Air conditioner control system and method and air conditioner

Abstract

The invention discloses an air conditioner control system and method and an air conditioner, the air conditioner control system is used in the air conditioner, the air conditioner comprises a compressor, an evaporator, a throttling device and a condenser, and the air conditioner control system comprises refrigerant adjusting devices which are arranged at the two ends of the throttling device in parallel, the refrigerant suction device is used for sucking a refrigerant from the throttling device or releasing the refrigerant to the throttling device; and the controller is connected with the refrigerant adjusting device and used for collecting operation parameters of the air conditioner and controlling the refrigerant adjusting device to suck a refrigerant or release the refrigerant according to the operation parameters. The refrigerant adjusting device is additionally arranged in the air conditioner, and the controller is combined to control the refrigerant adjusting device according to the collected operation parameters, so that the refrigerant adjusting device releases the refrigerant or sucks the refrigerant, and the effect of dynamically adjusting the refrigerant flow of the air conditioner according to the operation environment and the self state of the air conditioner is achieved; therefore, the use performance and the operation reliability of the air conditioner are improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioners, and in particular to an air conditioning control system, method and air conditioner. Background Art

[0002] As people's living standards improve, the popularity of air conditioners continues to rise, and the concept of environmental protection is becoming more and more popular. Therefore, developing efficient, energy-saving and environmentally friendly refrigeration systems has become an important goal of the air conditioning industry. Refrigerant is the carrier for realizing energy circulation in the refrigeration cycle. The refrigerant charge of the air conditioning unit has a great impact on the energy efficiency and reliability of the entire air conditioning system. If the refrigerant charge is too small, the air conditioning system may overheat and the compressor temperature may be too high, thereby increasing the load on the compressor and reducing the refrigeration effect; if the refrigerant charge is too much, the air conditioning system pressure may be too high, or the compressor may be compressed with liquid, which may cause the compressor to be damaged, and the refrigeration effect will also be reduced.

[0003] In addition, for split-type air conditioners, refrigerant is transmitted between the indoor and outdoor units through connecting pipes. When the length of the connecting pipe is longer than the standard length, the installer usually adds refrigerant based on the increased length according to previous experience. This results in the accuracy of the additional amount of refrigerant being unreliable, so there will be leakage or excessive addition. Moreover, as the operating time of the equipment increases, there will inevitably be slow leakage of refrigerant, which will also affect the user experience. At the same time, due to the different areas of the indoor heat exchanger and the outdoor heat exchanger, the refrigerant corresponding to the optimal energy efficiency of cooling and heating is often different. In addition, during the operation of the air conditioner, different indoor and outdoor operating conditions correspond to different load states of the air conditioner, especially low-load conditions. In order to prevent liquid compression, only less refrigerant is required to participate in the circulation, which requires the optimal refrigerant charge to change continuously.

[0004] Therefore, how to intelligently adjust the refrigerant flow of the air-conditioning system according to the load status of the air-conditioning unit itself when the operating environment and system load of the air-conditioning unit change greatly, so that the air-conditioning system can always maintain the effect of operating in a better state, is a problem that technical personnel in this field need to solve.

[0005] In this regard, the prior art proposes a variety of solutions, but these solutions all have certain defects. For example, the prior art CN102087057A discloses an air conditioning system that can balance the amount of refrigerant. The disclosed solution can only store a fixed capacity of refrigerant, and it is impossible to adjust the refrigerant flow rate in different temperature ranges of the cooling and heating outer rings of the air conditioning system. For another example, the prior art CN109458747A discloses an air conditioning outdoor unit, an air conditioner, and a method for adjusting the refrigerant in the air conditioner. The solution adjusts the liquid refrigerant content inside the liquid reservoir through two electronic expansion valves, and then adjusts the amount of refrigerant involved in the system circulation, which is used to automatically adjust the amount of refrigerant according to the length of the connecting pipe between the internal and external units of the air conditioner. However, the refrigerant at the inlet and outlet of the liquid reservoir is mainly liquid, and the device has limited refrigerant adjustment capacity. At the same time, when the ambient temperature changes, especially when the system refrigerant is too much at low frequency and low load, it is difficult for the device to achieve the adjustment effect. Summary of the invention

[0006] The embodiments of the present invention provide an air conditioning control system, method and air conditioner, which are intended to dynamically adjust the refrigerant flow of the air conditioner according to the operating environment and the state of the air conditioner, thereby improving the use performance and operating reliability of the air conditioner.

[0007] In a first aspect, an embodiment of the present invention provides an air conditioning control system for use in an air conditioner, wherein the air conditioner comprises a compressor, an evaporator, a throttling device, and a condenser, wherein the compressor, the evaporator, the throttling device, and the condenser are connected via a connecting pipe, and the air conditioning control system comprises:

[0008] A refrigerant regulating device, arranged in parallel at both ends of the throttling device, for sucking refrigerant from the throttling device or releasing refrigerant to the throttling device;

[0009] The controller is connected to the refrigerant regulating device and is used to collect operating parameters of the air conditioner and control the refrigerant regulating device to inhale or release refrigerant according to the operating parameters.

[0010] In a second aspect, an embodiment of the present invention provides an air conditioning control method, which adopts the air conditioning control system as described in the first aspect, and includes:

[0011] collecting operating parameters of the air conditioner;

[0012] The refrigerant regulating device is controlled to inhale refrigerant from the throttling device or release refrigerant to the throttling device according to the operating parameters.

[0013] In a third aspect, an embodiment of the present invention provides an air conditioner, comprising a compressor, an evaporator, a throttling device and a condenser, wherein the compressor, evaporator, throttling device and condenser are connected via a connecting pipe, and also comprises an air conditioning control system as described in the first aspect.

[0014] The embodiment of the present invention provides an air conditioning control system, method and air conditioner, the air conditioning control system is used in the air conditioner, the air conditioner includes a compressor, an evaporator, a throttling device and a condenser, the compressor, the evaporator, the throttling device and the condenser are connected through a connecting pipe, the air conditioning control system includes: a refrigerant regulating device, arranged in parallel at both ends of the throttling device, used to inhale refrigerant from the throttling device or release refrigerant to the throttling device; a controller, connected to the refrigerant regulating device, used to collect the operating parameters of the air conditioner, and control the refrigerant regulating device to inhale refrigerant or release refrigerant according to the operating parameters. The embodiment of the present invention adds a refrigerant regulating device to the air conditioner, and collects the operating parameters of the air conditioner in combination with the controller, and then controls the refrigerant regulating device according to the collected operating parameters to release refrigerant or inhale refrigerant, so as to achieve the effect of dynamically adjusting the refrigerant flow of the air conditioner according to the operating environment and the state of the air conditioner, thereby improving the use performance and operating reliability of the air conditioner, so that the air conditioner can stably maintain an efficient operating state. In addition, based on the controller and the refrigerant regulating device, the air conditioner can intelligently adjust its own refrigerant flow under different connecting pipe lengths or different ambient temperatures. The refrigerant regulating device can also alleviate the operating pressure of the air conditioner, reduce peak pressure pulses and reduce noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other accompanying drawings can be obtained based on these accompanying drawings without paying any creative work.

[0016] Figure 1 A schematic diagram of the structure of an air conditioning control system provided by an embodiment of the present invention;

[0017] Figure 2 A schematic diagram of the structure of an accumulator in an air-conditioning control system provided by an embodiment of the present invention;

[0018] Figure 3 A schematic flow chart of an air conditioning control method provided by an embodiment of the present invention;

[0019] Figure 4 A schematic diagram of a sub-flow chart of step S102 in an air conditioning control method provided by an embodiment of the present invention;

[0020] Figure 5 A schematic diagram of a sub-flow chart of step S202 in an air conditioning control method provided by an embodiment of the present invention;

[0021] Figure 6 A schematic diagram of a sub-flow chart of step S302 in an air conditioning control method provided by an embodiment of the present invention;

[0022] Figure 7 Another sub-flow diagram of step S302 in an air conditioning control method provided by an embodiment of the present invention;

[0023] Figure 8 A schematic diagram of a sub-flow chart of step S303 in an air conditioning control method provided by an embodiment of the present invention;

[0024] Fig. 9 Another sub-flow diagram of step S303 in an air conditioning control method provided by an embodiment of the present invention;

[0025] Fig.10 A schematic diagram of a sub-flow chart of step S304 in an air conditioning control method provided by an embodiment of the present invention;

[0026] Fig.11 A schematic diagram of a sub-flow chart of step S803 in an air conditioning control method provided by an embodiment of the present invention;

[0027] Fig.12 Another sub-flow diagram of step S803 in an air conditioning control method provided by an embodiment of the present invention;

[0028] Fig.13 A schematic diagram of a sub-flow chart of step S203 in an air conditioning control method provided by an embodiment of the present invention. DETAILED DESCRIPTION

[0029] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0030] It should be understood that when used in this specification and the appended claims, the terms "include" and "comprises" indicate the presence of described features, integers, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or combinations thereof.

[0031] It should also be understood that the terms used in this specification of the present invention are only for the purpose of describing specific embodiments and are not intended to limit the present invention. As used in the specification of the present invention and the appended claims, unless the context clearly indicates otherwise, the singular forms "a", "an" and "the" are intended to include plural forms.

[0032] It should be further understood that the term "and / or" used in the present description and the appended claims refers to and includes any and all possible combinations of one or more of the associated listed items.

[0033] See below Figure 1 The embodiment of the present invention provides an air conditioning control system for use in an air conditioner, wherein the air conditioner comprises a compressor 1, an evaporator 2, a throttling device 3 and a condenser 4, wherein the compressor 1, the evaporator 2, the throttling device 3 and the condenser 4 are connected via a connecting pipe, and the air conditioning control system comprises:

[0034] A refrigerant regulating device, which is arranged in parallel at both ends of the throttling device 3, and is used to inhale the refrigerant from the throttling device 3 or release the refrigerant to the throttling device 3;

[0035] The controller is connected to the refrigerant regulating device and is used to collect operating parameters of the air conditioner and control the refrigerant regulating device to inhale or release refrigerant according to the operating parameters.

[0036] This embodiment adds a refrigerant regulating device to the air conditioner, and collects the operating parameters of the air conditioner in combination with the controller, and then controls the refrigerant regulating device according to the collected operating parameters to release or inhale the refrigerant. In this way, the refrigerant flow rate of the air conditioner can be dynamically adjusted according to the operating environment and the state of the air conditioner, thereby improving the performance and operating reliability of the air conditioner, so that the air conditioner can stably maintain an efficient operating state. In addition, based on the controller and the refrigerant regulating device, the air conditioner can intelligently adjust its own refrigerant flow rate under different connecting pipe lengths or different ambient temperatures, and the refrigerant regulating device can also relieve the operating pressure of the air conditioner, reduce the peak pressure pulse and reduce the noise.

[0037] Here, the controller may be a control mainboard in the air conditioner, or may be a separately provided control module, which is only used to adjust the refrigerant flow in the air conditioner. Figure 1 In addition to the compressor 1, the evaporator 2, the throttling device 3 and the condenser 4, the air conditioner may also include a multi-way valve 5 arranged between the compressor 1, the evaporator 2 and the condenser 4. Specifically, the multi-way valve 5 is a four-way valve.

[0038] Combination Figure 2 In one embodiment, the refrigerant conditioning device comprises:

[0039] The accumulator 6 stores refrigerant, and the accumulator 6 is connected in parallel to both ends of the throttling device 3 through a connecting pipe;

[0040] A first control valve 7 is provided between the accumulator 6 and one end of the throttling device 3 close to the condenser 4;

[0041] The second control valve 8 is arranged between the accumulator 6 and one end of the throttling device 3 close to the evaporator 2 .

[0042] Furthermore, the accumulator 6 includes a hollow shell 61 , a deformable bladder 62 filled with gas is arranged inside the shell 61 , and a valve port 63 connecting the outside and the inside of the shell 61 is opened on one side of the shell 61 .

[0043] This embodiment is based on the existing air conditioner structure, and adds a refrigerant regulating device therein. The refrigerant regulating device specifically includes an accumulator 6 connected in parallel at both ends of the air conditioner throttling device 3, and a first control valve 7 and a second control valve 8 are respectively provided at both ends of the accumulator 6 to control the on-off, so as to achieve the effect of controlling the accumulator 6 to release refrigerant or inhale refrigerant. The accumulator 6 specifically includes a shell 61, a bladder 62 and a valve. Here, the accumulator 6 bladder 62 is made of a deformable material, and a certain amount of gas is filled in the bladder 62 (specifically, it can be an inert gas, such as helium, neon, etc.). When the internal pressure of the air conditioner is low, the pressure of the inert gas in the bladder 62 is low, and the volume of the bladder 62 will expand and increase. Figure 2 As shown in part a; when the internal pressure of the air conditioner increases, the high-pressure working fluid enters the housing 61 from the valve port 63, increasing the pressure on the capsule 62, thereby causing the volume of the capsule 62 to be compressed and reduced, as shown in FIG. Figure 2 As shown in part b, based on the volume change of the capsule 62, the accumulator 6 can realize the refrigerant storage or discharge operation.

[0044] In addition, in practical applications, both the first control valve 7 and the second control valve 8 can be solenoid valves, which can be controlled by an electromagnetic coil installed on the valve body, and the electromagnetic coil is connected to the control main board of the air conditioner. When the electromagnetic coil is not energized, the valve port 63 of the accumulator 6 is in a closed state; when the electromagnetic coil is energized, the valve port 63 of the accumulator 6 determines the open state according to the electrical signal.

[0045] like Figure 3 As shown, an embodiment of the present invention provides an air conditioning control method, which is applied to the air conditioning control system as described above. The method specifically includes: steps S101 to S102.

[0046] Step S101, collecting the operating parameters of the air conditioner;

[0047] Step S102 , controlling the refrigerant regulating device to inhale refrigerant from the throttling device 3 or release refrigerant to the throttling device 3 according to the operating parameters.

[0048] In this embodiment, by adding a refrigerant regulating device to the air conditioner, and combining the controller to collect the operating parameters of the air conditioner, and then controlling the refrigerant regulating device according to the collected operating parameters to release or inhale refrigerant, the effect of dynamically adjusting the refrigerant flow of the air conditioner according to the operating environment and the state of the air conditioner can be achieved, thereby improving the performance and operating reliability of the air conditioner, and allowing the air conditioner to stably maintain an efficient operating state. In addition, based on the controller and the refrigerant regulating device, the air conditioner can intelligently adjust its own refrigerant flow at different connecting pipe lengths or different ambient temperatures, and the refrigerant regulating device can also relieve the operating pressure of the air conditioner, reduce the peak pressure pulse and reduce the noise.

[0049] In one embodiment, the operating parameters include the first end pressure and the second end pressure of the throttling device 3, the accumulator pressure, the liquid pipe temperature and the gas pipe temperature of the evaporator 2; the first end pressure is the pressure at one end of the throttling device 3 close to the condenser 4, and the second end pressure is the pressure at one end of the throttling device 3 close to the evaporator 2;

[0050] like Figure 4 As shown, the step S102 includes: steps S201 to S203.

[0051] Step S201: when the air conditioner is in cooling mode, the first end pressure is compared with the accumulator pressure, or when the air conditioner is in heating mode, the second end pressure is compared with the accumulator pressure;

[0052] Step S202: when the first end pressure in the cooling mode or the second end pressure in the heating mode is less than or equal to a preset pressure threshold, the liquid pipe temperature and the gas pipe temperature of the evaporator 2 are obtained, and the first control valve 7 and the second control valve 8 are controlled according to the liquid pipe temperature and the gas pipe temperature of the evaporator 2, so that the accumulator 6 inhales refrigerant or releases refrigerant;

[0053] Step S203: When the first end pressure in the cooling mode or the second end pressure in the heating mode is greater than a preset pressure threshold, the first control valve 7 and the second control valve 8 are controlled according to the first end pressure and the second end pressure to balance the pressure of the accumulator 6.

[0054] In this embodiment, when the air conditioner is running, the pressures P1 (i.e., the first end pressure) and P2 (i.e., the second end pressure) at both ends of the throttling device 3 and the accumulator pressure P0 are obtained, and the pressure at one end of the throttling device 3 is compared with the preset pressure threshold P 限 Here, if the air conditioner is in cooling mode, the pressure at the first end near the condenser 4 is compared with the preset pressure threshold value P 限If the air conditioner is in heating mode, then the pressure at the second end near the evaporator 2 is compared with the preset pressure threshold P 限 Make a comparison.

[0055] Furthermore, when P1≤P 限 Or in heating mode, P2≤P 限 , it means that the air conditioning system pressure has not reached the warning value, and the subsequent refrigerant adjustment operation can be continued; then the current evaporator 2 liquid pipe temperature T1 and gas pipe temperature T2 are obtained, and the superheat ΔT of evaporator 2 is calculated. 蒸 =T2-T1, and the first control valve 7 and the second control valve 8 are controlled in different situations to make the accumulator 6 inhale refrigerant or release refrigerant.

[0056] When P1>P in cooling mode 限 Or in heating mode, P2>P 限 , it means that the air-conditioning system pressure has reached the warning value, which may be due to heavy load, or dirt or blockage in the two devices, etc. At this time, the control signal can be sent by the control main board of the air conditioner or the air conditioner, and the first control valve 7 and the second control valve 8 can be operated accordingly according to different operating modes, so that the accumulator 6 is fully connected to the air-conditioning system through the high-pressure side, thereby alleviating the situation of excessive pressure in the balanced air-conditioning system. At the same time, since the internal bladder 62 of the accumulator 6 can be deformed, it can weaken the peak pressure generated by the compression cycle of the compressor 1 in the air-conditioning system, thereby reducing the abnormal pulse noise when the exhaust pressure is too high. Subsequently, when the air conditioner is operated again t 初始 After a certain time, the operation of step S201 is executed again.

[0057] In one embodiment, if Figure 5 As shown, the step S202 includes: steps S301 to S304.

[0058] Step S301, calculating the temperature difference between the liquid pipe temperature and the gas pipe temperature of the evaporator 2, and comparing the temperature difference with a preset difference; wherein the preset difference includes a first preset difference and a second preset difference, and the first preset difference is greater than the second preset difference;

[0059] Step S302: if the temperature difference is greater than a first preset difference, a first opening coefficient is calculated based on the temperature difference, the first end pressure, the second end pressure and the accumulator pressure, and the first control valve 7 and the second control valve 8 are controlled based on the first opening coefficient so that the accumulator 6 releases the refrigerant;

[0060] Step S303: if the temperature difference is less than a second preset difference, a second opening coefficient is calculated based on the temperature difference, the first end pressure, the second end pressure and the accumulator pressure, and the first control valve 7 and the second control valve 8 are controlled based on the second opening coefficient so that the accumulator 6 inhales refrigerant;

[0061] Step S304: If the temperature difference is less than or equal to the first preset difference and greater than or equal to the second preset difference, the suction superheat of the compressor 1 is obtained, and the suction superheat is compared with the preset superheat threshold to obtain a superheat comparison result, and then the first control valve 7 and the second control valve 8 are controlled according to the superheat comparison result.

[0062] In this embodiment, when P1≤P 限 Or in heating mode, P2≤P 限 When the temperature difference between the liquid pipe temperature and the gas pipe temperature of evaporator 2 is obtained, that is, the superheat ΔT 蒸 =T2-T1, then ΔT 蒸 is compared with the difference range consisting of the first preset difference and the second preset difference. 蒸 When the difference exceeds the first preset value, it indicates that the refrigerant in the evaporator 2 in the cooling mode has completely evaporated and is seriously overheated, the system refrigerant is insufficient, and a refrigerant additional operation is required, or the refrigerant in the evaporator 2 in the heating mode is seriously overcooled, the system refrigerant circulation volume is insufficient, which is not conducive to the performance of the system, and a refrigerant additional operation is required; when ΔT 蒸 If the second preset difference is not reached, it means that the refrigerant in the evaporator 2 in the cooling mode has not been completely evaporated, the system refrigerant is too much, and the refrigerant reduction operation needs to be performed, or the refrigerant in the evaporator 2 in the heating mode is insufficient in supercooling, the system refrigerant circulation volume is too much, and the refrigerant reduction operation needs to be performed. 蒸 When the temperature is between the first preset difference and the second preset difference, it means that the refrigerant in the evaporator 2 is almost completely evaporated. At this time, the suction temperature T of the current air conditioning system can be further obtained. 吸 and suction pressure P 吸 , and calculate P at this time 吸 The corresponding saturation temperature T 吸’ , thus obtaining the suction superheat ΔT at this time 吸 =T 吸 -T 吸’ , and then the first control valve 7 and the second control valve 8 are controlled according to the suction gas superheat.

[0063] Specifically, if Figure 6 As shown, the step S302 includes: steps S401 to S403.

[0064] Step S401: When the air conditioner is in cooling mode, the first opening coefficient in cooling mode is calculated according to the following formula:

[0065] α=(ΔT 蒸 -m) / (P0-P2)

[0066] Where α represents the first opening coefficient in cooling mode, ΔT 蒸 represents the temperature difference, m represents the first preset difference in the cooling mode, P0 represents the accumulator pressure, and P2 represents the second end pressure;

[0067] Step S402, controlling the first control valve 7 to close, and opening the second control valve 8 according to a first opening coefficient in the cooling mode, so that the accumulator 6 releases the refrigerant;

[0068] Step S403: After the opening time of the second control valve 8 reaches a first preset time threshold, the second control valve 8 is controlled to be closed.

[0069] In cooling mode, when ΔT 蒸 When the difference exceeds the first preset value, it means that the refrigerant in the evaporator 2 has completely evaporated and is seriously overheated, the system refrigerant is insufficient, and refrigerant addition operation is required. At this time, the first opening coefficient α is calculated first = (ΔT 蒸 -m) / (P0-P2), and then the control main board sends a signal to close the first control valve 7 and open the second control valve 8, and at the same time control the opening of the second control valve 8 according to the first opening coefficient α. At this time, since P0>P2, the accumulator 6 releases the stored liquid refrigerant through the second control valve 8 and closes after time t0, achieving the purpose of replenishing the circulating refrigerant in the system. Then, run t again 初始 After a certain time, the operation of step S201 is executed again.

[0070] like Figure 7 As shown, the step S302 also includes: steps S501 to S503.

[0071] Step S501: When the air conditioner is in the heating mode, the first opening coefficient in the heating mode is calculated according to the following formula:

[0072] α'=(ΔT 蒸 -m') / (P0-P1)

[0073] Where α' represents the first opening coefficient in the heating mode, ΔT 蒸 represents the temperature difference, m' represents the first preset difference in the heating mode, P0 represents the accumulator pressure, and P1 represents the first end pressure;

[0074] Step S502, opening the first control valve 7 according to the first opening coefficient in the heating mode, and controlling the second control valve 8 to close, so that the accumulator 6 releases the refrigerant;

[0075] Step S503: After the opening time of the first control valve 7 reaches a second preset time threshold, the first control valve 7 is controlled to be closed.

[0076] In heating mode, when ΔT 蒸 When the difference exceeds the first preset value, it means that the refrigerant in the evaporator 2 is seriously overcooled, the refrigerant circulation volume of the system is too small, which is not conducive to the performance of the system, and the refrigerant needs to be added. Specifically, the first opening coefficient α' in the heating mode is calculated as follows: 蒸 -m') / (P0-P1), and then the control main board sends a signal to close the second control valve 8 and open the first control valve 7, and at the same time control the opening of the first control valve 7 according to the first opening coefficient in the heating mode. At this time, since P0>P1, the accumulator 6 releases the stored liquid refrigerant through the first control valve 7 and closes after time t0, so as to achieve the purpose of replenishing the circulating refrigerant of the air conditioning system. Run again t 初始 After a certain time, the operation of step S201 is executed again.

[0077] In another specific embodiment, Figure 8 As shown, the step S303 includes: steps S601 to S604.

[0078] Step S601: when the air conditioner is in cooling mode, the frequency of the compressor 1 is increased and the opening of the throttling device 3 is reduced so that the pressure at the first end is greater than the pressure of the accumulator, and the pressure difference between the pressure at the first end and the pressure of the accumulator reaches a first preset pressure threshold;

[0079] Step S602: Calculate the second opening coefficient in the cooling mode according to the following formula:

[0080] β=(n-ΔT 蒸 ) / (P1-P0)

[0081] Wherein, β represents the second opening coefficient in the cooling mode, n represents the second preset difference in the cooling mode, ΔT 蒸 represents the temperature difference, P1 represents the first end pressure, and P0 represents the accumulator pressure;

[0082] Step S603, opening the first control valve 7 according to the second opening coefficient in the cooling mode, and controlling the second control valve 8 to close, so that the accumulator 6 absorbs the refrigerant;

[0083] Step S604: After the opening time of the first control valve 7 reaches a third preset time threshold, the first control valve 7 is controlled to be closed.

[0084] In this embodiment, when ΔT in the cooling mode 蒸 If the second preset difference is not reached, it means that the refrigerant in the evaporator 2 is not completely evaporated, the system refrigerant is too much, and the refrigerant reduction operation needs to be performed. Specifically, firstly, the frequency of the compressor 1 is temporarily increased step by step, and the opening of the throttling device 3 is reduced to a predetermined value, so that P1 is increased to a certain value exceeding P0. Then calculate the second opening coefficient β in the cooling mode = (n-ΔT 蒸 ) / (P1-P0), and then the control main board sends a signal to close the second control valve 8 and open the first control valve 7, and at the same time control the opening of the first control valve 7 according to the second opening coefficient β in the cooling mode. At this time, since P1>P0, the accumulator 6 absorbs the liquid refrigerant of the air-conditioning system through the first control valve 7, and closes after time t0, while restoring the original frequency of the compressor 1 and the opening of the throttling device 3, restoring the impact on the operating state of the air-conditioning system, and achieving the purpose of reducing the amount of circulating refrigerant in the system. Run again t 初始 After a certain time, the operation of step S201 is executed again.

[0085] like Fig. 9 As shown, the step S303 also includes: steps S701 to S704.

[0086] Step S701: when the air conditioner is in heating mode, the second end pressure is made greater than the accumulator pressure by increasing the frequency of the compressor 1 and reducing the opening of the throttling device 3, and the pressure difference between the second end pressure and the accumulator pressure reaches a second preset pressure threshold;

[0087] Step S702: Calculate the second opening coefficient in the heating mode according to the following formula:

[0088] β'=(n'-ΔT 蒸 ) / (P2-P0)

[0089] Wherein, β' represents the second opening coefficient in the heating mode, n' represents the second preset difference in the heating mode, ΔT 蒸 represents the temperature difference, P2 represents the second end pressure, and P0 represents the accumulator pressure;

[0090] Step S703, controlling the first control valve 7 to close, and opening the second control valve 8 according to the second opening coefficient in the heating mode, so that the accumulator 6 absorbs the refrigerant;

[0091] Step S704: After the opening time of the second control valve 8 reaches a fourth preset time threshold, the second control valve 8 is controlled to be closed.

[0092] When ΔT in heating mode 蒸If the second preset difference is not reached, it means that the subcooling degree of the internal refrigerant of the evaporator 2 is insufficient, the amount of refrigerant circulating in the system is too much, and a refrigerant reduction operation is required. Specifically, first temporarily increase the frequency of the compressor 1 step by step and reduce the opening of the throttling device 3 to a predetermined value, so that P2 is increased to a certain value exceeding P0. Then calculate the second opening coefficient β' in the heating mode = (n'-ΔTevaporation) / (P2-P0), and then the control main board sends a signal to close the first control valve 7 and open the second control valve 8, and at the same time control the opening of the second control valve 8 according to the second opening coefficient in the heating mode. At this time, since P2>P0, the accumulator 6 sucks in the liquid refrigerant of the air-conditioning system through the second control valve 8, and closes after time t0, while restoring the original frequency of the compressor 1 and the opening of the throttling device 3, restoring the impact on the operating state of the air-conditioning system, and achieving the purpose of reducing the amount of circulating refrigerant in the air-conditioning system. Run again t 初始 After a certain time, the operation of step S201 is executed again.

[0093] In actual application scenarios, the first preset difference and the second preset difference in cooling mode may be 3 and 0, and the first preset difference and the second preset difference in heating mode may be 5 and 1, that is, m=3, m'=5, n=0, n'=1.

[0094] In one embodiment, if Fig.10 As shown, the step S304 includes: steps S801 to S803.

[0095] Step S801, obtaining the suction temperature and suction pressure of the compressor 1, and obtaining the corresponding saturation temperature according to the suction pressure, and then calculating the suction superheat according to the suction temperature and the saturation temperature;

[0096] Step S802: When the suction air superheat is greater than or equal to a preset superheat threshold, maintaining the current operating state of the air conditioner;

[0097] Step S803: When the suction air superheat is less than a preset superheat threshold, the first control valve 7 and the second control valve 8 are controlled by increasing the frequency of the compressor 1 and reducing the opening of the throttling device 3.

[0098] In this embodiment, when ΔT in the cooling mode 蒸 When the ΔT in the heating mode is between the first preset difference and the second preset difference, it means that the refrigerant in the evaporator 2 is almost completely evaporated, or when the ΔT in the heating mode is 蒸 When the temperature is between the first preset difference and the second preset difference, it means that the subcooling degree of the refrigerant inside the evaporator 2 is relatively appropriate, so the suction temperature T of the current air conditioning system is further obtained. 吸 and suction pressure P 吸 , and obtain P at this time 吸The corresponding saturation temperature T 吸’ , and calculate the suction superheat ΔT at this time 吸 =T 吸 -T 吸’ Then the suction gas superheat ΔT 吸 is compared with the preset superheat threshold. In practical applications, the preset superheat threshold can be set to 1. Then, when ΔT 吸 ≥1, it means that the suction superheat is sufficient, the amount of circulating refrigerant in the system is appropriate, and the system is operating normally. 吸 When it is less than 1, it indicates that the suction superheat is insufficient and the air conditioning system load is relatively light at this time. To prevent compressor 1 from carrying liquid into compression, it is necessary to perform a refrigerant reduction operation.

[0099] Specifically, Fig.11 As shown, the step S803 includes: steps S901 to S904.

[0100] Step S901, when the air conditioner is in cooling mode, by increasing the frequency of the compressor 1 and reducing the opening of the throttling device 3, the pressure at the second end is made greater than the pressure at the first end, and the pressure difference between the pressure at the second end and the pressure at the first end reaches a third preset pressure threshold;

[0101] Step S902: Calculate the third opening coefficient in the cooling mode according to the following formula:

[0102] γ=(k-ΔT 吸 ) / (P1-P0)

[0103] Wherein, γ represents the third opening coefficient in cooling mode, k represents the preset superheat threshold in cooling mode, ΔT 吸 represents suction superheat, P1 represents the first end pressure, and P0 represents the accumulator pressure;

[0104] Step S903, opening the first control valve 7 according to the third opening coefficient in the cooling mode, and controlling the second control valve 8 to close, so that the accumulator 6 absorbs refrigerant;

[0105] Step S904: After the opening time of the first control valve 7 reaches a fifth preset time threshold, the first control valve 7 is controlled to be closed.

[0106] In cooling mode, when ΔT 吸 When ΔT<1, firstly, the frequency of compressor 1 is temporarily increased step by step, and the opening of throttling device 3 is reduced to a predetermined value, so that P1 is increased to a certain value exceeding P0. Then, the third opening coefficient γ in the cooling mode is calculated as (1-ΔT 吸) / (P1-P0), and then the control main board sends a signal to close the second control valve 8 and open the first control valve 7. At the same time, the opening degree of the first control valve 7 is determined according to the third opening coefficient γ in the cooling mode.

[0107] At this time, since P1>P0, the accumulator 6 absorbs the liquid refrigerant of the air conditioning system through the first control valve 7 and closes after time t0, while restoring the original frequency of the compressor 1 and the opening of the throttling device 3, restoring the impact on the system operation state and achieving the purpose of reducing the amount of circulating refrigerant in the system. 初始 After a certain time, the operation of step S201 is executed again.

[0108] like Fig.12 As shown, the step S803 also includes: steps S1001 to S1004.

[0109] Step S1001, when the air conditioner is in heating mode, by increasing the frequency of the compressor 1 and reducing the opening of the throttling device 3, the pressure at the first end is greater than the pressure at the second end, and the pressure difference between the pressure at the first end and the pressure at the second end reaches a fourth preset pressure threshold;

[0110] Step S1002: Calculate the third opening coefficient in the heating mode according to the following formula:

[0111] γ'=(k'-ΔT 吸 ) / (P2-P0)

[0112] Wherein, γ' represents the third opening coefficient in the heating mode, k' represents the preset superheat threshold in the heating mode, ΔT 吸 represents suction superheat, P2 represents the second end pressure, and P0 represents the accumulator pressure;

[0113] Step S1003, controlling the first control valve 7 to close, and opening the second control valve 8 according to the third opening coefficient in the heating mode, so that the accumulator 6 absorbs the refrigerant;

[0114] Step S1004: After the opening time of the second control valve 8 reaches a sixth preset time threshold, the second control valve 8 is controlled to be closed.

[0115] In heating mode, when ΔT 吸 When γ' is less than 1, the frequency of compressor 1 is temporarily increased step by step, and the opening of throttling device 3 is reduced to a predetermined value, so that P2 is increased to a certain value exceeding P0. Then the third opening coefficient γ' in heating mode is calculated as (1-ΔT 吸 ) / (P2-P0), and then the control main board sends a signal to close the first control valve 7 and open the second control valve 8, and at the same time determine the opening degree of the second control valve 8 according to the third opening coefficient γ' in the cooling mode.

[0116] At this time, since P2>P0, the accumulator 6 absorbs the liquid refrigerant of the air conditioning system through the second control valve 8 and closes after time t0. At the same time, the original frequency of the compressor 1 and the opening of the throttling device 3 are restored, the impact on the system operation state is restored, and the purpose of reducing the amount of circulating refrigerant in the system is achieved. 初始 After a certain time, the operation of step S201 is executed again.

[0117] In one embodiment, if Fig.13 As shown, the step S203 includes: steps S1101 to S1102.

[0118] Step S1101: when the air conditioner is in cooling mode, the first control valve 7 is controlled to be opened, and the second control valve 8 is controlled to be closed, so that the accumulator 6 is connected to the air conditioner through the high-pressure side and the pressure is balanced;

[0119] Step S1102: When the air conditioner is in heating mode, the first control valve 7 is controlled to be opened, and the second control valve 8 is controlled to be closed, so that the accumulator 6 is connected to the air conditioner through the high-pressure side and balances the pressure.

[0120] In this embodiment, when P1>P 限 Or in heating mode, P2>P 限 , it means that the pressure of the air conditioning system has reached the warning value, which may be due to heavy load, or dirt blockage of the two devices, etc. At this time, the control signal can be sent by the control mainboard of the air conditioner or the air conditioner. Specifically, in the cooling mode, the accumulator 6 is fully connected to the air conditioning system through the high-pressure side by controlling the first control valve 7 to open and the second control valve 8 to close, or in the heating mode, the accumulator 6 is fully connected to the air conditioning system through the high-pressure side by controlling the second control valve 8 to open and the first control valve 7 to close, thereby alleviating the situation of excessive pressure in the balanced air conditioning system. At the same time, since the internal capsule 62 of the accumulator 6 can be deformed, it can weaken the peak pressure generated by the compression cycle of the compressor 1 in the air conditioning system, thereby reducing the abnormal pulse noise when the exhaust pressure is too high.

[0121] An embodiment of the present invention also provides an air conditioner, including a compressor 1, an evaporator 2, a throttling device 3 and a condenser 4, wherein the compressor 1, evaporator 2, throttling device 3 and condenser 4 are connected via a connecting pipe, and also includes the air conditioning control system as described above.

[0122] The various embodiments in the specification are described in a progressive manner, and each embodiment focuses on the differences from other embodiments. The same and similar parts between the various embodiments can be referred to each other. For the system disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant parts can be referred to the method part description. It should be pointed out that for ordinary technicians in this technical field, without departing from the principles of this application, several improvements and modifications can be made to the present application, and these improvements and modifications also fall within the scope of protection of the claims of this application.

[0123] It should also be noted that, in this specification, relational terms such as first and second, etc. are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the terms "comprises", "comprising" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the statement "comprising a ..." does not exclude the presence of other identical elements in the process, method, article or device including the element.

Claims

1. An air conditioning control system, used in an air conditioner, the air conditioner comprising a compressor, an evaporator, a throttling device and a condenser, the compressor, the evaporator, the throttling device and the condenser being connected through a connecting pipe, characterized in that: The air conditioning control system comprises: A refrigerant regulating device, arranged in parallel at both ends of the throttling device, for sucking refrigerant from the throttling device or releasing refrigerant to the throttling device; The controller is connected to the refrigerant regulating device and is used to collect operating parameters of the air conditioner and control the refrigerant regulating device to inhale or release refrigerant according to the operating parameters.

2. The air conditioning control system according to claim 1, characterized in that: The refrigerant regulating device comprises: An accumulator stores refrigerant, and the accumulator is connected in parallel to two ends of the throttling device through a connecting pipe; a first control valve, arranged between the accumulator and an end of the throttling device close to the condenser; The second control valve is arranged between the accumulator and one end of the throttling device close to the evaporator.

3. The air conditioning control system according to claim 2, characterized in that: The accumulator comprises a hollow shell, a deformable sac filled with gas is arranged inside the shell, and a valve port connecting the outside and the inside of the shell is opened on one side of the shell.

4. An air conditioning control method, applied to the air conditioning control system according to any one of claims 1 to 3, characterized in that: include: collecting operating parameters of the air conditioner; The refrigerant regulating device is controlled to inhale refrigerant from the throttling device or release refrigerant to the throttling device according to the operating parameters.

5. The air conditioning control method according to claim 4 is applied to the air conditioning control system according to claim 2, characterized in that: The operating parameters include the first end pressure and the second end pressure of the throttling device, the accumulator pressure, the liquid pipe temperature and the gas pipe temperature of the evaporator; the first end pressure is the pressure at one end of the throttling device close to the condenser, and the second end pressure is the pressure at one end of the throttling device close to the evaporator; The controlling the refrigerant regulating device to inhale refrigerant from the throttling device or release refrigerant to the throttling device according to the operating parameters includes: When the air conditioner is in cooling mode, the first end pressure is compared with the accumulator pressure, or when the air conditioner is in heating mode, the second end pressure is compared with the accumulator pressure; When the first end pressure in the cooling mode or the second end pressure in the heating mode is less than or equal to a preset pressure threshold, obtaining the liquid pipe temperature and the gas pipe temperature of the evaporator, and controlling the first control valve and the second control valve according to the liquid pipe temperature and the gas pipe temperature of the evaporator, so that the accumulator inhales refrigerant or releases refrigerant; When the first end pressure in cooling mode or the second end pressure in heating mode is greater than a preset pressure threshold, the first control valve and the second control valve are controlled according to the first end pressure and the second end pressure to balance the pressure of the accumulator.

6. The air conditioning control method according to claim 5, characterized in that: When the first end pressure in the cooling mode or the second end pressure in the heating mode is less than or equal to a preset pressure threshold, the liquid pipe temperature and the gas pipe temperature of the evaporator are obtained, and the first control valve and the second control valve are controlled according to the liquid pipe temperature and the gas pipe temperature of the evaporator so that the accumulator inhales refrigerant or releases refrigerant, including: Calculating the temperature difference between the liquid pipe temperature and the gas pipe temperature of the evaporator, and comparing the temperature difference with a preset difference; wherein the preset difference includes a first preset difference and a second preset difference, and the first preset difference is greater than the second preset difference; If the temperature difference is greater than a first preset difference, a first opening coefficient is calculated based on the temperature difference, the first end pressure, the second end pressure and the accumulator pressure, and the first control valve and the second control valve are controlled based on the first opening coefficient so that the accumulator releases the refrigerant; If the temperature difference is less than a second preset difference, a second opening coefficient is calculated based on the temperature difference, the first end pressure, the second end pressure and the accumulator pressure, and the first control valve and the second control valve are controlled based on the second opening coefficient so that the accumulator inhales refrigerant; If the temperature difference is less than or equal to the first preset difference and greater than or equal to the second preset difference, the suction superheat of the compressor is obtained, and the suction superheat is compared with the preset superheat threshold to obtain a superheat comparison result, and then the first control valve and the second control valve are controlled according to the superheat comparison result.

7. The air conditioning control method according to claim 6, characterized in that: If the temperature difference is greater than a first preset difference, a first opening coefficient is calculated based on the temperature difference, the first end pressure, the second end pressure and the accumulator pressure, and the first control valve and the second control valve are controlled based on the first opening coefficient so that the accumulator releases the refrigerant, including: When the air conditioner is in cooling mode, the first opening coefficient in cooling mode is calculated according to the following formula: α=(ΔT 蒸 -m) / (P0-P2) Where α represents the first opening coefficient in cooling mode, ΔT 蒸 represents the temperature difference, m represents the first preset difference in the cooling mode, P0 represents the accumulator pressure, and P2 represents the second end pressure; Controlling the first control valve to close, and opening the second control valve according to a first opening coefficient in a cooling mode, so that the accumulator releases refrigerant; After the opening time of the second control valve reaches a first preset time threshold, controlling the second control valve to close; When the air conditioner is in the heating mode, the first opening coefficient in the heating mode is calculated according to the following formula: α'=(ΔT 蒸 -m') / (P0-P1) Where α' represents the first opening coefficient in the heating mode, ΔT 蒸 represents the temperature difference, m' represents the first preset difference in the heating mode, P0 represents the accumulator pressure, and P1 represents the first end pressure; opening the first control valve according to a first opening coefficient in a heating mode, and controlling the second control valve to close, so that the accumulator releases refrigerant; After the opening time of the first control valve reaches a second preset time threshold, the first control valve is controlled to be closed.

8. The air conditioning control method according to claim 6, characterized in that: If the temperature difference is less than a second preset difference, a second opening coefficient is calculated based on the temperature difference, the first end pressure, the second end pressure and the accumulator pressure, and the first control valve and the second control valve are controlled based on the second opening coefficient so that the accumulator inhales refrigerant, including: When the air conditioner is in cooling mode, the compressor frequency is increased and the throttling device opening is reduced so that the first end pressure is greater than the accumulator pressure, and the pressure difference between the first end pressure and the accumulator pressure reaches a first preset pressure threshold; Calculate the second opening coefficient in cooling mode according to the following formula: β=(n-ΔT 蒸 ) / (P1-P0) Wherein, β represents the second opening coefficient in the cooling mode, n represents the second preset difference in the cooling mode, ΔT 蒸 represents the temperature difference, P1 represents the first end pressure, and P0 represents the accumulator pressure; opening the first control valve according to a second opening coefficient in a cooling mode, and controlling the second control valve to close so that the accumulator absorbs refrigerant; After the opening time of the first control valve reaches a third preset time threshold, controlling the first control valve to close; When the air conditioner is in heating mode, the compressor frequency is increased and the throttling device opening is reduced so that the second end pressure is greater than the accumulator pressure, and the pressure difference between the second end pressure and the accumulator pressure reaches a second preset pressure threshold; Calculate the second opening coefficient in heating mode according to the following formula: β'=(n'-ΔT 蒸 ) / (P2-P0) Wherein, β' represents the second opening coefficient in the heating mode, n' represents the second preset difference in the heating mode, ΔT 蒸 represents the temperature difference, P2 represents the second end pressure, and P0 represents the accumulator pressure; Controlling the first control valve to close, and opening the second control valve according to a second opening coefficient in a heating mode, so that the accumulator absorbs refrigerant; After the opening time of the second control valve reaches a fourth preset time threshold, the second control valve is controlled to be closed.

9. The air conditioning control method according to claim 6, characterized in that: If the temperature difference is less than or equal to the first preset difference and greater than or equal to the second preset difference, the suction superheat of the compressor is obtained, and the suction superheat is compared with a preset superheat threshold to obtain a superheat comparison result, and then the first control valve and the second control valve are controlled according to the superheat comparison result, including: Obtaining the suction temperature and suction pressure of the compressor, and obtaining the corresponding saturation temperature according to the suction pressure, and then calculating the suction superheat according to the suction temperature and the saturation temperature; When the suction air superheat is greater than or equal to a preset superheat threshold, maintaining the current operating state of the air conditioner; When the suction air superheat is less than a preset superheat threshold, the first control valve and the second control valve are controlled by increasing the compressor frequency and reducing the throttling device opening.

10. The air conditioning control method according to claim 9, characterized in that: When the suction air superheat is less than a preset superheat threshold, the first control valve and the second control valve are controlled by increasing the compressor frequency and reducing the throttling device opening, including: When the air conditioner is in cooling mode, the pressure at the second end is made greater than the pressure at the first end by increasing the compressor frequency and reducing the opening of the throttling device, and the pressure difference between the pressure at the second end and the pressure at the first end reaches a third preset pressure threshold; Calculate the third opening coefficient in cooling mode according to the following formula: γ=(k-ΔT 吸 ) / (P1-P0) Wherein, γ represents the third opening coefficient in cooling mode, k represents the preset superheat threshold in cooling mode, ΔT 吸 represents suction superheat, P1 represents the first end pressure, and P0 represents the accumulator pressure; opening the first control valve according to a third opening coefficient in the cooling mode, and controlling the second control valve to close, so that the accumulator absorbs refrigerant; After the opening time of the first control valve reaches a fifth preset time threshold, controlling the first control valve to close; When the air conditioner is in heating mode, the pressure at the first end is made greater than the pressure at the second end by increasing the compressor frequency and reducing the opening of the throttling device, and the pressure difference between the pressure at the first end and the pressure at the second end reaches a fourth preset pressure threshold; Calculate the third opening coefficient in heating mode according to the following formula: γ'=(k'-ΔT 吸 ) / (P2-P0) Wherein, γ' represents the third opening coefficient in the heating mode, k' represents the preset superheat threshold in the heating mode, ΔT 吸 represents suction superheat, P2 represents the second end pressure, and P0 represents the accumulator pressure; Controlling the first control valve to close, and opening the second control valve according to a third opening coefficient in a heating mode, so that the accumulator absorbs refrigerant; After the opening time of the second control valve reaches a sixth preset time threshold, the second control valve is controlled to be closed.

11. The air conditioning control method according to claim 5, characterized in that: When the first end pressure in the cooling mode or the second end pressure in the heating mode is greater than a preset pressure threshold, the first control valve and the second control valve are controlled according to the first end pressure and the second end pressure to balance the pressure of the accumulator, including: When the air conditioner is in cooling mode, the first control valve is controlled to be opened, and the second control valve is controlled to be closed, so that the accumulator is connected to the air conditioner through the high-pressure side and the pressure is balanced; When the air conditioner is in a heating mode, the first control valve is controlled to be opened, and the second control valve is controlled to be closed, so that the accumulator is connected to the air conditioner through the high-pressure side and the pressure is balanced.

12. An air conditioner, comprising a compressor, an evaporator, a throttling device and a condenser, wherein the compressor, the evaporator, the throttling device and the condenser are connected via a connecting pipe, characterized in that: It also includes an air conditioning control system as described in any one of claims 1 to 3.

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