Push valve differential pressure correction method of multi-connected system and multi-connected system

Abstract

The application relates to a push valve pressure difference correction method of a multi-connected system and the multi-connected system. Current working condition information of the multi-connected system is acquired; reference push valve pressure difference of the multi-connected system and reference working condition information corresponding to the reference push valve pressure difference are acquired; the reference push valve pressure difference is adjusted based on the current working condition information and the reference working condition information, and a corrected push valve pressure difference is obtained. The reference push valve pressure difference can be corrected according to the current working condition information, the problem that reversing fails and reversing reliability is low when a multi-way valve in an existing multi-connected system is reversed can be solved, the reliability of reversing the multi-way valve in the multi-connected system is improved, and the multi-way valve reversing air failure caused by insufficient push valve pressure difference is avoided.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and in particular to a method for correcting differential pressure of a push valve in a multi-split system and the multi-split system itself. Background Technology

[0002] Multi-split systems (or air conditioning systems) typically use multi-way valves to switch the flow of refrigerant during operation. When switching the multi-way valve, the switching action is usually performed when the pressure difference on both sides of the slider in the multi-way valve reaches a preset pressure difference (also known as the push valve pressure difference, or the pressure difference between the high pressure and low pressure of the multi-split system). However, since the operating conditions of the multi-way valve (or multi-split system) are usually not ideal conditions suitable for the preset pressure difference, there are problems such as switching failure and low switching reliability when switching the multi-way valve. Summary of the Invention

[0003] This application provides a method for correcting differential pressure of a push valve in a multi-split air conditioning system and a multi-split air conditioning system, which can solve the problems of switching failure and low switching reliability when switching the multi-way valve in the existing multi-split air conditioning system.

[0004] In a first aspect, this application provides a method for correcting the differential pressure of a push valve in a multi-split air conditioning system, including:

[0005] Obtain the current operating status information of the multi-unit system;

[0006] Obtain the reference valve differential pressure of the multi-split air conditioning system, and the reference operating condition information corresponding to the reference valve differential pressure;

[0007] Based on the current operating condition information and the baseline operating condition information, the baseline push valve pressure difference is adjusted to obtain the corrected push valve pressure difference.

[0008] In some embodiments, the reference operating condition information includes a reference temperature and a reference refrigerant quantity, and the current operating condition information includes the current temperature and the current refrigerant quantity;

[0009] The step of adjusting the reference push valve pressure difference based on the current operating condition information and the reference operating condition information to obtain the corrected push valve pressure difference includes:

[0010] The temperature effect ratio on the degree of influence of the set operating temperature on the differential pressure of the push valve;

[0011] Set the refrigerant quantity as the proportion of the refrigerant quantity's influence on the differential pressure of the push valve;

[0012] The temperature-corrected differential pressure is obtained based on the temperature influence ratio, the reference temperature, the current temperature, and the reference valve differential pressure.

[0013] The refrigerant quantity correction pressure difference is obtained based on the refrigerant quantity influence ratio, the reference refrigerant quantity, the current refrigerant quantity, and the reference valve pressure difference;

[0014] The corrected push valve pressure difference is obtained based on the temperature-corrected pressure difference and the refrigerant quantity-corrected pressure difference.

[0015] In some embodiments, obtaining the temperature-corrected pressure difference based on the temperature influence ratio, the reference temperature, the current temperature, and the reference valve pressure difference specifically involves:

[0016] By comparing the reference temperature and the current temperature, a temperature correction factor is obtained;

[0017] The temperature-corrected differential pressure is obtained based on the temperature influence ratio, the temperature correction factor, and the reference valve differential pressure.

[0018] In some embodiments, obtaining the refrigerant quantity correction pressure difference based on the refrigerant quantity influence ratio, the reference refrigerant quantity, the current refrigerant quantity, and the reference valve pressure difference specifically involves:

[0019] By comparing the baseline refrigerant quantity with the current refrigerant quantity, a refrigerant quantity correction factor is obtained;

[0020] The refrigerant quantity correction pressure difference is obtained based on the refrigerant quantity influence ratio, the refrigerant quantity correction factor, and the reference valve pressure difference.

[0021] In some embodiments, the reference operating condition information further includes a reference voltage and a reference load, and the current operating condition information further includes the current voltage and the current load;

[0022] The process of obtaining the corrected push valve pressure difference based on the temperature-corrected pressure difference and the refrigerant quantity-corrected pressure difference includes:

[0023] Set the voltage influence ratio of the operating voltage on the differential pressure of the push valve;

[0024] Set the load influence ratio for the degree of influence of the working load on the differential pressure of the push valve;

[0025] The voltage correction differential is obtained based on the voltage influence ratio, the reference voltage, the current voltage, and the reference valve pressure difference;

[0026] The load correction differential is obtained based on the load influence ratio, the reference load, the current load, and the reference push valve differential pressure.

[0027] The corrected push valve pressure difference is obtained based on the temperature-corrected pressure difference, the refrigerant quantity-corrected pressure difference, the voltage-corrected pressure difference, and the load-corrected pressure difference.

[0028] In some embodiments, obtaining the voltage correction differential based on the voltage influence ratio, the reference voltage, the current voltage, and the reference valve differential pressure is specifically as follows:

[0029] By comparing the reference voltage with the current voltage, a voltage correction factor is obtained;

[0030] The voltage correction differential is obtained based on the voltage influence ratio, the voltage correction factor, and the reference valve pressure difference.

[0031] In some embodiments, obtaining the load-corrected differential pressure based on the load influence ratio, the reference load, the current load, and the reference push valve differential pressure specifically involves:

[0032] By comparing the baseline load with the current load, a load correction factor is obtained;

[0033] The load-corrected differential pressure is obtained based on the load influence ratio, the load correction factor, and the reference valve differential pressure.

[0034] Secondly, this application provides a multi-unit system, comprising:

[0035] The first three-way valve has a first compressor exhaust port, a first condensate inlet port and a first compressor suction port;

[0036] The second three-way valve has a second compressor exhaust port, a second condenser inlet port and a second compressor suction port;

[0037] The compressor unit has its exhaust end connected to the first compressor exhaust port and the second compressor exhaust port, and its intake end connected to the first compressor intake port and the second compressor intake port.

[0038] The outdoor unit is connected to the second condenser air inlet;

[0039] The indoor unit is connected at one end to the first condenser air inlet and at the other end to the outdoor unit;

[0040] The hot water unit is connected at one end to the exhaust end of the compressor unit and at the other end to the outdoor unit.

[0041] In some embodiments, the compressor unit includes:

[0042] The compressor assembly has its exhaust end connected to the first compressor exhaust port, the second compressor exhaust port, and the hot water unit;

[0043] The gas-liquid separation component has its suction end connected to the suction port of the first compressor, the suction port of the second compressor, and the outdoor unit, and its discharge end connected to the suction end of the compressor component.

[0044] In some embodiments, the outdoor unit includes:

[0045] The outdoor heat exchange component is connected to the second condenser air inlet;

[0046] The subcooler is connected at one end to the indoor unit and at the other end to the outdoor heat exchange component and the gas-liquid separation component.

[0047] The technical solutions provided in this application have the following advantages compared with the prior art:

[0048] The method for correcting the differential pressure of the push valve in a multi-split air conditioning system and the multi-split air conditioning system provided in this application embodiment obtain the current operating condition information of the multi-split air conditioning system; obtain the reference push valve differential pressure and the reference operating condition information corresponding to the reference push valve differential pressure; adjust the reference push valve differential pressure based on the current operating condition information and the reference operating condition information to obtain the corrected push valve differential pressure. It can correct the reference push valve differential pressure according to the current operating condition information, which can solve the problems of switching failure and low switching reliability when switching multi-way valves in existing multi-split air conditioning systems, improve the reliability of switching multi-way valves in multi-split air conditioning systems, and avoid multi-way valve switching failure due to insufficient push valve differential pressure. Attached Figure Description

[0049] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0050] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0051] One or more embodiments are illustrated by way of example with reference numerals in the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are denoted as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0052] Figure 1 A flowchart of the method for correcting the differential pressure of the push valve in a multi-split air conditioning system provided in the embodiments of this application;

[0053] Figure 2 This is a system diagram of a multi-unit system provided in an embodiment of this application.

[0054] Explanation of reference numerals in the attached figures:

[0055] 10. First three-way valve;

[0056] 20. Second three-way valve;

[0057] 310. Compressor assembly; 3101. Air compressor; 3102. Compressor exhaust temperature sensor; 3103. High-pressure switch; 3104. Oil separator; 3105. Oil filter; 3106. Oil return capillary tube; 3107. Oil return solenoid valve;

[0058] 320. Gas-liquid separation assembly; 3201. Gas-liquid separator; 3202. Low-pressure sensor; 3203. Temperature sensor for steam separator inlet pipe; 3204. Temperature sensor for steam separator outlet pipe;

[0059] 410. Outdoor heat exchange components; 4101. Outdoor heat exchanger; 4102. Condensate outlet temperature sensor; 4103. Subcooling filter; 4104. Heating electronic expansion valve; 4105. Unloading valve;

[0060] 420. Subcooler;

[0061] 50. Indoor unit;

[0062] 60. Hot water unit. Detailed Implementation

[0063] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0064] The following disclosure provides numerous different embodiments or examples for implementing various structures of the invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed.

[0065] For ease of description, spatial relative terms may be used in the text to describe the relative position or movement of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "front," "back," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure undergoes a positional flip, orientation change, or change of motion, these directional indications will change accordingly. For instance, an element described as "below other elements or features" or "below other elements or features" will subsequently be oriented "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptors used in the text will be interpreted accordingly.

[0066] Existing tri-generation multi-split systems can provide air conditioning, underfloor heating, and hot water functions, requiring only one outdoor air conditioning unit to meet multi-functional needs. They achieve different operating modes by switching the direction of two four-way valves within the system. However, in existing tri-generation multi-split systems, the E port (connected to the evaporator's inlet pipe) and C port (connected to the condenser's inlet pipe) of the two four-way valves are connected to long capillary tubes to block the refrigerant flow from the high-pressure area to the low-pressure area. However, even with these long capillary tubes blocking the E and C ports, refrigerant leakage still occurs; the high-pressure refrigerant is directly discharged to the low-pressure area. This leakage is ineffective and reduces the energy efficiency of the tri-generation multi-split system. Furthermore, the existing tri-generation multi-split system, with its two four-way valves, suffers from complex piping connections and limited space.

[0067] When switching the four-way valve (or multi-way valve) in an existing tri-generation multi-split system, the switching action is usually performed when the pressure difference on both sides of the slider in the multi-way valve reaches the preset pressure difference (or push valve pressure difference). However, since the operating conditions of the multi-way valve (or multi-split system) are usually not ideal conditions suitable for the preset pressure difference, there are problems such as switching failure and low switching reliability when switching the multi-way valve.

[0068] Firstly, such as Figure 1 As shown, to address the aforementioned technical problems, this application provides a method for correcting the differential pressure of a push valve in a multi-split air conditioning system, including:

[0069] S101: Obtain the current operating status information of the multi-unit system;

[0070] S102: Obtain the reference valve differential pressure of the multi-split air conditioning system and the reference operating condition information corresponding to the reference valve differential pressure;

[0071] S103: Adjust the reference push valve pressure difference based on the current operating condition information and the reference operating condition information to obtain the corrected push valve pressure difference.

[0072] It should be noted that the current operating condition information of the multi-split air conditioning system can be obtained through various sensors, such as temperature sensors, pressure sensors, flow sensors, voltage sensors, etc. This application does not specifically limit the method of obtaining the current operating condition information. The reference push valve pressure difference is usually a pressure difference set under reference operating conditions to ensure smooth switching of the multi-way valve. However, in actual applications, since the current operating condition information is usually inconsistent with the reference operating condition information, if the multi-way valve (or four-way valve, three-way valve) is switched based on the reference push valve pressure difference under the current operating conditions, there will be insufficient pressure difference on both sides of the slider in the multi-way valve, resulting in failure of switching air leakage. The embodiments of this application adjust the reference push valve pressure difference based on the current operating condition information and the reference operating condition information to obtain the corrected push valve pressure difference. It can adjust the reference push valve pressure difference according to the current operating condition information, and perform switching air leakage when the pressure on both sides of the slider in the multi-way valve reaches the corrected push valve pressure difference, which can ensure successful push valve operation and improve the reliability of the push valve.

[0073] In some embodiments, the reference operating condition information includes a reference temperature and a reference refrigerant quantity, and the current operating condition information includes the current temperature and the current refrigerant quantity;

[0074] The step of adjusting the reference push valve pressure difference based on the current operating condition information and the reference operating condition information to obtain the corrected push valve pressure difference includes:

[0075] The temperature effect ratio on the degree of influence of the set operating temperature on the differential pressure of the push valve;

[0076] Set the refrigerant quantity as the proportion of the refrigerant quantity's influence on the differential pressure of the push valve;

[0077] The temperature-corrected differential pressure is obtained based on the temperature influence ratio, the reference temperature, the current temperature, and the reference valve differential pressure.

[0078] The refrigerant quantity correction pressure difference is obtained based on the refrigerant quantity influence ratio, the reference refrigerant quantity, the current refrigerant quantity, and the reference valve pressure difference;

[0079] The corrected push valve pressure difference is obtained based on the temperature-corrected pressure difference and the refrigerant quantity-corrected pressure difference.

[0080] It should be noted that since the components in different working conditions (such as the working temperature and the working refrigerant amount) have different degrees of influence on the valve pushing pressure difference, a temperature influence ratio representing the degree of influence of working temperature on the valve pushing pressure difference and a refrigerant amount influence ratio representing the degree of influence of working refrigerant amount on the valve pushing pressure difference may be preset, so as to correct the reference valve pushing pressure difference according to the temperature influence ratio and the refrigerant amount influence ratio. The specific value of the temperature influence ratio may be 30%, and the specific value of the refrigerant amount influence ratio may be 20%, which is not specifically limited in the present application.

[0081] It should be noted that after the multi-online system determines the operation mode, the compressor starts to frequency up. Assuming that the valve pushing action is executed when the valve pushing pressure difference Pc-Pe ≥ F, when the compressor frequency is P, if Pc-Pe ≥ F, the valve pushing action is executed; when the compressor frequency is P, if Pc-Pe < F, the valve pushing action is not executed until the compressor frequency increases and Pc-Pe ≥ F, then the valve pushing action is executed, wherein Pc and Pe are the high pressure value and low pressure value of the compressor respectively, F is the friction between the slide block and the valve body in the multi-way valve, and Pc-Pe ≥ F must be ensured throughout the valve pushing process of the multi-way valve (four-way valve or three-way valve); wherein the friction F between the slide block and the valve body is affected by the working temperature and the working refrigerant amount, so it is necessary to correct the friction F according to the current temperature and the current refrigerant amount, that is, correct the reference valve pushing pressure difference Pc-Pe, so as to ensure that the multi-way valve can smoothly perform commutation and air leakage.

[0082] It should be noted that the level of the working temperature and the amount of the working refrigerant of the multi-online system will affect the valve pushing pressure difference on both sides of the slide block in the multi-way valve. Generally speaking: the lower the working temperature of the outdoor environment is, the smaller the valve pushing pressure difference is under the same working frequency of the compressor. In order to ensure the reliability of successful commutation, a larger valve pushing pressure difference needs to be corrected when the current temperature is too low; when the working refrigerant amount is less, the valve pushing pressure difference is smaller under the same working frequency of the compressor. In order to ensure the reliability of successful commutation, when the current refrigerant amount is less than the reference refrigerant amount, a larger valve pushing pressure difference needs to be corrected to ensure the reliability of valve pushing.

[0083] In some embodiments, the obtaining of the temperature correction pressure difference based on the temperature influence ratio, the reference temperature, the current temperature and the reference valve pushing pressure difference is specifically:[ END]]

[0084] Comparing the reference temperature and the current temperature to obtain a temperature correction factor;

[0085] Obtaining a temperature correction pressure difference based on the temperature influence ratio, the temperature correction factor and the reference valve pushing pressure difference.

[0086] It should be noted that by obtaining the temperature correction factor, and based on the temperature influence ratio, the temperature correction factor, and the reference valve pressure difference (i.e., temperature influence ratio C1 × temperature correction factor m1 × reference valve pressure difference Y0), the temperature correction pressure difference can be obtained, thereby correcting the influence of temperature on the reference valve pressure difference. The temperature correction factor can be: if the current temperature T1 > the reference temperature T0, then the temperature correction factor m1 = 1; if the current temperature T1 < the reference temperature T0, then the temperature correction factor m1 > 1. The specific value of m1 can be set according to the proportion by which the current temperature is less than the reference temperature.

[0087] In some embodiments, obtaining the refrigerant quantity correction pressure difference based on the refrigerant quantity influence ratio, the reference refrigerant quantity, the current refrigerant quantity, and the reference valve pressure difference specifically involves:

[0088] By comparing the baseline refrigerant quantity with the current refrigerant quantity, a refrigerant quantity correction factor is obtained;

[0089] The refrigerant quantity correction pressure difference is obtained based on the refrigerant quantity influence ratio, the refrigerant quantity correction factor, and the reference valve pressure difference.

[0090] It should be noted that by obtaining the refrigerant quantity correction factor, and based on the refrigerant quantity influence ratio, the refrigerant quantity correction factor, and the reference valve pressure difference (i.e., refrigerant quantity influence ratio C2 × refrigerant quantity correction factor m2 × reference valve pressure difference Y0), the refrigerant quantity correction pressure difference can be obtained, thereby correcting the influence of refrigerant quantity on the reference valve pressure difference. The refrigerant quantity correction factor can be: if the current refrigerant quantity L1 > the reference refrigerant quantity L0, then the refrigerant quantity correction factor m2 = 1; if the current refrigerant quantity L1 < the reference refrigerant quantity L0, then the refrigerant quantity correction factor m2 > 1. The specific value of m2 can be set according to the proportion by which the current refrigerant quantity is less than the reference refrigerant quantity.

[0091] In some embodiments, the reference operating condition information further includes a reference voltage and a reference load, and the current operating condition information further includes the current voltage and the current load;

[0092] The process of obtaining the corrected push valve pressure difference based on the temperature-corrected pressure difference and the refrigerant quantity-corrected pressure difference includes:

[0093] Set the voltage influence ratio of the operating voltage on the differential pressure of the push valve;

[0094] Set the load influence ratio for the degree of influence of the working load on the differential pressure of the push valve;

[0095] The voltage correction differential is obtained based on the voltage influence ratio, the reference voltage, the current voltage, and the reference valve pressure difference;

[0096] The load correction differential is obtained based on the load influence ratio, the reference load, the current load, and the reference push valve differential pressure.

[0097] The corrected push valve pressure difference is obtained based on the temperature-corrected pressure difference, the refrigerant quantity-corrected pressure difference, the voltage-corrected pressure difference, and the load-corrected pressure difference.

[0098] It should be noted that since the influence of components (such as the working voltage and the working load) on the differential pressure of the push valve is not the same under different operating conditions, the voltage influence ratio of the working voltage on the differential pressure of the push valve and the load influence ratio of the working load on the differential pressure of the push valve can be preset so as to correct the reference differential pressure of the push valve according to the voltage influence ratio and the load influence ratio. The specific value of the voltage influence ratio can be 30%, the specific value of the load influence ratio can be 20%, etc., and this application does not make specific limitations on this.

[0099] It should be noted that the operating voltage and workload of the multi-split air conditioning system affect the pressure difference across the slider of the multi-way valve. Generally speaking: the lower the operating voltage, the smaller the coil current in the multi-way valve (four-way or three-way valve), and the easier it is for the valve to fail to switch at the same compressor frequency. When the voltage of the unit (or system) is less than the reference voltage, a larger pressure difference needs to be adjusted to ensure successful switching. Conversely, a smaller workload (or operating load) means that some refrigerant is actually present in the indoor unit when it is not running, resulting in a smaller pressure difference at the same compressor frequency. To ensure reliable switching, a larger pressure difference needs to be adjusted when the workload of the unit (or system) is too low.

[0100] In some embodiments, obtaining the voltage correction differential based on the voltage influence ratio, the reference voltage, the current voltage, and the reference valve differential pressure is specifically as follows:

[0101] By comparing the reference voltage with the current voltage, a voltage correction factor is obtained;

[0102] The voltage correction differential is obtained based on the voltage influence ratio, the voltage correction factor, and the reference valve pressure difference.

[0103] It should be noted that by obtaining the voltage correction factor, and based on the voltage influence ratio, the voltage correction factor, and the reference valve pressure difference (i.e., voltage influence ratio C3 × voltage correction factor m3 × reference valve pressure difference Y0), the voltage correction pressure difference can be obtained, thereby correcting the influence of voltage on the reference valve pressure difference. The voltage correction factor can be: if the current voltage W1 > the reference voltage W0, then the voltage correction factor m3 = 1; if the current voltage W1 < the reference voltage W0, then the voltage correction factor m3 > 1. The specific value of m3 can be set according to the proportion that the current voltage is less than the reference voltage.

[0104] In some embodiments, obtaining the load-corrected differential pressure based on the load influence ratio, the reference load, the current load, and the reference push valve differential pressure specifically involves:

[0105] By comparing the baseline load with the current load, a load correction factor is obtained;

[0106] The load-corrected differential pressure is obtained based on the load influence ratio, the load correction factor, and the reference valve differential pressure.

[0107] It should be noted that by obtaining the load correction factor, and based on the load influence ratio, the load correction factor, and the reference valve pressure difference (i.e., load influence ratio C4 × load correction factor m4 × reference valve pressure difference Y0), the load correction pressure difference can be obtained, thereby correcting the influence of the load on the reference valve pressure difference. The load correction factor can be: if the current load Q1 > the reference load Q0, then the load correction factor m4 = 1; if the current load Q1 < the reference load Q0, then the load correction factor m4 > 1. The specific value of m4 can be set according to the proportion that the current load is less than the reference load.

[0108] It should be noted that the corrected push valve pressure difference obtained based on the temperature-corrected pressure difference, the refrigerant quantity-corrected pressure difference, the voltage-corrected pressure difference, and the load-corrected pressure difference is: Corrected push valve pressure difference Y = C1×m1×Y0 + C2×m2×Y0 + C3×m3×Y0 + C4×m4×Y0, where C1 + C2 + C3 + C4 = 1. In actual use, after the multi-split system is turned on, the corrected push valve pressure difference is first calculated. Then, the frequency of the air compressor 3101 can be increased so that the pressure difference on both sides of the slider in the multi-way valve reaches the corrected push valve pressure difference, thus executing the push valve action and avoiding multi-way valve switching failure due to insufficient push valve pressure difference.

[0109] In summary, the push valve differential pressure correction method for multi-split air conditioning systems provided in this application obtains the current operating condition information of the multi-split air conditioning system; obtains the reference push valve differential pressure and the reference operating condition information corresponding to the reference push valve differential pressure; and adjusts the reference push valve differential pressure based on the current operating condition information and the reference operating condition information to obtain the corrected push valve differential pressure. This method can correct the reference push valve differential pressure according to the current operating condition information, and can solve the problems of switching failure and low switching reliability when switching multi-way valves in existing multi-split air conditioning systems. It improves the reliability of switching multi-way valves in multi-split air conditioning systems and avoids multi-way valve switching failure due to insufficient push valve differential pressure.

[0110] Secondly, such as Figure 2 As shown in the figure, this application provides a multi-unit air conditioning system, including:

[0111] The first three-way valve 10 has a first compressor exhaust port, a first condensate inlet port and a first compressor suction port;

[0112] The second three-way valve 20 has a second compressor exhaust port, a second condenser inlet port and a second compressor suction port;

[0113] The compressor unit has its exhaust end connected to the exhaust port of the first compressor and the exhaust port of the second compressor, and its intake end connected to the intake port of the first compressor and the intake port of the second compressor.

[0114] The outdoor unit is connected to the second condenser air inlet;

[0115] The indoor unit 50 is connected at one end to the first condenser air inlet and at the other end to the outdoor unit;

[0116] The hot water unit 60 is connected at one end to the exhaust end of the compressor unit and at the other end to the outdoor unit.

[0117] It should be noted that existing tri-generation multi-split systems switch between different operating modes by reversing two four-way valves within the system. Furthermore, the E port (connected to the evaporator's inlet pipe) and C port (connected to the condenser's inlet pipe) of these two four-way valves in existing tri-generation multi-split systems are connected to long capillary tubes to block the refrigerant flow from the high-pressure zone to the low-pressure zone. However, even with long capillary tubes blocking the E and C ports, refrigerant leakage still occurs; the high-pressure refrigerant is directly discharged to the low-pressure zone. This leakage is ineffective and reduces the energy efficiency of the tri-generation multi-split system. Moreover, the existing tri-generation multi-split system, with its two four-way valves, suffers from complex piping connections and limited space. This application addresses this by using a first three-way valve 10 and a second three-way valve 20 connected to the compressor unit, indoor unit 50, and outdoor unit. This simplifies the piping structure and reduces material costs. It also prevents ineffective refrigerant leakage at the long capillary tubes, thereby improving the energy efficiency of the multi-split system.

[0118] In some embodiments, the compressor unit includes:

[0119] The compressor assembly 310 has its discharge end connected to the discharge port of the first compressor, the discharge port of the second compressor, and the hot water unit 60;

[0120] The gas-liquid separation assembly 320 has its suction end connected to the suction inlet of the first compressor, the suction inlet of the second compressor, and the outdoor unit, and its discharge end connected to the suction end of the compressor assembly 310.

[0121] It should be noted that by connecting the exhaust end of the compressor assembly 310 to the first compressor exhaust port (i.e., port D of the first three-way valve 10) and the second compressor exhaust port (i.e., port D of the second three-way valve 20), and connecting the first condenser inlet port (i.e., port C of the first three-way valve 10) of the first three-way valve 10 to the indoor unit 50 and the second condenser inlet port (i.e., port C of the second three-way valve 20) of the second three-way valve 20 to the outdoor unit, and by connecting the hot water unit 60, the outdoor unit, and the compressor assembly 310, multiple operating modes can be switched through a single compressor assembly 310, the switching action of the first three-way valve 10, and the switching action of the second three-way valve 20. The system can switch between modes such as heating, cooling, and hot water production. By connecting the gas-liquid separation component 320 to the first compressor suction port (i.e., the S port of the first three-way valve 10), the second compressor suction port (i.e., the S port of the second three-way valve 20), and the outdoor unit, it can effectively separate liquid components (such as unevaporated refrigerant droplets) that may be carried in the refrigerant flowing from the outdoor unit and indoor unit 50. This allows only gaseous refrigerant to enter the suction end of the compressor assembly 310, preventing liquid refrigerant from directly entering the compressor (i.e., the "liquid slugging" phenomenon). This reduces the impact and wear of internal mechanical parts of the compressor (such as pistons and valve plates), significantly extending the service life of the compressor.

[0122] It should be noted that the compressor unit includes an air compressor 3101, a high-pressure switch 3103 and a compressor exhaust temperature sensor 3102 located on the exhaust end (or compressor exhaust pipe) of the air compressor 3101, and an oil separator 3104. The oil separator 3104 has two discharge pipes (one is an oil separator discharge pipe, and the other is an oil separator exhaust pipe). The oil separator exhaust pipe is connected to the first compressor exhaust port, the second compressor exhaust port, and the hot water unit 60. The oil separator discharge pipe is connected to the air compressor 3101 through an oil separator filter 3105 and an oil return capillary tube 3106. An oil return solenoid valve 3107 is connected in parallel to the oil return capillary tube 3106 to control the oil return. A high-pressure sensor can be installed on the oil separator exhaust pipe to detect the pressure of the oil separator exhaust pipe. By setting the oil return capillary tube 3106, the oil return flow rate can be limited by the pipe diameter. To prevent a sudden influx of large amounts of lubricating oil into the compressor (which could lead to liquid slugging or affect compression efficiency), the return oil solenoid valve 3107 is designed to address the issue of insufficient oil return from the capillary tube, which can cause lubricating oil to accumulate in the oil separator 3104. Prolonged accumulation of lubricating oil in this condition could lead to compressor wear due to lack of oil. In such cases, opening the return oil solenoid valve 3107 increases the return oil flow and replenishes the oil volume. Furthermore, the return oil capillary tube 3106 may become clogged with grease and impurities over time. Relying solely on the capillary tube would interrupt the return oil flow, causing compressor malfunction. By connecting the return oil solenoid valve 3107 in parallel with the return oil capillary tube 3106, a "backup channel" can be formed. When the capillary tube is clogged, the controller can detect abnormal oil return (such as excessively high oil level in the oil separator 3104) and trigger the return oil solenoid valve 3107 to open, preventing interruption of the return oil flow and significantly improving the system's fault tolerance and reliability.

[0123] It should be noted that the gas-liquid separation assembly 320 includes a gas-liquid separator 3201, a low-pressure sensor 3202 and a vapor separator inlet temperature sensor 3203 located on the gas-liquid separator 3201's suction end (or vapor separator suction pipe), and a vapor separator outlet temperature sensor 3204 located on the gas-liquid separator 3201's discharge end (or vapor separator discharge pipe). The gas-liquid separator 3201's discharge end is connected to the air compressor 3101's suction end. The vapor separator inlet temperature sensor 3203 and the low-pressure sensor 3202 can monitor the working fluid state (temperature, pressure) entering the gas-liquid separator 3201 in real time, while the vapor separator outlet temperature sensor 3204 can monitor the temperature of the working fluid entering the compressor after separation. These parameters provide a basis for system control. For example, by adjusting components such as the expansion valve, the working fluid entering the gas-liquid separator 3201 can be kept in a suitable state to ensure maximum separation efficiency.

[0124] In some embodiments, the outdoor unit includes:

[0125] The outdoor heat exchange component 410 is connected to the second condenser air inlet;

[0126] The subcooler 420 is connected at one end to the indoor unit 50 and at the other end to the outdoor heat exchange component 410 and the gas-liquid separation component 320.

[0127] It should be noted that the outdoor heat exchange component 410 is connected to the second condenser inlet, which can make full use of the outdoor environment for heat exchange (dissipating heat as a condenser during cooling and absorbing heat as an evaporator during heating), ensuring that the refrigerant fully exchanges heat during condensation or evaporation, providing a basic guarantee for heat exchange in the system; the subcooler 420 can further cool the refrigerant (or refrigerant) after it has been processed by the outdoor heat exchange component 410, making it a "subcooled liquid" (the temperature is lower than the saturation temperature at the corresponding pressure). When the subcooled liquid enters the throttling device (such as an expansion valve) of the indoor unit 50, it can reduce the "flash gas" (ineffective gas that does not participate in heat exchange) generated by the sudden pressure drop during the throttling process, allowing more refrigerant to enter the indoor evaporator in liquid form and directly participate in heat absorption / release, thereby improving the effective heat exchange efficiency per unit mass of refrigerant and ultimately improving the system's energy efficiency ratio.

[0128] It should be noted that the outdoor heat exchange component 410 includes an outdoor heat exchanger 4101. One end of the outdoor heat exchanger 4101 is connected to the second condenser inlet, and the other end of the outdoor heat exchanger 4101 is connected to the subcooler 420. The pipeline (or subcooling pipeline) between the outdoor heat exchanger 4101 and the subcooler 420 is equipped with a subcooling filter 4103, a condenser outlet temperature sensing bulb 4102, and a heating electronic expansion valve 4104. A relief valve 4105 is connected in parallel to the heating electronic expansion valve 4104.

[0129] It should be noted that by installing a subcooling filter 4103 on the subcooling pipeline, impurities (such as welding slag, oxide scale), moisture, or sludge that may exist in the refrigerant circulation can be intercepted, preventing these contaminants from entering precision components such as the heating electronic expansion valve 4104 and the subcooler 420, and preventing malfunctions such as valve jamming and blockage of the heat exchange tubes of the subcooler 420; by connecting a relief valve 4105 in parallel with the heating electronic expansion valve 4104, it can automatically open when the pressure in the subcooling pipeline rises suddenly due to a malfunction of the heating electronic expansion valve 4104 (such as jamming or malfunction), quickly releasing pressure and preventing the pipeline, outdoor heat exchanger 4101, or subcooler 420 from deforming or cracking due to high pressure; by installing a condenser outlet temperature sensor 4102, the refrigerant temperature at the outlet of the outdoor heat exchanger 4101 can be directly detected.

[0130] It should be noted that the pipeline between the subcooler 420 and the gas-liquid separator 3201 is equipped with an electronic expansion valve for the subcooler 420 and a subcooling outlet temperature sensor. By setting the electronic expansion valve for the subcooler 420 and the subcooling outlet temperature sensor, the refrigerant status (such as temperature and pressure) at the outlet of the subcooler 420 can be monitored in real time, and the valve opening can be precisely adjusted according to the system operating conditions (such as load changes and ambient temperature fluctuations). Valves and filters can be installed on the pipelines connecting the indoor unit 50 and the hot water unit 60 to control the flow rate of the corresponding pipelines and filter impurities.

[0131] It should be noted that the flow path of the multi-split air conditioning system provided in this application embodiment in heating mode is as follows: air compressor 3101 exhaust → oil separator 3104 → first three-way valve 10 (DC connected, power off) → gas-side pipe (low pressure) of indoor unit 50 → indoor unit 50 → liquid side of indoor unit 50 → subcooler 420 → outdoor heat exchanger 4101 → second three-way valve 20 (SC connected, energized) → gas-liquid separator 3201 → air compressor 3101 suction end; the flow path in cooling mode is as follows: air compressor 3101 exhaust → oil separator 3104 → second three-way valve 20 (DC connected, power off) → outdoor heat exchanger 4101 01—> Subcooler 420—> Liquid side of indoor unit 50—> Indoor unit 50—> Gas side of indoor unit 50 (low pressure)—> First three-way valve 10 (SC connected, energized)—> Gas-liquid separator 3201—> Air compressor 3101 suction end; The flow path for hot water mode is: Air compressor 3101 exhaust—> Oil separator 3104—> Gas side pipe of hot water unit 60 (high pressure)—> Hot water generator (hot water unit 60)—> Liquid side of hot water unit 60—> Subcooler 420—> Outdoor heat exchanger 4101—> Second three-way valve 20 (SC connected, energized)—> Gas-liquid separator 3201—> Air compressor 3101 suction end.

[0132] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0133] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0134] The above description is merely a specific embodiment of the present invention, enabling those skilled in the art to understand or implement the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A method for correcting a push valve differential pressure of a multi-split system, characterized in that, Comprising: Acquiring current working condition information of the multi-online system, wherein the current working condition information comprises current temperature, current refrigerant charge, current voltage and current load; Acquiring a reference valve pushing pressure difference of the multi-online system and reference working condition information corresponding to the reference valve pushing pressure difference, wherein the reference working condition information comprises reference temperature, reference refrigerant charge, reference voltage and reference load; Setting a temperature influence proportion C1 of the influence degree of working temperature on the valve pushing pressure difference, a refrigerant charge influence proportion C2 of the influence degree of working refrigerant charge on the valve pushing pressure difference, a voltage influence proportion C3 of the influence degree of working voltage on the valve pushing pressure difference, and a load influence proportion C4 of the influence degree of working load on the valve pushing pressure difference, wherein C1+C2+C3+C4=1; obtaining a temperature correction factor m1 by comparing a reference temperature T0 with a current temperature T1; obtaining a refrigerant charge correction factor m2 by comparing a reference refrigerant charge L0 with a current refrigerant charge L1; obtaining a voltage correction factor m3 by comparing a reference voltage W0 with a current voltage W1; obtaining a load correction factor m4 by comparing a reference load Q0 with a current load Q1; obtaining a corrected valve pushing pressure difference Y based on a formula Y=C1×m1×Y0+C2×m2×Y0+C3×m3×Y0+C4×m4×Y0, wherein Y0 is the reference valve pushing pressure difference; executing a valve pushing action when the pressure difference between two sides of a sliding block in a multi-way valve reaches the corrected valve pushing pressure difference Y; if T1>T0, then m1=1; if T1<T0, then m1>1, and m1 is set according to a proportion of T1 being less than T0; if L1>L0, then m2=1; if L1<L0, then m2>1, and m2 is set according to a proportion of L1 being less than L0; if W1>W0, then m3=1; if W1<W0, then m3>1, and m3 is set according to a proportion of W1 being less than W0; if Q1>Q0, then m4=1; if Q1<Q0, then m4>1, and m4 is set according to a proportion of Q1 being less than Q0.

2. A multi-split system for performing the push valve differential pressure correction method of the multi-split system of claim 1, wherein Comprising: a first three-way valve provided with a first compressor exhaust port, a first condensation air inlet and a first compressor suction port; a second three-way valve provided with a second compressor exhaust port, a second condensation air inlet and a second compressor suction port; a compressor unit, an exhaust end of which is connected to the first compressor exhaust port and the second compressor exhaust port, and a suction end of which is connected to the first compressor suction port and the second compressor suction port; an outdoor unit connected to the second condensation air inlet; an indoor unit, one end of which is connected to the first condensation air inlet, and the other end of which is connected to the outdoor unit; a hot water unit, one end of which is connected to the exhaust end of the compressor unit, and the other end of which is connected to the outdoor unit.

3. The multi-split system according to claim 2, wherein, the compressor unit comprises: a compressor assembly, an exhaust end of which is connected to the first compressor exhaust port, the second compressor exhaust port and the hot water unit; a gas-liquid separation assembly, a suction end of which is connected to the first compressor suction port, the second compressor suction port and the outdoor unit, and an exhaust end of which is connected to a suction end of the compressor assembly.

4. The multi-split system according to claim 3, wherein, the outdoor unit comprises: an outdoor heat exchange assembly connected to the second condensation air inlet; The subcooler is connected at one end to the indoor unit and at the other end to the outdoor heat exchange component and the gas-liquid separation component.

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