is related to the refrigerant saturation temperature Ts corresponding to the pressure detected by the lubricant pressure detection device (205).

15. The refrigeration system according to claim 4, characterized in that: The refrigeration system further comprises: an evaporator (107), the evaporator (107) being in fluid communication with the compressor (102); and an evaporator pressure detection device (208), the evaporator pressure detection device (208) being configured to detect the evaporation pressure in the evaporator (107); Wherein, the control device (202) is communicatively connected with the evaporator pressure detection device (208); The evaporation saturation temperature Te of the refrigerant is the evaporation saturation temperature corresponding to the evaporation pressure in the evaporator (107) detected by the evaporator pressure detection device (208).

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