CN218781453U - Cooling system and air conditioning unit - Google Patents
Cooling system and air conditioning unit Download PDFInfo
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- CN218781453U CN218781453U CN202222863017.2U CN202222863017U CN218781453U CN 218781453 U CN218781453 U CN 218781453U CN 202222863017 U CN202222863017 U CN 202222863017U CN 218781453 U CN218781453 U CN 218781453U
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The utility model discloses a cooling system and air conditioning unit, cooling system includes: the main loop is provided with a compressor, a condenser, a flash evaporator and an evaporator which are sequentially connected, one end of the cooling branch is connected to the condenser through a cooling throttle valve, the other end of the cooling branch is provided with a flash flow path and an evaporation flow path, the on-off state of the flash flow path and the on-off state of the evaporation flow path can be switched, the flash flow path is connected to the flash evaporator, the evaporation flow path is connected to the evaporator, and the evaporation flow path is provided with a refrigerant pump. The utility model discloses an add the refrigerant pump at the evaporation flow path, after the evaporation flow path was put through, the refrigerant passed through the pressure boost of refrigerant pump for the increase of end pressure difference around the cooling branch road, with this promotion cooling capacity, avoid cooling not enough.
Description
Technical Field
The utility model relates to a cooling system technical field especially relates to cooling system and air conditioning unit that condenser and refrigerant pump jointly supply liquid.
Background
For an air conditioning unit, a large amount of heat is generated by increasing the operation load of heat generating components such as a motor along with the accumulation of the operation time in use, so that an effective cooling scheme is required to ensure the reliability of the operation of the motor. At present, a conventional cooling scheme is to take a high-pressure liquid refrigerant from a condenser, cool the refrigerant by an electronic expansion valve and reduce the pressure of the refrigerant, then send the liquid refrigerant to a heating component by using the pressure difference between the condensing pressure of the refrigerant in the condenser and the refrigerant in an evaporator, and make the refrigerant evaporated by absorbing heat enter the evaporator, thereby achieving the purpose of cooling the heating component. However, due to the different operating conditions of the units, the pressure difference between the condenser and the evaporator varies greatly, and the change of the cooling liquid supply amount before and after the switching of the operating conditions is easily caused by the reduction of the pressure difference, so that the excessive or insufficient cooling liquid supply of the heating components is caused, and the normal operation of the heating components and the units is influenced.
The scheme that adaptability is poor around switching to the operating mode has appeared among the prior art, and it is through being connected to flash tank and evaporimeter respectively with the cooling branch road, relies on the cooling liquid supply volume that increases or reduces the cooling branch road that switches the flow path on-off state and the aperture of adjustment choke valve, avoids cooling surplus or cooling not enough. However, the throttle valve has a very limited capacity for adjusting the refrigerant flow rate, and cannot effectively ensure the refrigerant liquid supply amount, and the refrigerant liquid supply amount is still insufficient due to the reduction of the pressure difference during the operation of the unit.
Therefore, how to design a cooling system and an air conditioning unit for effectively improving cooling capacity is an urgent technical problem to be solved in the industry.
SUMMERY OF THE UTILITY MODEL
In order to solve the defect that current air conditioning unit pressure differential control range is limited, cooling output capacity is not enough, the utility model provides a cooling system and air conditioning unit through add the refrigerant pump at the evaporation flow path, after the evaporation flow path is put through, the refrigerant passes through the pressure boost of refrigerant pump for cooling branch road front and back end pressure differential increase to this promotes cooling capacity, avoids cooling not enough.
The utility model discloses a technical scheme be, design cooling system, include: the main loop is provided with a compressor, a condenser, a flash evaporator and an evaporator which are sequentially connected, one end of the cooling branch is connected to the condenser through a cooling throttle valve, the other end of the cooling branch is provided with a flash flow path and an evaporation flow path, the on-off state of the flash flow path and the on-off state of the evaporation flow path can be switched, the flash flow path is connected to the flash evaporator, the evaporation flow path is connected to the evaporator, and the evaporation flow path is provided with a refrigerant pump.
Further, the cooling system further includes: the first detection module is used for detecting the coolant supply amount of the cooling system.
In some embodiments, the first detection module employs a liquid level sensor mounted in the condenser or evaporator or a flow meter mounted on the cooling branch or main circuit.
Furthermore, the refrigerant pump and the first detection module are both connected to a controller of the cooling system; when the evaporation flow path is connected, the controller starts the refrigerant pump and controls the working state of the refrigerant pump according to the refrigerant liquid supply quantity.
Furthermore, the main loop is provided with a primary throttle valve and a secondary throttle valve, the primary throttle valve is connected between the condenser and the flash evaporator in series, and the secondary throttle valve is connected between the flash evaporator and the evaporator in series.
Further, the cooling system further includes: and the second detection module is used for detecting the temperature parameters of the main circuit and the cooling branch circuit.
In some embodiments, the second detecting module includes a plurality of temperature sensors for detecting an actual temperature of the heat generating component, a temperature of the refrigerant before and after flowing through the heat generating component, an evaporation temperature of the evaporator, and a temperature of the chilled water flowing out of the evaporator.
Furthermore, the first-stage throttle valve, the second-stage throttle valve and the second detection module are all connected to a controller of the cooling system, and the controller synchronously adjusts the opening degree of the first-stage throttle valve and the opening degree of the second-stage throttle valve according to temperature parameters.
The utility model also provides an air conditioning unit, this air conditioning unit adopts foretell cooling system.
In some embodiments, the air conditioning unit is a centrifugal chiller.
Compared with the prior art, the utility model discloses an add the refrigerant pump at the evaporation flow path, after the evaporation flow path was put through, the refrigerant process refrigerant pump's pressure boost for cooling branch road front and back end pressure differential increase guarantees the refrigerant liquid supply volume with this, effectively promotes the cooling capacity, avoids the cooling not enough.
Drawings
The invention is explained in more detail below with reference to exemplary embodiments and the accompanying drawings, in which:
fig. 1 is a schematic connection diagram of the cooling system of the present invention.
Detailed Description
In order to make the technical problem, technical solution and advantageous effects to be solved by the present invention more clearly understood, the following description is given in conjunction with the accompanying drawings and embodiments to illustrate the present invention in further detail. It should be understood that the specific embodiments described herein are merely illustrative of the present patent and are not limiting upon the present patent.
As shown in fig. 1, the cooling system of the present invention is suitable for use in air conditioning units, including but not limited to centrifugal chiller units. The cooling system mainly comprises a main circuit with a compressor 5, a condenser 1, a flash tank 8 and an evaporator 13 connected in series, and a cooling branch circuit for cooling heat generating components 6, one end of which is connected to the condenser 1 through a cooling throttle valve 3, and the other end of which is connected to the low pressure side of the cooling system. More specifically, a part of refrigerant flowing out of the condenser 1 is sent to the cooling branch, the other end of the cooling branch is provided with a flash flow path and an evaporation flow path in parallel, the flash flow path is connected to the flash unit 8, the flash unit 8 is connected to an air supplement port of the compressor 5 through the middle air supplement pipeline 2, a liquid outlet of the flash unit 8 is connected to the evaporator 13, the evaporation flow path is connected to the evaporator 13, the flash flow path is provided with the flash control valve 7, the evaporation flow path is provided with the evaporation control valve 9, the on-off state of the flow path where the flash unit is located can be flexibly switched through the flash control valve 7 and the evaporation control valve 9, and the refrigerant flowing out of the cooling branch can be sent to the flash unit 8 through the flash flow path or sent to the evaporator 13 through the evaporation flow path.
The heat generating components include, but are not limited to, an electric motor, for example, a cooling system is designed according to the following principle: according to the fluid mechanics principle and related research experience, the mass flow of the fluid flowing through a throttle valve is calculated according to the following formula:
wherein, C D For the flow coefficient, A is the flow area of the throttle valve, and they are all only related to the geometric structure of the throttle valve; delta p is the pressure difference between the front and the rear of the throttle valve; ρ is a unit of a gradient 1 Is the pre-throttle fluid density.
According to the flow formula, neglecting the flow loss of the refrigerant in the motor or the evaporator, and under the condition of throttle valve selection determination (geometric structure determination), C D And A is a definite value, Δ p is the condensation pressure p c With evaporation pressure p e (cooling branch to evaporator) or condensing pressure p c And flash pressure p s Difference between (cooling branch connected to flash vessel), p 1 The density of the refrigerant liquid at the front end of the cooling branch, namely the outlet of the condenser; the outlet conditions of the condenser 1 are the same for the same design conditions, i.e. p 1 The same is true. Therefore, under the same other conditions, the pressure difference Δ p between the cooling branch and the evaporator 13 is larger than that between the cooling branch and the flash tank 8, and the refrigerant flow rate of the cooling branch is larger.
Under some operating modes that condensation and evaporation pressure difference are large, the refrigeration cycle efficiency is poor, in order to guarantee the large output capacity of the unit, the power of the motor is large, and therefore the heat productivity of the motor is larger than that of the conventional operating mode. In order to ensure the cooling reliability, a throttle valve is designed by the maximum heating value of a cooling system, if a cooling pipeline is singly connected to an evaporator 13 or a flash evaporator 8, the adjusting range of the throttle valve is only limited in the operating range under the large-load working condition, the small-load operating range under the refrigeration working condition deviates from the large-load working condition, the heating value of a motor is much smaller, and the cooling capacity of the cooling system is excessive to cause the cooling capacity loss of the system; if design the choke valve according to, then can't satisfy required cooling capacity under the heavy load operating mode, the motor can be overheated, influences life.
Based on the above analysis, the flash flow path and the evaporation flow path are designed at the outlet of the cooling branch, and the on-off state of the flash flow path and the evaporation flow path is switched according to the heat generation amount of the heat generating component, so as to adjust the amount of the refrigerant liquid supply to adapt to the heat generation condition of the heat generating component. The utility model discloses on the basis of flash flow path and evaporation flow path, install the refrigerant pump at the evaporation flow path, when the component temperature that generates heat is higher, the evaporation flow path is put through, and refrigerant pump 10 opens work, and the refrigerant flows out back from condenser 1 through the pressure boost of refrigerant pump 10 for the exit differential pressure increase of cooling branch road, with this assurance refrigerant liquid supply volume, effectively promotes the cooling capacity, avoids the cooling not enough.
As shown in fig. 1, in some embodiments, the cooling system further comprises: the liquid level sensor 11 is used for detecting the actual liquid level of the condenser 1, and the actual liquid level accurately reflects the amount of the refrigerant liquid supply of the cooling system. In order to realize the automatic control of the refrigerant pump, the refrigerant pump 10 and the liquid level sensor 11 are both connected to a controller of the cooling system, when the evaporation flow path is connected, the controller starts the refrigerant pump 10 and controls the working state of the refrigerant pump 10 according to the actual liquid level, namely when the actual liquid level is lower, the opening degree of the refrigerant pump 10 is increased, and the refrigerant liquid supply amount is increased.
It should be understood that the refrigerant supply amount of the cooling system is detected by the first detection module, the liquid level sensor is only a possible implementation of the first detection module, and the first detection module may also adopt a flow meter, and the flow meter detects the refrigerant flow rate of the cooling branch to reflect the refrigerant supply amount of the cooling system. Because the refrigerant can flow at major loop and cooling branch road inner loop, among the practical application, level sensor also can detect the liquid level of evaporimeter and reflect cooling system's refrigerant supplies the liquid measure size, and the refrigerant flow that the flowmeter detected the major loop also can reflect cooling system's refrigerant supplies the liquid measure size equally, the utility model discloses do not do special restriction to specific sensor type and the mounted position of a detection module, can realize that reflecting cooling system's refrigerant supplies the liquid measure size can.
In some embodiments, the main circuit is provided with a primary throttle 4 and a secondary throttle 12, the primary throttle 4 being connected in series between the condenser 1 and the flash tank 8, the secondary throttle 12 being connected in series between the flash tank 8 and the evaporator 13, the cooling flow being regulated by the primary throttle 4 and the secondary throttle 12. In order to realize the automatic control of the first-stage throttle valve 4 and the second-stage throttle valve 12, the first-stage throttle valve 4 and the second-stage throttle valve 12 are both connected to a controller of the cooling system, the cooling system is further provided with a second detection module, the second detection module is used for detecting temperature parameters of a main loop and a cooling branch, and the controller synchronously adjusts the opening degrees of the first-stage throttle valve 4 and the second-stage throttle valve 12 according to the temperature parameters.
More specifically, the second detection module includes a plurality of temperature sensors, which are respectively used to detect the actual temperature of the heat generating component, the temperatures of the refrigerant before and after flowing through the heat generating component, the evaporation temperature of the evaporator, and the temperature of the chilled water flowing out of the evaporator, the second detection module collects the temperature of the refrigerant before the cooling branch passes through the heat generating component and the temperature of the refrigerant after passing through the heat generating component, the controller obtains the superheat degree of the actual temperature of the heat generating component from the temperature difference between the temperatures of the refrigerant before and after passing through the heat generating component 6, and a part of the adjustment amount of the primary throttle valve 4 is calculated by using the superheat degree of the actual temperature of the heat generating component. The second detection module also collects the evaporating temperature of the evaporator 13 and the outlet water temperature of the chilled water flowing out of the evaporator 13, the controller obtains the actual evaporator end temperature difference by taking the temperature difference between the outlet water temperature of the chilled water and the evaporating temperature, the other part of regulating quantity of the primary throttle valve 4 is calculated by utilizing the actual evaporator end temperature difference, the two parts of regulating quantity are superposed to obtain the opening regulating quantity of the primary throttle valve 4, the opening of the secondary throttle valve 12 is synchronously regulated along with the primary throttle valve 4, the output capacity of the cooling system can be reasonably matched with the heating quantity of the heating component 6 and the load demand of the terminal equipment by regulating the openings of the primary throttle valve 4 and the secondary throttle valve 12, the running stability of the unit is improved, and insufficient or waste of cooling capacity is avoided.
Specifically, the controller executes the following control method:
detecting the actual temperature of the heat generating component 6;
switching the on-off state of the flash flow path and the evaporation flow path according to the actual temperature, switching on the flash flow path and switching off the evaporation flow path when the actual temperature is lower than a set lower limit threshold, and switching off the flash flow path and switching on the evaporation flow path when the actual temperature is higher than a set upper limit threshold;
after the evaporation flow path is connected, the operating state of the refrigerant pump 10 is controlled according to the refrigerant supply amount of the cooling system.
Specifically, the working state adjusting process of the refrigerant pump 10 is as follows: work is setting for initial aperture when refrigerant pump 10 starts, when the refrigerant supplies the liquid measure to reach when setting for more than the liquid measure, explains cooling system's refrigerant supplies the liquid measure sufficient, and the controller maintains refrigerant pump 10's current aperture, supplies the liquid measure to be less than when setting for when supplying the liquid measure when the refrigerant, explains cooling system's refrigerant supplies the liquid measure not enough, and the controller increases refrigerant pump 10's aperture to the exit differential pressure of increase cooling branch promotes the refrigerant and supplies the liquid measure.
For realizing the accurate control of refrigerant pump aperture, in some embodiments, the refrigerant liquid supply volume is the actual liquid level of condenser, sets for the liquid supply volume and for the settlement liquid level of condenser, and utility model people obtains the settlement function model that is fit for centrifugal cooling water set through a large amount of experimental statistics analysis, and the aperture after the refrigerant pump increases is calculated through the settlement function model and is obtained, and the settlement function model is: opening degree = (actual liquid level × 0.3 × rated flow rate)/100, and the rated flow rate is a rated flow rate of the refrigerant pump.
In some embodiments, the control method further comprises:
when the actual temperature is within the target temperature range, the temperature of the heating component is within a proper range, the cold quantity of the cooling system is supplied properly, and the opening degree of the first-stage throttle valve and the opening degree of the second-stage throttle valve are kept unchanged;
when the actual temperature is outside the target temperature range, the temperature of the heating part is over-high or over-low, the cold quantity supply of the cooling system is insufficient or over-high, the temperature parameters of the main loop and the cooling branch are detected, and the opening degree of the primary throttle valve and the opening degree of the secondary throttle valve are synchronously adjusted according to the temperature parameters.
Note that the upper threshold and the lower threshold are designed according to the heat resistance of the heat generating component, and in the case of a motor, the upper threshold may be designed to be 58 ℃ and the lower threshold may be designed to be 32 ℃. The target temperature interval is a target temperature +/-margin, the margin can be designed to be 4 ℃ and the like, and the target temperature interval is between a set upper limit threshold and a set lower limit threshold. The set liquid level is the liquid level of the unit in the optimal running state as a design standard, and the optimal liquid level of 1/2 or other proportion is taken as the set liquid level according to the actual use requirement.
In some embodiments, the opening of the first-stage throttle valve and the opening of the second-stage throttle valve are adjusted as follows:
D＝D1+D2，D C ＝U×D；
when |. Tshdt | ≦ the set deviation, it indicates that the temperature of the heat generating component is effectively controlled, D1=0;
when | < Tshdt > is set as a deviation, indicating that the cooling capacity supply deviation of the cooling branch is large, the throttle valve needs to be adjusted to adapt to the heat generation amount of the heat generating component 6, D1= a _ EXV1 × Kp _ EXV1 × < Tshdt + a _ EXV1 × Ki _ EXV1 × (-Tshdt- Δ Tshdt'), < Δ Tshdt = Tshdt-Tshdt;
when Tdwc is more than or equal to A _ EXV1 × dwc _ EXV1, which indicates that the cold supply deviation of the evaporator is large, the throttle valve needs to be adjusted to adapt to the load demand of the end equipment, D2= A _ EXV1 × Kp1_ EXV1 × DeltaTwct, deltaTwct = Tdwc-A _ EXV1 × dwc _ EXV1;
when Tdwc < a _ EXV1 × dwc _ EXV1, indicating that the refrigeration capacity supply of the evaporator is appropriate, D2=0;
wherein D is the opening regulating quantity of the first-stage throttle valve, and D C The opening adjustment quantity of the two-stage throttle valve is U which is a proportionality coefficient, tshd is the actual temperature superheat degree of a heating part, tshdt is the target temperature superheat degree of the heating part, a calculation formula of the target temperature superheat degree of the humidity of the heating part can be obtained by fitting experimental data, or the target temperature superheat degree of the heating part is designed to be a fixed value to simplify control logic, and delta Tshdt is the superheat degree deviation of the heating part in the current periodThe difference Δ Tshdt' is the superheat deviation of the heat generating component in the previous cycle, a _ EXV1 is a correction coefficient, kp _ EXV1 and Kp1_ EXV1 are proportional coefficients, ki _ EXV1 is an integral coefficient, tdwc is the actual evaporator end temperature difference, dwc _ EXV1 is the target evaporator end temperature difference, and Δ Tdwct is the evaporator end temperature difference deviation. In some embodiments, the set deviation is 0.1 ℃, and the specific values of the set deviation and the coefficients such as a _ EXV1 can be designed according to specific requirements in practical applications.
It should be understood that the opening, holding, or closing of the primary and secondary throttle valves is determined by the positive or negative of D1+ D2, with D1+ D2>0 the primary throttle valve being open and the secondary throttle valve subsequently being open, D1+ D2<0 the primary throttle valve being closed and the secondary throttle valve subsequently being closed, and D1+ D2=0 the primary and secondary throttle valves being held at current opening. During the adjustment of the first-stage throttle valve 4 and the second-stage throttle valve 12, the throttle minimum-opening operation is maintained when the throttle valve is already at the minimum opening and D1+ D2<0, and the throttle maximum-opening operation is maintained when the throttle valve is already at the maximum opening and D1+ D2> 0.
It is noted that the terminology used above is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise. The "throttle valve" appearing above may be an electronic expansion valve, and the "control valve" may be a solenoid valve.
The relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present application unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not intended to limit the present invention, and any modifications, equivalents, improvements, etc. made within the spirit and principles of the present invention should be included within the scope of the present invention.
Claims (10)
1. A cooling system, comprising: the main circuit is provided with a compressor, a condenser, a flash evaporator and an evaporator which are sequentially connected, one end of the cooling branch is connected to the condenser through a cooling throttle valve, the other end of the cooling branch is provided with a flash flow path and an evaporation flow path, the on-off state of the flash flow path and the on-off state of the evaporation flow path can be switched, the flash flow path is connected to the flash evaporator, and the evaporation flow path is connected to the evaporator; the evaporator is characterized in that the evaporation flow path is provided with a refrigerant pump.
2. The cooling system of claim 1, further comprising: further comprising: and the first detection module is used for detecting the refrigerant liquid supply amount of the cooling system.
3. The cooling system according to claim 2, wherein the first detection module employs a liquid level sensor installed in the condenser or the evaporator or a flow meter installed on the cooling branch or the main circuit.
4. The cooling system of claim 2, wherein the refrigerant pump and the first detection module are both connected to a controller of the cooling system; when the evaporation flow path is communicated, the controller starts the refrigerant pump and controls the working state of the refrigerant pump according to the refrigerant liquid supply amount.
5. The cooling system of claim 1, wherein the primary circuit is provided with a primary throttle valve and a secondary throttle valve, the primary throttle valve being in series between the condenser and the flash tank, the secondary throttle valve being in series between the flash tank and the evaporator.
6. The cooling system of claim 5, further comprising: a second detection module for detecting temperature parameters of the main loop and the cooling branch.
7. The cooling system of claim 6, wherein the second detecting module comprises a plurality of temperature sensors for detecting an actual temperature of the heat generating component, a temperature of the refrigerant before and after flowing through the heat generating component, an evaporation temperature of the evaporator, and a temperature of the outlet water of the chilled water flowing out from the evaporator.
8. The cooling system of claim 6, wherein the primary throttle valve, the secondary throttle valve, and the second detection module are each connected to a controller of the cooling system, the controller synchronously adjusting the opening of the primary throttle valve and the secondary throttle valve based on the temperature parameter.
9. Air conditioning assembly, characterized in that it employs a cooling system according to any one of claims 1 to 8.
10. The air conditioning assembly of claim 9, wherein the air conditioning assembly is a centrifugal chiller.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117345591A (en) * | 2023-12-05 | 2024-01-05 | 珠海格力电器股份有限公司 | Cooling system and cooling control method of suspension type compressor |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117345591A (en) * | 2023-12-05 | 2024-01-05 | 珠海格力电器股份有限公司 | Cooling system and cooling control method of suspension type compressor |
| CN117345591B (en) * | 2023-12-05 | 2024-03-19 | 珠海格力电器股份有限公司 | Cooling system and cooling control method of suspension type compressor |
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