Abnormal start control method of refrigerating system, controller and refrigerating system

Abstract

The invention discloses an abnormal starting control method of a refrigerating system, a controller and the refrigerating system, and relates to the field of compressor control, and the abnormal starting control method comprises the steps that under the condition that condenser side temperature and evaporator side temperature represent that the refrigerating system is in an abnormal starting state, an evaporator electromagnetic expansion valve is controlled to be opened to the opening degree matched with the abnormal starting state, and controlling the balance valve to be switched on, and controlling the magnetic suspension type compressor to operate at the starting load value matched with the abnormal starting state. According to the control method, the balance valve is controlled to be conducted in the abnormal state, the electromagnetic expansion valve of the evaporator is opened to the opening degree matched with the abnormal starting state, the inflow amount of the refrigerant entering the evaporator is changed, and the magnetic suspension type compressor is configured to operate at the starting load value at which surge does not occur in the abnormal starting state; the purpose of the present invention is to increase the intake pressure, suppress the speed-saving rate of exhaust pressure, and increase the build-up pressure ratio. Therefore, the starting reliability of the magnetic suspension type compressor is improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressor control, and particularly relates to an abnormal start control method of a refrigeration system, a controller and the refrigeration system. BACKGROUND

[0002] The compressor pressure ratio refers to the ratio of the discharge pressure to the suction pressure of the compressor in the refrigeration system. For the refrigeration system equipped with the magnetic suspension compressor, only when the discharge pressure is greater than the suction pressure and the compressor pressure ratio is within the normal start pressure ratio interval, the magnetic suspension compressor can build a refrigerant circulation for refrigeration, so as to realize the refrigeration function.

[0003] However, since the discharge pressure and the suction pressure are easily affected by the external temperature to cause the compressor pressure ratio to be abnormal, the magnetic suspension compressor is increased in start duration or even fails to start, and the start reliability of the magnetic suspension compressor is reduced. SUMMARY

[0004] In view of the above problems, the present application provides an abnormal start control method of a refrigeration system, a controller and the refrigeration system, to realize the purpose of improving the start reliability of the magnetic suspension compressor. The specific scheme is as follows:

[0005] The first aspect of the present application provides an abnormal start control method of a refrigeration system, applied to the refrigeration system, the refrigeration system comprising a magnetic suspension compressor, an evaporator electromagnetic expansion valve and a balance valve, and the abnormal start control method of the refrigeration system comprising:

[0006] obtaining a condenser side temperature and an evaporator side temperature of the refrigeration system;

[0007] in a case where the condenser side temperature and the evaporator side temperature represent that the refrigeration system is in an abnormal start state, controlling the evaporator electromagnetic expansion valve to open to an opening degree adapted to the abnormal start state, controlling the balance valve to be turned on, and controlling the magnetic suspension compressor to operate at a start load value adapted to the abnormal start state, wherein the opening degree adapted to the abnormal start state is different from that of the evaporator electromagnetic expansion valve in a normal start state, and the start load value adapted to the abnormal start state is a start load value at which the magnetic suspension compressor does not occur in the abnormal start state.

[0008] In a possible implementation, the abnormal start state comprises a first abnormal start state, a second abnormal start state and a third abnormal start state, and the controlling the evaporator electromagnetic expansion valve to open to the opening degree adapted to the abnormal start state, and the controlling the magnetic suspension compressor to operate at the start load value adapted to the abnormal start state, comprises:

[0009] In the first abnormal start state, the evaporator electromagnetic expansion valve is controlled to open to a first opening degree adapted to the first abnormal start state, and the magnetic levitation compressor is controlled to run at a first start load value adapted to the first abnormal start state, in which the evaporator side temperature is greater than the condenser side temperature;

[0010] In the second abnormal start state, the evaporator electromagnetic expansion valve is controlled to open to a second opening degree adapted to the second abnormal start state, and the magnetic levitation compressor is controlled to run at a second start load value adapted to the second abnormal start state, in which the evaporator side temperature is less than the condenser side temperature;

[0011] In the third abnormal start state, the evaporator electromagnetic expansion valve is controlled to open to a third opening degree adapted to the third abnormal start state, and the magnetic levitation compressor is controlled to run at a third start load value adapted to the third abnormal start state, in which the evaporator side temperature and the condenser side temperature are both greater than a preset temperature threshold, wherein the first opening degree is greater than the third opening degree, the third opening degree is greater than the second opening degree, the second start load value is greater than the third start load value, and the third start load value is greater than the first start load value.

[0012] In a possible implementation, the control of the balance valve to be turned on includes:

[0013] In the first abnormal start state, the balance valve is controlled to open to a fourth opening degree adapted to the first abnormal start state;

[0014] In the second abnormal start state, the balance valve is controlled to open to a fifth opening degree adapted to the second abnormal start state;

[0015] In the third abnormal start state, the balance valve is controlled to open to a sixth opening degree adapted to the third abnormal start state, wherein the fourth opening degree is greater than the fifth opening degree, and the fifth opening degree is greater than the sixth opening degree.

[0016] In a possible implementation, the refrigeration system further includes a variable frequency fan for cooling a condenser of the refrigeration system.

[0017] The abnormal start control method of the refrigeration system further includes:

[0018] In the first abnormal start state and the third abnormal start state, the variable frequency fan is controlled to run at a speed gear adapted to an ambient temperature.

[0019] In the second abnormal start state, the variable frequency fan is controlled to run at an initial speed gear, and a wind speed of the initial speed gear is greater than a wind speed of the speed gear adapted to the ambient temperature.

[0020] In a possible implementation, the refrigeration system further includes a variable frequency water pump configured to adjust a flow rate of cooling water flowing through an evaporator of the refrigeration system.

[0021] The abnormal start control method of the refrigeration system further includes:

[0022] In the first abnormal start state and the third abnormal start state, the variable frequency water pump is controlled to run at an abnormal state power, and the abnormal state power is less than a running power of the variable frequency water pump in the normal start state.

[0023] In a possible implementation, the refrigeration system further includes a backup refrigerant pump configured to deliver refrigerant to the magnetic suspension compressor.

[0024] The abnormal start control method of the refrigeration system further includes:

[0025] When the actual speed of the magnetic suspension compressor is greater than a start speed threshold, the temperature of the magnetic suspension compressor is greater than an alarm temperature threshold, the liquid level height of the liquid accumulator is not less than a preset height threshold, and the downtime of the backup refrigerant pump is greater than the shortest downtime of the main refrigerant pump of the refrigeration system, the backup refrigerant pump is controlled to start running.

[0026] When the magnetic suspension compressor stops running, the backup refrigerant pump is controlled to stop running; or, when the temperature of the magnetic suspension compressor is not greater than the alarm temperature threshold and the running time of the backup refrigerant pump exceeds a minimum running time, the backup refrigerant pump is controlled to stop running; or, when the temperature of the magnetic suspension compressor is greater than the alarm temperature threshold and the running time of the backup refrigerant pump exceeds a maximum running time, the backup refrigerant pump is controlled to stop running.

[0027] The second aspect of the present application provides a controller, including at least one processor and a memory connected with the processor, wherein:

[0028] The memory is configured to store a computer program.

[0029] The processor is configured to execute the computer program, so that the controller can implement the abnormal start control method of the refrigeration system provided in the first aspect of the present application and any possible implementation of the first aspect.

[0030] The third aspect of the present application provides a refrigeration system, including:

[0031] The magnetic suspension compressor, the evaporator electromagnetic expansion valve, the balance valve, the refrigerant bypass pipeline and the controller provided by the second aspect of the application, the refrigerant outlet of the magnetic suspension compressor is communicated with the refrigerant inlet of the condenser of the refrigeration system through a first refrigerant transmission pipeline, the refrigerant outlet of the condenser is communicated with the first refrigerant inlet of the evaporator of the refrigeration system through a second refrigerant transmission pipeline, the refrigerant outlet of the evaporator is communicated with the refrigerant inlet of the magnetic suspension compressor, one end of the refrigerant bypass pipeline bypasses the first refrigerant transmission pipeline, and the other end of the refrigerant bypass pipeline is communicated with the second refrigerant inlet of the evaporator;

[0032] The evaporator electromagnetic expansion valve is arranged in the second refrigerant transmission pipeline and is used for controlling the refrigerant flow flowing into the evaporator;

[0033] The balance valve is arranged in the refrigerant bypass pipeline and is used for controlling the refrigerant flow flowing into the evaporator from the first refrigerant transmission pipeline;

[0034] The controller is electrically connected with the magnetic suspension compressor, the evaporator electromagnetic expansion valve and the balance valve respectively, and is used for, in the case that the condenser side temperature and the evaporator side temperature indicate that the refrigeration system is in an abnormal starting state, controlling the evaporator electromagnetic expansion valve to open to an opening degree adapted to the abnormal starting state, controlling the balance valve to be turned on, and controlling the magnetic suspension compressor to operate at a starting load value adapted to the abnormal starting state, wherein the opening degree adapted to the abnormal starting state is different from an opening degree of the evaporator electromagnetic expansion valve in a normal starting state, and the starting load value adapted to the abnormal starting state is a starting load value at which the magnetic suspension compressor does not generate surge in the abnormal starting state.

[0035] In a possible implementation, when the controller controls the evaporator electromagnetic expansion valve to open to an opening degree adapted to the abnormal starting state and controls the magnetic suspension compressor to operate at a starting load value adapted to the abnormal starting state, the controller is configured to:

[0036] In the first abnormal starting state, the evaporator electromagnetic expansion valve is controlled to open to a first opening degree adapted to the first abnormal starting state, and the magnetic suspension compressor is controlled to operate at a first starting load value adapted to the first abnormal starting state, wherein the abnormal starting state includes the first abnormal starting state, a second abnormal starting state and a third abnormal starting state, and in the first abnormal starting state, the evaporator side temperature is greater than the condenser side temperature.

[0037] in the second abnormal start state, the evaporator electromagnetic expansion valve is controlled to open to a second opening degree adapted to the second abnormal start state, the magnetic levitation compressor is controlled to operate at a second start load value adapted to the second abnormal start state, and in the second abnormal start state, the evaporator side temperature is less than the condenser side temperature;

[0038] in the third abnormal start state, the evaporator electromagnetic expansion valve is controlled to open to a third opening degree adapted to the third abnormal start state, the magnetic levitation compressor is controlled to operate at a third start load value adapted to the third abnormal start state, and in the third abnormal start state, both the evaporator side temperature and the condenser side temperature are greater than a preset temperature threshold, wherein the first opening degree is greater than the third opening degree, the third opening degree is greater than the second opening degree, the second start load value is greater than the third start load value, and the third start load value is greater than the first start load value.

[0039] In a possible implementation, the refrigeration system further comprises:

[0040] a variable frequency fan for cooling a condenser of the refrigeration system;

[0041] the controller is electrically connected with the variable frequency fan, and is configured to control the variable frequency fan to operate at a speed gear adapted to an ambient temperature in the first abnormal start state and the third abnormal start state, and control the variable frequency fan to operate at an initial speed gear in the second abnormal start state, wherein a wind speed of the initial speed gear is greater than a wind speed of the speed gear adapted to the ambient temperature.

[0042] By the technical scheme, the application provides an abnormal start control method, a controller and a refrigeration system, which collects the condenser side temperature and the evaporator side temperature, uses the condenser side temperature to represent the exhaust pressure, and uses the evaporator side temperature to represent the suction pressure, so as to accurately extract the parameters for determining whether the refrigeration system is in an abnormal start state. Then, the evaporator electromagnetic expansion valve is controlled to open to an opening degree suitable for the abnormal start state, and the opening degree suitable for the abnormal start state is different from the opening degree of the evaporator electromagnetic expansion valve in the normal start state, so that the refrigerant flow into the evaporator is changed in the abnormal start state, and the suction pressure and the exhaust pressure are adjusted by adjusting the refrigerant flow into the evaporator, and then the normal pressure ratio is constructed, and the start reliability of the magnetic suspension compressor is improved. At the same time, the balance valve is controlled to be turned on when the refrigeration system is in the abnormal start state, and part of the high-pressure refrigerant output by the magnetic suspension compressor is introduced into the evaporator, so that the refrigerant flow into the evaporator is increased while the exhaust pressure is reduced, the exhaust pressure and the suction pressure are changed, and compared with the way of constructing the pressure ratio independently by the compressor, the construction rate of the normal pressure ratio is improved. Moreover, the start load value suitable for the abnormal start state is configured, which is the start load value of the magnetic suspension compressor without surge in the abnormal start state, and the magnetic suspension compressor is controlled to operate at the start load value suitable for the abnormal start state, so as to suppress the operating power of the magnetic suspension compressor and avoid the occurrence of surge phenomenon, and the construction rate of the pressure ratio is improved. It can be seen that the start reliability of the refrigeration system provided with the magnetic suspension compressor is improved. BRIEF DESCRIPTION OF DRAWINGS

[0043] The above and other features, advantages, and aspects of the present disclosure will become more apparent by describing in detail the following specific embodiments with reference to the attached drawings. Throughout the drawings, the same or similar reference numerals refer to the same or similar elements. It should be understood that the drawings are schematic, and the sizes and elements are not necessarily drawn to scale.

[0044] Figure 1 A flowchart of an abnormal start control method of a refrigeration system provided by the application;

[0045] Figure 2 A refrigeration system start state schematic diagram provided by the application;

[0046] Figure 3 A structural schematic diagram of a controller provided by the application;

[0047] Figure 4 A structural schematic diagram of a refrigeration system provided by the application;

[0048] Figure 5 A structural schematic diagram of a refrigeration system provided by a possible implementation of the application. DETAILED DESCRIPTION

[0049] The embodiments of the present application will be described below in conjunction with the accompanying drawings. The terms used in the embodiments of the present application are only used to explain the specific embodiments of the present application, and are not intended to limit the present application.

[0050] The embodiments of the present application will be described below in conjunction with the accompanying drawings. The terms used in the embodiments of the present application are only used to explain the specific embodiments of the present application, and are not intended to limit the present application.

[0051] The terms "first", "second", and the like in the description of the specification and claims of the present application and the above-described drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged, and this is only a distinguishing way used in the description of the embodiments of the present application to describe the objects with the same attribute. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion, so that the processes, methods, systems, products or equipment containing a series of units are not necessarily limited to those units, but can include other units not clearly listed or inherent to these processes, methods, products or equipment.

[0052] It should be noted that, in actual application scenarios, compared with the prior art, the application improves the starting reliability, specifically: in order to avoid the risk of compressor liquid strike and realize rapid starting, the existing refrigeration system will open the electromagnetic expansion valve to a small opening degree until the starting is completed, and the compressor is configured to run at a high power. In the case where the temperature on the evaporator side is higher than the temperature on the condenser side, the suction pressure will be greater than the exhaust pressure. At this time, the suction pressure will hinder the flow of liquid refrigerant from the condenser into the evaporator, and the decrease in the amount of liquid refrigerant flowing into the evaporator will result in a decrease in the amount of gaseous refrigerant sucked by the compressor, thereby further causing the exhaust pressure to decrease. However, the electromagnetic expansion valve of the existing refrigeration system only maintains the fixed opening degree of the normal starting state during the starting stage, which causes the refrigerant flow into the evaporator under the normal starting state to be unable to meet the demand of pressure ratio construction, so that the compressor cannot construct the pressure ratio required for normal starting. In the case where the temperature on the condenser side is too high or the temperature on both sides is too high (the temperature on the condenser side and the temperature on the evaporator side both exceed the rated operating temperature), the exhaust pressure will increase or the exhaust and suction pressures will increase simultaneously, thereby causing the pressure ratio to be greater than the upper limit of the normal starting pressure ratio. In order to construct the pressure ratio required for normal starting, the magnetic suspension compressor will increase the operating power. However, for the magnetic suspension compressor, due to the slow acceleration of the centrifugal compressor, the high operating power during the starting stage will cause the magnetic suspension compressor to have a risk of surge, and will cause the suction pressure to be insufficient, thereby failing to construct the pressure ratio required for normal starting. As can be seen, in the case of the above-mentioned abnormal starting state, the pressure ratio cannot meet the demand of normal starting of the compressor, thereby causing the magnetic suspension compressor to need to increase the operating power. In the case where the pressure ratio cannot be constructed, long-time high-power operation will increase the risk of failure of the magnetic suspension compressor due to long-time high-power operation, thereby reducing the starting reliability of the compressor. However, in the case where the temperature on the condenser side and the temperature on the evaporator side represent that the refrigeration system is in an abnormal starting state, the application controls the balance valve to be turned on, thereby guiding part of the refrigerant flowing into the condenser into the evaporator, and increasing the refrigerant inflow amount of the evaporator. At the same time, the evaporator electromagnetic expansion valve is configured to be opened to an opening degree adapted to the abnormal starting state, and the opening degree adapted to the abnormal starting state is different from the opening degree of the evaporator electromagnetic expansion valve under the normal starting state, thereby changing the refrigerant inflow amount into the evaporator under the abnormal starting state, to assist in adjusting the exhaust pressure and the suction pressure, and accelerating the construction of the pressure ratio. Finally, the magnetic suspension compressor is configured to run at a starting load value adapted to the abnormal starting state. Since the starting load value adapted to the abnormal starting state is the starting load value of the magnetic suspension compressor under the abnormal starting state without surge, the starting load value adapted to the abnormal starting state can increase the suction pressure while suppressing the increase rate of the exhaust pressure, thereby accelerating the construction of the pressure ratio. As can be seen, the application improves the starting reliability of the magnetic suspension compressor.

[0053] The first aspect of the application provides an abnormal start control method of a refrigeration system, applied to the refrigeration system, the refrigeration system comprising: a magnetic suspension compressor, an evaporator electromagnetic expansion valve and a balance valve, as shown in Figure 1 The abnormal start control method of the refrigeration system comprises:

[0054] S101, obtaining a condenser side temperature and an evaporator side temperature of the refrigeration system.

[0055] It should be noted that in actual application scenarios, the condenser side temperature can also be a parameter collected by a temperature sensor deployed on the condenser, and the evaporator side temperature can be a parameter collected by a temperature sensor deployed on the evaporator. According to the equation of ideal gas, when the volume and the amount of substance of the refrigerant are relatively stable, the pressure and the temperature are positively correlated, so the condenser side temperature can represent the exhaust pressure of the magnetic suspension compressor, and the evaporator side temperature can represent the suction pressure of the magnetic suspension compressor.

[0056] It should be noted that in actual application scenarios, the refrigeration system will generate vibration during startup and running, and the refrigerant will impact the equipment in the pipeline during the startup phase, thereby affecting the data collection accuracy of the pressure sensor and further affecting the subsequent judgment of whether the startup state is abnormal. Therefore, the application collects the condenser side temperature and the evaporator side temperature, uses the condenser side temperature to represent the exhaust pressure, and uses the evaporator side temperature to represent the suction pressure, thereby realizing accurate extraction of parameters for determining whether the refrigeration system is in an abnormal startup state.

[0057] S102, in the case that the condenser side temperature and the evaporator side temperature represent that the refrigeration system is in an abnormal startup state, controlling the evaporator electromagnetic expansion valve to open to an opening degree adapted to the abnormal startup state, controlling the balance valve to be turned on, and controlling the magnetic suspension compressor to run at a startup load value adapted to the abnormal startup state, wherein the opening degree adapted to the abnormal startup state is different from the opening degree of the evaporator electromagnetic expansion valve in the normal startup state, and the startup load value adapted to the abnormal startup state is a startup load value at which the magnetic suspension compressor does not occur in the abnormal startup state.

[0058] It should be noted that in actual application scenarios, the abnormal startup state can be a state that cannot build a normal startup pressure ratio within a preset startup time after a calibration test of the refrigeration system.

[0059] It should be noted that in the actual application scenario, the above-mentioned evaporator electromagnetic expansion valve is an electronic expansion valve located at the refrigerant inlet of the evaporator of the refrigeration system, which is used to adjust the refrigerant flow entering the evaporator. For the existing refrigeration system, in the normal starting state, only the electromagnetic expansion valve needs to be maintained at a small opening to ensure that the refrigerant flow entering the evaporator meets the starting requirements of the magnetic suspension compressor, thereby building a normal pressure ratio. However, in the case where the evaporator side temperature is higher than the condenser side temperature, the suction pressure will be greater than the discharge pressure. At this time, the suction pressure will hinder the inflow of liquid refrigerant from the condenser to the evaporator, and the decrease of the amount of liquid refrigerant flowing into the evaporator will lead to a decrease in the amount of gaseous refrigerant sucked by the compressor, thereby further reducing the discharge pressure. The existing refrigeration system electromagnetic expansion valve maintains a small opening during the starting stage, which will further exacerbate the decrease of the discharge pressure, so that the compressor cannot build the pressure ratio required for normal startup. In the case where the condenser side temperature is too high or the double side temperature is too high (the condenser side temperature and the evaporator side temperature both exceed the rated operating temperature), the discharge pressure or the discharge and suction pressure will rise. At this time, if the opening of the electromagnetic expansion valve is still maintained at a small opening as in the normal starting state, the suction pressure will be further reduced and the discharge pressure will be increased, which will cause the magnetic suspension compressor to fail to build a normal pressure ratio. Therefore, the present application configures the opening of the evaporator electromagnetic expansion valve to an opening suitable for the abnormal starting state, and the opening suitable for the abnormal starting state is different from the opening of the evaporator electromagnetic expansion valve in the normal starting state, so as to change the refrigerant flow entering the evaporator in the abnormal starting state, and adjust the suction pressure and the discharge pressure by adjusting the refrigerant flow entering the evaporator, thereby building a normal pressure ratio and improving the starting reliability of the magnetic suspension compressor.

[0060] It should be noted that in the actual application scenario, the above-mentioned balance valve is a valve for directly introducing part of the refrigerant output by the magnetic suspension compressor into the evaporator to balance the pressure of the condenser and the evaporator. In the case of an abnormal start state of the refrigeration system, the balance valve is controlled to be turned on, and part of the high-pressure refrigerant output by the magnetic suspension compressor is introduced into the evaporator, thereby increasing the refrigerant flow into the evaporator while reducing the exhaust pressure, changing the exhaust pressure and suction pressure, and improving the construction rate of the normal pressure ratio compared to the way of relying only on the compressor to independently build the pressure ratio. It should be noted that in the actual application scenario, the magnetic suspension compressor is a compressor that uses an energized magnetic field to control the rotor to suspend and rotate. In the initial stage of starting, the magnetic suspension compressor needs to be energized to generate a magnetic field to suspend the rotor, which requires a certain amount of energy, and at the same time, the motor of the compressor starts to operate, overcoming the inertia of the rotor and the initial resistance in the system, resulting in a lower operating power of the magnetic suspension compressor in the initial stage of starting. Due to the small frictional resistance of the rotor, the operating power of the magnetic suspension compressor quickly rises after the rotor starts to rotate. Moreover, as the starting process progresses, the magnetic suspension compressor starts to work on the refrigerant compression, thereby further improving the operating power. However, in the abnormal start state where the pressure ratio cannot be normally established, the evaporator cannot provide sufficient and stable refrigerant to the compressor, causing the magnetic suspension compressor to easily experience surge when operating at high power, thereby causing the refrigerant to flow backward in the compressor and causing the risk of a decrease in exhaust pressure and an increase in suction pressure. Therefore, the starting load value adapted to the abnormal start state is configured to be a starting load value at which the magnetic suspension compressor does not surge in the abnormal start state, and the magnetic suspension compressor is controlled to operate at the starting load value adapted to the abnormal start state, thereby suppressing the operating power of the magnetic suspension compressor and preventing the occurrence of surge, and improving the construction rate of the pressure ratio.

[0061] It should be noted that in the actual application scenario, the above-mentioned evaporator electromagnetic expansion valve and the opening degree adapted to the abnormal start state, as well as the magnetic suspension compressor and the starting load value adapted to the abnormal start state, can be determined by testing and calibrating the refrigeration system.

[0062] The present application collects the condenser side temperature and the evaporator side temperature by configuration, uses the condenser side temperature to represent the exhaust pressure, uses the evaporator side temperature to represent the suction pressure, and realizes accurate extraction of the parameters for determining whether the refrigeration system is in an abnormal starting state. Subsequently, the evaporator electromagnetic expansion valve is controlled to open to an opening degree adapted to the abnormal starting state, and the opening degree adapted to the abnormal starting state is different from the opening degree of the evaporator electromagnetic expansion valve in the normal starting state, so as to change the refrigerant flow into the evaporator in the abnormal starting state, and adjust the suction pressure and the exhaust pressure by adjusting the refrigerant flow into the evaporator, and then build a normal pressure ratio, and improve the starting reliability of the magnetic suspension compressor. At the same time, by configuring that the balance valve is controlled to be turned on when the refrigeration system is in an abnormal starting state, part of the high-pressure refrigerant output by the magnetic suspension compressor is introduced into the evaporator, so as to increase the refrigerant flow into the evaporator while reducing the exhaust pressure, so as to change the exhaust pressure and the suction pressure, so as to improve the construction rate of the normal pressure ratio compared with the way of only relying on the compressor to independently build the pressure ratio. And, by configuring the starting load value adapted to the abnormal starting state, which is the starting load value of the magnetic suspension compressor without surge in the abnormal starting state, and controlling the magnetic suspension compressor to operate at the starting load value adapted to the abnormal starting state, so as to suppress the operating power of the magnetic suspension compressor and avoid the occurrence of surge phenomenon, and improve the construction rate of the pressure ratio. It can be seen that the present application improves the starting reliability of the refrigeration system configured with the magnetic suspension compressor.

[0063] In a possible implementation, the abnormal starting state includes a first abnormal starting state, a second abnormal starting state and a third abnormal starting state, the control of the evaporator electromagnetic expansion valve to open to the opening degree adapted to the abnormal starting state and the control of the magnetic suspension compressor to operate at the starting load value adapted to the abnormal starting state include:

[0064] In the first abnormal starting state, the evaporator electromagnetic expansion valve is controlled to open to a first opening degree adapted to the first abnormal starting state, and the magnetic suspension compressor is controlled to operate at a first starting load value adapted to the first abnormal starting state, and in the first abnormal starting state, the evaporator side temperature is greater than the condenser side temperature;

[0065] In the second abnormal starting state, the evaporator electromagnetic expansion valve is controlled to open to a second opening degree adapted to the second abnormal starting state, and the magnetic suspension compressor is controlled to operate at a second starting load value adapted to the second abnormal starting state, and in the second abnormal starting state, the evaporator side temperature is less than the condenser side temperature;

[0066] In the third abnormal start state, the evaporator electromagnetic expansion valve is controlled to open to a third opening degree adapted to the third abnormal start state, and the magnetic suspension compressor is controlled to run at a third start load value adapted to the third abnormal start state, and in the third abnormal start state, the evaporator side temperature and the condenser side temperature are both greater than the preset temperature threshold, wherein the first opening degree is greater than the third opening degree, the third opening degree is greater than the second opening degree, the second start load value is greater than the third start load value, and the third start load value is greater than the first start load value.

[0067] It should be noted that in actual application scenarios, since the evaporator side temperature and the condenser side temperature are continuously changing states, in the first abnormal start state, the evaporator side temperature is greater than the condenser side temperature, and at the same time, the evaporator side temperature is not less than the evaporator temperature threshold, and the condenser side temperature does not satisfy the condition of not greater than the condenser temperature threshold, so as to filter the temperature rise in the normal start state. Similarly, in the second abnormal start state, the evaporator side temperature is less than the condenser side temperature, and at the same time, the evaporator side temperature is not greater than the evaporator temperature threshold, and the condenser side temperature is not less than the condenser temperature threshold.

[0068] It should be noted that in the second abnormal start state, the evaporator side temperature is less than the condenser side temperature, so that the internal pressure of the evaporator is relatively low, which is opposite to the normal start state. At this time, by reducing the evaporator electromagnetic expansion opening, the internal pressure of the evaporator can be increased, and at the same time, since the amount of refrigerant flowing into the condenser is reduced, the internal pressure of the condenser is reduced. In the first abnormal start state and the third abnormal start state, since the evaporator side temperature is higher than the evaporator side temperature in the normal start state, the amount of refrigerant entering the evaporator needs to be increased to reduce the evaporator side pressure by heat absorption. Therefore, in order to facilitate actual use, the size relationship between the opening degree in each abnormal start state and the opening degree in the normal start state is: the first opening degree is greater than the third opening degree, the third opening degree is greater than the opening degree in the normal start state, and the opening degree in the normal start state is greater than the second opening degree.

[0069] It should be noted that in actual application scenarios, the inventors of the present application have found that there are four start states of the refrigeration system in the start stage: normal start state, reverse start state, high pressure ratio start state and double high start state. As shown in Figure 2 The figure shows the start state diagram of the refrigeration system obtained by the inventors of the present application after simulating the refrigeration system. Wherein, the abscissa represents the condenser side temperature, and the ordinate represents the evaporator side temperature. As shown in Figure 2It can be known that when the evaporator side temperature is greater than the condenser side temperature (i.e. the first abnormal starting state or the reverse starting state) in the test state, the magnetic suspension compressor of the refrigeration system is in the reverse starting state, at this time, the suction pressure is greater than the exhaust pressure. When the evaporator side temperature is less than the condenser side temperature (i.e. the second abnormal starting state or the high pressure ratio starting state), the magnetic suspension compressor of the refrigeration system is in the high pressure ratio starting state, at this time, the suction pressure is less than the exhaust pressure. When the evaporator side temperature and the condenser side temperature are both greater than the preset temperature threshold (i.e. the third abnormal starting state or the double high starting state), the magnetic suspension compressor of the refrigeration system is in the double high starting state, at this time, the pressure ratio is greater than the upper limit of the normal starting pressure ratio. It can be seen that due to the difference in pressure state in the refrigeration system under different abnormal starting states, the application determines the abnormal starting state based on the evaporator side temperature and the condenser side temperature, and configures the corresponding control mode to be executed, thereby improving the control accuracy under different abnormal starting states, and further improving the construction rate of the normal pressure ratio under different abnormal starting states, and improving the starting reliability of the magnetic suspension compressor. Figure 2 The condenser side temperature of 25℃, 30℃ and 35℃, and the evaporator side temperature of 30℃ are temperature thresholds for distinguishing different abnormal starting states and normal starting states, Figure 2 The other regions except the high pressure ratio starting state, the reverse starting state and the double high starting state belong to the normal starting state.

[0070] It should be noted that in the actual application scenario, when the magnetic suspension compressor is in the first abnormal starting state where the evaporator side temperature is greater than the condenser side temperature, the suction pressure is greater than the exhaust pressure, which may cause a pressure backflow risk. At this time, the higher suction pressure will cause the pressure difference before and after the evaporator electromagnetic expansion valve to decrease, resulting in a decrease in the amount of refrigerant entering the evaporator. Since the evaporator side temperature is greater than the condenser side temperature, the evaporation amount is large, and the demand of the evaporator for refrigerant is greater than that in the normal working condition. If the evaporator electromagnetic expansion valve still maintains a small opening degree as in the normal starting state, the amount of refrigerant entering the evaporator will be small. At this time, if the magnetic suspension compressor still operates at a power corresponding to the high starting load in the normal starting state, the small amount of refrigerant cannot meet the operating requirements of the evaporator and the compressor, resulting in a further decrease in the exhaust pressure, which causes the pressure ratio in the normal starting state to be unable to be established. Therefore, the evaporator electromagnetic expansion valve is controlled to open to a first opening degree adapted to the first abnormal starting state in the present application. Since the first opening degree is the largest opening degree among the three abnormal starting states, the refrigerant flow into the evaporator is increased. Furthermore, the magnetic suspension compressor is controlled to operate at a first starting load value adapted to the first abnormal starting state. Since the first starting load value is the smallest load value among the three abnormal starting states, the magnetic suspension compressor operates at the smallest operating power when operating at the first starting load value. This not only suppresses the surge of the magnetic suspension compressor, but also suppresses the rising rate of the suction pressure and stabilizes the exhaust pressure, thereby improving the establishment rate of the normal pressure ratio.

[0071] It should be noted that in the actual application scenario, when the magnetic suspension compressor is in the second abnormal starting state where the evaporator side temperature is less than the condenser side temperature, the exhaust pressure is greater than the suction pressure, resulting in a pressure ratio greater than the upper limit of the normal starting pressure ratio. Therefore, the evaporator electromagnetic expansion valve is controlled to open to a second opening degree adapted to the second abnormal starting state in the present application. Since the second opening degree is the smallest opening degree among the three abnormal starting states, the suction pressure is reduced by reducing the amount of refrigerant entering the evaporator. Furthermore, the magnetic suspension compressor is controlled to operate at a third starting load value adapted to the third abnormal starting state. Since the second starting load value is the largest load value among the three abnormal starting states, the exhaust pressure will increase. On this basis, by configuring the above-mentioned second opening degree and second starting load value, the exhaust pressure rising rate is less than the suction pressure decreasing rate, so that the pressure ratio is reduced to the normal starting pressure ratio.

[0072] It should be noted that in the actual application scenario, when the magnetic suspension compressor is in the third abnormal starting state in which the evaporator side temperature and the condenser side temperature are both greater than the preset temperature threshold, the pressure ratio is greater than the upper limit of the normal starting pressure ratio. Therefore, the application is configured to control the evaporator electromagnetic expansion valve to open to a third opening degree adapted to the third abnormal starting state, and control the magnetic suspension compressor to operate at a third starting load value adapted to the third abnormal starting state. By configuring the specific values of the third opening degree and the third starting load value, the exhaust pressure rise rate and the suction pressure drop rate are regulated, and the pressure ratio is reduced to the normal starting pressure ratio.

[0073] It should be noted that in the actual application scenario, the control mode of the evaporator electromagnetic expansion valve and the magnetic suspension compressor during the starting stage cannot meet the operation requirements. After the normal pressure ratio is established and the magnetic suspension compressor completes the starting, the control of the evaporator electromagnetic expansion and the magnetic suspension valve can be controlled to cut in the running state after a preset time delay.

[0074] In one possible implementation, the above control of the balance valve conduction includes:

[0075] In the first abnormal starting state, the balance valve is controlled to open to a fourth opening degree adapted to the first abnormal starting state;

[0076] In the second abnormal starting state, the balance valve is controlled to open to a fifth opening degree adapted to the second abnormal starting state;

[0077] In the third abnormal starting state, the balance valve is controlled to open to a sixth opening degree adapted to the third abnormal starting state, the fourth opening degree is greater than the fifth opening degree, and the fifth opening degree is greater than the sixth opening degree.

[0078] It should be noted that in the actual application scenario, the application is configured to increase the refrigerant flow into the evaporator by configuring the fourth opening degree to be greater than the fifth opening degree, and the fifth opening degree to be greater than the sixth opening degree, and configuring the balance valve to open to the fourth opening degree adapted to the first abnormal starting state in the first abnormal starting state. In the second abnormal starting state and the third abnormal starting state, the high-pressure refrigerant output by the magnetic suspension compressor to the condenser is introduced into the evaporator by controlling the balance valve to open to the fifth opening degree adapted to the second abnormal starting state and to open to the sixth opening degree adapted to the third abnormal starting state. Therefore, while reducing the exhaust pressure rise rate, the suction pressure drop rate is also reduced, thereby assisting in establishing a normal pressure ratio.

[0079] It should be noted that in the actual application scenario, the balance valve is opened to destroy the refrigerant circulation in the normal running state. After the normal pressure ratio is built and the magnetic suspension compressor is started, the balance valve can be controlled to be completely closed at a preset closing rate within a preset time period, so as to avoid destroying the refrigerant circulation in the normal running state while reducing the refrigerant impact.

[0080] In a possible implementation, the refrigeration system further comprises: a variable frequency fan, the variable frequency fan being configured to cool a condenser of the refrigeration system.

[0081] The abnormal start control method of the refrigeration system further comprises:

[0082] In the first abnormal start state and the third abnormal start state, the variable frequency fan is controlled to operate at a speed gear adapted to the ambient temperature.

[0083] In the second abnormal start state, the variable frequency fan is controlled to operate at an initial speed gear, and the air speed of the initial speed gear is greater than the air speed of the speed gear adapted to the ambient temperature.

[0084] It should be noted that in the actual application scenario, the condenser is cooled by heat exchange with air. The decrease of the refrigerant temperature will cause the decrease of the exhaust pressure. In the first abnormal start state and the third abnormal start state, the factors causing abnormal pressure ratio are not only the exhaust pressure. Therefore, the application controls the variable frequency fan to operate at a speed gear adapted to the ambient temperature in the first abnormal start state and the third abnormal start state, so as to dynamically adjust the exhaust pressure to adapt to the overall pressure change of the refrigeration system and accelerate the construction rate of the normal pressure ratio.

[0085] It should be noted that in the actual application scenario, in the second abnormal start state, the exhaust pressure is much higher than the suction pressure. Therefore, the application controls the variable frequency fan to operate at an initial speed gear in the second abnormal start state, and the air speed of the initial speed gear is greater than the air speed of the speed gear adapted to the ambient temperature, so as to increase the decrease rate of the exhaust pressure and accelerate the construction rate of the normal pressure ratio. In a possible implementation, the implementation manner of controlling the variable frequency fan to operate at the speed gear adapted to the ambient temperature can be:

[0086] Step A1, collect the ambient temperature T; and trigger steps A2, A3, A4 and A5.

[0087] Step A2, if T≥A1℃, the speed gear is S1 gear.

[0088] Step A3, if A2℃≤T<A1℃, the speed gear is S2 gear.

[0089] Step A4, if A3℃≤T<A2℃, the speed gear is S3 gear.

[0090] Step A5, if T<A4℃, the speed gear is S4 gear.

[0091] It should be noted that in actual application scenarios, the speed of the variable frequency fan affects the refrigeration effect of the refrigeration system in the normal running state. After the normal construction pressure is built and the magnetic suspension compressor is started, the variable frequency fan can be configured to enter the control of the refrigeration system in the normal running state.

[0092] In a possible implementation, the refrigeration system further includes: a variable frequency water pump, the variable frequency water pump being configured to adjust the flow rate of cooling water flowing through the evaporator of the refrigeration system.

[0093] The abnormal start control method of the refrigeration system further includes:

[0094] In the first abnormal start state and the third abnormal start state, the variable frequency water pump is controlled to operate at an abnormal state operating power, and the abnormal state operating power is less than the operating power of the variable frequency water pump in the normal start state.

[0095] It should be noted that in actual application scenarios, the above cooling water is a cooling medium for cooling the environment to be cooled. After the high-temperature cooling water flows into the evaporator, heat exchange is performed between the cooling water and the evaporator, thereby reducing the temperature of the cooling water flowing out of the evaporator, and then cooling the environment to be cooled. In the first abnormal start state and the third abnormal start state, the greater the flow rate of the cooling water in the heat exchange process, the greater the heat exchange amount between the cooling water and the evaporator, resulting in an increase in the pressure of the evaporator, and thus the magnetic suspension compressor needs to increase the operating power to compress the gaseous refrigerant output by the evaporator. In this process, the increase in the operating power of the magnetic suspension compressor may cause overcurrent and overheating risks. Therefore, the present application controls the variable frequency water pump to operate at an abnormal state operating power in the first abnormal start state and the third abnormal start state, and configures the abnormal state operating power to be less than the operating power of the variable frequency water pump in the normal start state, thereby reducing the heat exchange amount of the evaporator to suppress the overcurrent and cooling risks caused by the increase in the operating power of the magnetic suspension compressor, and improving the start reliability.

[0096] It should be noted that in actual application scenarios, the above abnormal state operating power can be determined based on a calibration test. For example, 60% of the operating power in the normal start state is set as the abnormal state operating power.

[0097] In a possible implementation, the above refrigeration system further includes: a standby refrigerant pump, the standby refrigerant pump being configured to deliver refrigerant to the magnetic suspension compressor.

[0098] The abnormal start control method of the above refrigeration system further includes:

[0099] In a case where the actual rotation speed of the magnetic suspension compressor is greater than the start-up rotation speed threshold, the temperature of the magnetic suspension compressor is greater than the alarm temperature threshold, the liquid level height of the liquid accumulator is not less than the preset height threshold, and the standby refrigerant pump is stopped for a time length greater than the minimum stop time length of the main refrigerant pump of the refrigeration system, the standby refrigerant pump is controlled to start running.

[0100] In a case where the magnetic suspension compressor is stopped, the standby refrigerant pump is controlled to stop running; or in a case where the temperature of the magnetic suspension compressor is not greater than the alarm temperature threshold and the standby refrigerant pump is running for a time length exceeding the minimum running time length, the standby refrigerant pump is controlled to stop running; or in a case where the temperature of the magnetic suspension compressor is greater than the alarm temperature threshold and the standby refrigerant pump is running for a time length exceeding the maximum running time length, the standby refrigerant pump is controlled to stop running.

[0101] It should be noted that in an actual application scenario, the present application delivers refrigerant to the magnetic suspension compressor through the standby refrigerant pump to cool the compressor, thereby avoiding the risk of failure stop of the magnetic suspension compressor due to the temperature rising caused by the rising of the running power.

[0102] The second aspect of the present application provides a controller comprising at least one processor and a memory connected to the processor, wherein:

[0103] The memory is configured to store a computer program;

[0104] The processor is configured to execute the computer program to enable the controller to implement the abnormal start control method of the refrigeration system provided in the first aspect of the present application and any possible implementation of the first aspect.

[0105] The present application also provides a controller in an embodiment. Referring to Figure 3 The controller shown in the figure shows a structural schematic diagram suitable for realizing the controller in the embodiment of the present application. The controller in the embodiment of the present application can include but is not limited to fixed terminals such as notebook computers, PDAs (personal digital assistants), PADs (tablet computers), CPUs, etc. Figure 3 The controller shown in the figure is only an example and should not impose any limitation on the functions and use range of the embodiment of the present application.

[0106] As Figure 3As shown, the controller can include a processing device (e.g., a central processor, a graphics processor, etc.) 301 that can perform various appropriate actions and processes according to programs stored in a read-only memory (ROM) 302 or loaded from a storage device 308 into a random access memory (RAM) 303. In a state where the controller is powered on, various programs and data required for the operation of the controller are also stored in the RAM 303. The processing device 301, the ROM 302, and the RAM 303 are connected to each other through a bus 304. An input / output (I / O) interface 305 is also connected to the bus 304.

[0107] Generally, the following devices can be connected to the I / O interface 305: input devices 306 including, for example, a touch screen, a touch pad, a keyboard, a mouse, a camera, a microphone, a temperature sensor, etc.; output devices 307 including, for example, a liquid crystal display (LCD), a balance valve, a magnetic levitation compressor, etc.; storage devices 308 including, for example, a memory card, a hard disk, etc.; and communication devices 309. The communication devices 309 can allow the controller to communicate wirelessly or wired with other devices to exchange data. Although Figure 3 The controller is shown with various devices, but it should be understood that not all of the shown devices are required to be implemented or present. More or fewer devices can alternatively be implemented or present.

[0108] The third aspect of the present application provides a refrigeration system, such as Figure 4 As shown, the refrigeration system includes:

[0109] A magnetic levitation compressor 401, an evaporator electromagnetic expansion valve 402, a balance valve 403, a refrigerant bypass pipeline 404, and a controller 405 as provided in the second aspect of the present application, a refrigerant outlet of the magnetic levitation compressor 401 is in communication with a refrigerant inlet of a condenser 407 of the refrigeration system through a first refrigerant transmission pipeline 406, a refrigerant outlet of the condenser 407 is in communication with a first refrigerant inlet of an evaporator 409 of the refrigeration system through a second refrigerant transmission pipeline 408, a refrigerant outlet of the evaporator 409 is in communication with a refrigerant inlet of the magnetic levitation compressor 401, one end of the refrigerant bypass pipeline 404 bypasses the first refrigerant transmission pipeline 406, and the other end of the refrigerant bypass pipeline 404 is in communication with a second refrigerant inlet of the evaporator 409;

[0110] The evaporator electromagnetic expansion valve 402 is disposed in the second refrigerant transmission pipeline 408 for controlling the flow of refrigerant into the evaporator 409;

[0111] The balance valve 403 is disposed in the refrigerant bypass pipeline 404 for controlling the flow of refrigerant from the first refrigerant transmission pipeline 406 into the evaporator 409;

[0112] The controller 405 is electrically connected with the magnetic suspension compressor 401, the evaporator electromagnetic expansion valve 402 and the balance valve 403 respectively, for controlling the evaporator electromagnetic expansion valve 402 to open to an opening degree adapted to the abnormal starting state, controlling the balance valve 403 to be turned on, and controlling the magnetic suspension compressor 401 to run at a starting load value adapted to the abnormal starting state in the case that the condenser side temperature and the evaporator side temperature indicate that the refrigeration system is in an abnormal starting state, wherein the opening degree adapted to the abnormal starting state is different from the opening degree of the evaporator electromagnetic expansion valve 402 in the normal starting state, and the starting load value adapted to the abnormal starting state is a starting load value at which the magnetic suspension compressor 401 does not occur surge in the abnormal starting state.

[0113] It should be noted that in the actual application scenario, the refrigeration system shown in the structure diagram as described above Figure 4 includes auxiliary elements for refrigeration in the existing refrigeration system, such as the economizer deployed in the second refrigerant transmission pipeline, the sensors in each pipeline, the needle valve, the refrigerant storage tank, etc. Figure 4 The above auxiliary elements are not embodied in order to highlight the elements and connection relationship of the refrigeration system provided by the third aspect of the present application.

[0114] In a possible implementation, when the controller 405 controls the evaporator electromagnetic expansion valve 402 to open to an opening degree adapted to the abnormal starting state, and controls the magnetic suspension compressor 401 to run at a starting load value adapted to the abnormal starting state, it is set to:

[0115] In the first abnormal starting state, the evaporator electromagnetic expansion valve 402 is controlled to open to a first opening degree adapted to the first abnormal starting state, and the magnetic suspension compressor 401 is controlled to run at a first starting load value adapted to the first abnormal starting state, wherein the abnormal starting state includes the first abnormal starting state, the second abnormal starting state and the third abnormal starting state, and in the first abnormal starting state, the evaporator side temperature is greater than the condenser side temperature;

[0116] In the second abnormal starting state, the evaporator electromagnetic expansion valve 402 is controlled to open to a second opening degree adapted to the second abnormal starting state, and the magnetic suspension compressor 401 is controlled to run at a second starting load value adapted to the second abnormal starting state, and in the second abnormal starting state, the evaporator side temperature is less than the condenser side temperature;

[0117] In the third abnormal start state, the evaporator electromagnetic expansion valve 402 is controlled to open to a third opening degree adapted to the third abnormal start state, the magnetic levitation compressor 401 is controlled to run at a third start load value adapted to the third abnormal start state, and in the third abnormal start state, both the evaporator side temperature and the condenser side temperature are greater than the preset temperature threshold value, wherein the first opening degree is greater than the third opening degree, the third opening degree is greater than the second opening degree, the second start load value is greater than the third start load value, and the third start load value is greater than the first start load value.

[0118] In a possible implementation, the refrigeration system provided in the third aspect of the present application further includes:

[0119] A variable frequency fan, which is used to cool the condenser of the refrigeration system;

[0120] The controller 405 is electrically connected with the variable frequency fan, and is configured to control the variable frequency fan to run at an ambient temperature-adapted speed gear in the first abnormal start state and the third abnormal start state, and control the variable frequency fan to run at an initial speed gear in the second abnormal start state, wherein the wind speed of the initial speed gear is greater than the wind speed of the ambient temperature-adapted speed gear.

[0121] In a possible implementation, the refrigeration system provided in the third aspect of the present application further includes:

[0122] A standby refrigerant pump, an inlet of the standby refrigerant pump being in communication with the liquid storage tank of the refrigeration system, and an outlet of the standby refrigerant pump being in communication with the cooling port of the magnetic levitation compressor 401, the standby refrigerant pump being used to deliver refrigerant to the magnetic levitation compressor.

[0123] In a possible implementation, the refrigeration system provided in the third aspect of the present application further includes:

[0124] A cut-in valve and a standby refrigerant bypass pipeline, one end of the standby refrigerant bypass pipeline bypassing the first refrigerant transmission pipeline, and the other end of the standby refrigerant bypass pipeline being in communication with the second refrigerant inlet of the evaporator, the cut-in valve being disposed in the standby refrigerant bypass pipeline and being used to guide part of the refrigerant in the first refrigerant transmission pipeline into the evaporator.

[0125] It should be noted that, in the start phase of the refrigeration system, the function of the cut-in valve is consistent with that of the balance valve 403, and the standby refrigerant bypass pipeline is consistent with the refrigerant bypass pipeline 404. The specific control mode of the cut-in valve is consistent with that of the balance valve 403 provided in the first aspect of the present application and any possible implementation of the first aspect.

[0126] For the purpose of facilitating the understanding of the structure of the refrigeration system provided in the third aspect of the present application and any possible implementation of the third aspect, the present application is described in combination with a possible implementation of the present application:

[0127] AsFigure 5 A refrigeration system is shown in the structural diagram, including: a magnetic suspension compressor 401, an evaporator electromagnetic expansion valve 402, a balance valve 403, a refrigerant bypass pipeline 404, a controller 405, a first refrigerant transmission pipeline 406, a condenser 407, a second refrigerant transmission pipeline 408, an evaporator 409, a variable frequency fan 410, a cut-in valve 411, a standby refrigerant bypass pipeline 412, a refrigerant pump 413, a standby refrigerant pump 414, a variable frequency water pump 415, a cooling water pipeline 416, an economizer 417, a cooling pipeline 418 and a liquid storage tank 419. The refrigerant outlet of the magnetic suspension compressor 401 is communicated with the refrigerant inlet of the condenser 407 of the refrigeration system through the first refrigerant transmission pipeline 406, the refrigerant outlet of the condenser 407 is communicated with the first refrigerant inlet of the evaporator 409 of the refrigeration system through the second refrigerant transmission pipeline 408, the refrigerant outlet of the evaporator 409 is communicated with the refrigerant inlet of the magnetic suspension compressor 401, one end of the refrigerant bypass pipeline 404 bypasses the first refrigerant transmission pipeline 406, the other end of the refrigerant bypass pipeline 404 is communicated with the second refrigerant inlet of the evaporator 409, the balance valve 403 is disposed in the refrigerant bypass pipeline 404, one end of the standby refrigerant bypass pipeline 412 bypasses the first refrigerant transmission pipeline 406, the other end of the standby refrigerant bypass pipeline 412 is communicated with the third refrigerant inlet of the evaporator 409, and the cut-in valve 411 is disposed in the standby refrigerant bypass pipeline 412. The liquid storage tank 419, the refrigerant pump 413, the economizer 417 and the evaporator electromagnetic expansion valve 402 are sequentially arranged in the second refrigerant transmission pipeline 408 along the refrigerant flow direction. One end of the cooling pipeline 418 is communicated with the liquid storage tank 419, and the other end of the cooling pipeline 418 is communicated with the cooling inlet of the magnetic suspension compressor 401. The standby refrigerant pump 414 is arranged in the cooling pipeline 418. The cooling water pipeline 416 passes through the evaporator 409, and the variable frequency water pump 415 is arranged in the cooling water pipeline 416. The variable frequency fan 410 is disposed near the condenser 407. The magnetic suspension compressor 401, the evaporator electromagnetic expansion valve 402, the balance valve 403, the cut-in valve 411, the standby refrigerant pump 414, the variable frequency fan 410 and the variable frequency water pump 415 are electrically connected with the controller 405. Among them, the balance valve 403 and the cut-in valve 411 are used to guide part of the refrigerant in the first refrigerant transmission pipeline 406 into the evaporator 409, the standby refrigerant pump 414 is used to guide the refrigerant in the liquid storage tank into the cooling inlet of the evaporator 409 to cool the evaporator 409, the variable frequency fan 410 is used to cool the condenser 407, and the variable frequency water pump 415 is used to control the cooling water flow rate.

[0128] In addition, it should be noted that the apparatus embodiments described above are merely illustrative, wherein the units described as separate components can or can not be physically separate, and the components displayed as units can or can not be physical units, i.e., can be located in one place, or can be distributed on multiple network units. Part or all of the modules can be selected according to actual needs to achieve the purpose of the embodiment. In addition, the connection relationship between the modules in the apparatus embodiments provided in the present application indicates that there is a communication connection between them, which can be implemented as one or more communication buses or signal lines.

[0129] Through the description of the above embodiments, those skilled in the art can clearly understand that the present application can be realized by means of software and the necessary general hardware, and of course can also be realized by special hardware including special integrated circuits, special CPUs, special memories, special components, etc. Generally, functions completed by computer programs can be easily realized by corresponding hardware, and the specific hardware structure for realizing the same function can also be various, such as analog circuit, digital circuit or special circuit, etc. However, for the present application, software program implementation is a better embodiment. Based on this understanding, the technical solutions of the present application can be embodied in the form of software products, which are stored in readable storage media, such as computer floppy disks, U disks, mobile hard disks, ROM, RAM, magnetic or optical disks, etc., including a plurality of instructions for making a computer device (which can be a personal computer, a training device, or a network device, etc.) execute the methods described in various embodiments of the present application.

[0130] In the above embodiments, all or part can be realized by software, hardware, firmware or any combination thereof. When realized by software, it can be realized in the form of a computer program product in whole or in part.

[0131] The computer program product includes one or more computer instructions. When the computer program instructions are loaded and executed on a computer, the processes or functions described in the embodiments of the present application are generated in whole or in part. The computer can be a general-purpose computer, a special-purpose computer, a computer network, or other programmable devices. The computer instructions can be stored in a computer-readable storage medium or transmitted from one computer-readable storage medium to another computer-readable storage medium, for example, the computer instructions can be transmitted from one website, computer, training device or data center to another website, computer, training device or data center through wired (such as coaxial cable, optical fiber, digital subscriber line (DSL)) or wireless (such as infrared, wireless, microwave, etc.). The computer-readable storage medium can be any available medium that can be stored by the computer or a data storage device such as a training device, a data center, etc. integrated with one or more available media sets. The available media can be a magnetic medium (for example, a floppy disk, a hard disk, a magnetic tape), an optical medium (for example, a DVD), or a semiconductor medium (for example, a solid state disk (SSD)), etc.

Claims

1. An abnormal start-up control method of a refrigeration system, characterized by, The application is applied to a refrigeration system, which comprises a magnetic suspension compressor, an evaporator electromagnetic expansion valve and a balance valve, and an abnormal start control method of the refrigeration system comprises: obtaining a condenser side temperature and an evaporator side temperature of the refrigeration system; in the case that the condenser side temperature and the evaporator side temperature represent that the refrigeration system is in an abnormal start state, controlling the evaporator electromagnetic expansion valve to open to an opening degree adapted to the abnormal start state, controlling the balance valve to be turned on, and controlling the magnetic suspension compressor to operate at a start load value adapted to the abnormal start state, wherein the opening degree adapted to the abnormal start state is different from an opening degree of the evaporator electromagnetic expansion valve in a normal start state, and the start load value adapted to the abnormal start state is a start load value at which the magnetic suspension compressor does not surge in the abnormal start state.

2. The abnormal start-up control method of a refrigeration system according to claim 1, characterized by, The abnormal start state comprises a first abnormal start state, a second abnormal start state and a third abnormal start state, and the control of the evaporator electromagnetic expansion valve to open to the opening degree adapted to the abnormal start state and the control of the magnetic suspension compressor to operate at the start load value adapted to the abnormal start state comprise: in the first abnormal start state, the evaporator side temperature is greater than the condenser side temperature, the evaporator electromagnetic expansion valve is controlled to open to a first opening degree adapted to the first abnormal start state, and the magnetic suspension compressor is controlled to operate at a first start load value adapted to the first abnormal start state; in the second abnormal start state, the evaporator side temperature is less than the condenser side temperature, the evaporator electromagnetic expansion valve is controlled to open to a second opening degree adapted to the second abnormal start state, and the magnetic suspension compressor is controlled to operate at a second start load value adapted to the second abnormal start state; in the third abnormal start state, the evaporator side temperature and the condenser side temperature are both greater than a preset temperature threshold, the evaporator electromagnetic expansion valve is controlled to open to a third opening degree adapted to the third abnormal start state, and the magnetic suspension compressor is controlled to operate at a third start load value adapted to the third abnormal start state, wherein the first opening degree is greater than the third opening degree, the third opening degree is greater than the second opening degree, the second start load value is greater than the third start load value, and the third start load value is greater than the first start load value.

3. The abnormal start-up control method of a refrigeration system according to claim 2, characterized by, The control of the balance valve to be turned on comprises: in the first abnormal start state, the balance valve is controlled to open to a fourth opening degree adapted to the first abnormal start state; in the second abnormal start state, the balance valve is controlled to open to a fifth opening degree adapted to the second abnormal start state; in the third abnormal start state, the balance valve is controlled to open to a sixth opening degree adapted to the third abnormal start state, wherein the fourth opening degree is greater than the fifth opening degree, and the fifth opening degree is greater than the sixth opening degree.

4. The abnormal start-up control method of a refrigeration system according to claim 2, characterized by The refrigeration system further comprises a variable frequency fan for cooling a condenser of the refrigeration system; The abnormal start control method of the refrigeration system further comprises: In the first abnormal start state and the third abnormal start state, the variable frequency fan is controlled to operate at a speed gear adapted to an ambient temperature; In the second abnormal start state, the variable frequency fan is controlled to operate at an initial speed gear, and a wind speed of the initial speed gear is greater than a wind speed of the speed gear adapted to the ambient temperature.

5. The abnormal start-up control method of a refrigeration system according to claim 4, characterized by, The refrigeration system further comprises a variable frequency water pump for adjusting a flow rate of cooling water flowing through an evaporator of the refrigeration system; The abnormal start control method of the refrigeration system further comprises: In the first abnormal start state and the third abnormal start state, the variable frequency water pump is controlled to operate at an abnormal state operating power, and the abnormal state operating power is less than an operating power of the variable frequency water pump in the normal start state.

6. The abnormal start-up control method of a refrigeration system according to any one of claims 1 to 5, characterized in that, The refrigeration system further comprises a standby refrigerant pump for delivering refrigerant to the magnetic suspension compressor; The abnormal start control method of the refrigeration system further comprises: In a case where an actual rotating speed of the magnetic suspension compressor is greater than a start rotating speed threshold, a temperature of the magnetic suspension compressor is greater than an alarm temperature threshold, a liquid level height of a liquid accumulator is not less than a preset height threshold, and a stop running time length of the standby refrigerant pump is greater than a minimum stop running time length of a main refrigerant pump of the refrigeration system, the standby refrigerant pump is controlled to start running; In a case where the magnetic suspension compressor stops running, the standby refrigerant pump is controlled to stop running; or, in a case where the temperature of the magnetic suspension compressor is not greater than the alarm temperature threshold and a running time length of the standby refrigerant pump exceeds a minimum running time length, the standby refrigerant pump is controlled to stop running; or, in a case where the temperature of the magnetic suspension compressor is greater than the alarm temperature threshold and the running time length of the standby refrigerant pump exceeds a maximum running time length, the standby refrigerant pump is controlled to stop running.

7. A controller characterized by comprising: The controller comprises at least one processor and a memory connected with the processor, wherein: The memory is configured to store a computer program; The processor is configured to execute the computer program, so that the controller can implement the abnormal start control method of the refrigeration system according to any one of claims 1 to 6.

8. A refrigeration system characterized by, The controller comprises: a magnetic suspension compressor, an evaporator electromagnetic expansion valve, a balance valve, a refrigerant bypass pipeline, and the controller according to claim 7, a refrigerant outlet of the magnetic suspension compressor is communicated with a refrigerant inlet of a condenser of the refrigeration system through a first refrigerant transmission pipeline, a refrigerant outlet of the condenser is communicated with a first refrigerant inlet of an evaporator of the refrigeration system through a second refrigerant transmission pipeline, a refrigerant outlet of the evaporator is communicated with a refrigerant inlet of the magnetic suspension compressor, one end of the refrigerant bypass pipeline bypasses the first refrigerant transmission pipeline, and the other end of the refrigerant bypass pipeline is communicated with a second refrigerant inlet of the evaporator; The evaporator electromagnetic expansion valve is arranged in the second refrigerant transmission pipeline and is configured to control a refrigerant flow rate flowing into the evaporator. The balance valve is arranged in the refrigerant bypass pipeline and used for controlling the refrigerant flow rate flowing into the evaporator from the first refrigerant transmission pipeline; The controller is electrically connected with the magnetic suspension compressor, the evaporator electromagnetic expansion valve and the balance valve respectively, and is configured to control the evaporator electromagnetic expansion valve to open to an opening degree adapted to an abnormal starting state, control the balance valve to be turned on, and control the magnetic suspension compressor to operate at a starting load value adapted to the abnormal starting state, when the condenser side temperature and the evaporator side temperature indicate that the refrigeration system is in the abnormal starting state, wherein the opening degree adapted to the abnormal starting state is different from an opening degree of the evaporator electromagnetic expansion valve in a normal starting state, and the starting load value adapted to the abnormal starting state is a starting load value at which the magnetic suspension compressor does not surge in the abnormal starting state.

9. The refrigeration system of claim 8, wherein, The controller is configured to: in a first abnormal starting state, control the evaporator electromagnetic expansion valve to open to a first opening degree adapted to the first abnormal starting state, and control the magnetic suspension compressor to operate at a first starting load value adapted to the first abnormal starting state, wherein the abnormal starting state includes the first abnormal starting state, a second abnormal starting state and a third abnormal starting state, and in the first abnormal starting state, the evaporator side temperature is greater than the condenser side temperature; in the second abnormal starting state, control the evaporator electromagnetic expansion valve to open to a second opening degree adapted to the second abnormal starting state, and control the magnetic suspension compressor to operate at a second starting load value adapted to the second abnormal starting state, and in the second abnormal starting state, the evaporator side temperature is less than the condenser side temperature; in the third abnormal starting state, control the evaporator electromagnetic expansion valve to open to a third opening degree adapted to the third abnormal starting state, and control the magnetic suspension compressor to operate at a third starting load value adapted to the third abnormal starting state, and in the third abnormal starting state, both the evaporator side temperature and the condenser side temperature are greater than a preset temperature threshold, wherein the first opening degree is greater than the third opening degree, the third opening degree is greater than the second opening degree, the second starting load value is greater than the third starting load value, and the third starting load value is greater than the first starting load value.

10. The refrigeration system of claim 9, wherein, The refrigeration system further comprises: a variable frequency fan used for cooling a condenser of the refrigeration system; the controller is electrically connected with the variable frequency fan and is configured to control the variable frequency fan to operate at a speed gear adapted to an ambient temperature in the first abnormal starting state and the third abnormal starting state, and control the variable frequency fan to operate at an initial speed gear in the second abnormal starting state, wherein an air speed of the initial speed gear is greater than an air speed of the speed gear adapted to the ambient temperature.

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