A control method for a heat pump system and a heat pump system

Abstract

The application provides a control method for a heat pump system and the heat pump system, and comprises a compressor, a hot water heat exchanger, an outdoor air heat exchanger, a cold water heat exchanger and a gas-liquid separator which are connected by a circulating pipeline assembly, and the circulating pipeline assembly comprises an output pipeline, a first input pipeline, a second input pipeline and a third input pipeline; wherein a first pipeline assembly arranged on the liquid side of the outdoor air heat exchanger is connected with a second pipeline assembly composed of the first input pipeline and the output pipeline and a third pipeline assembly composed of the second input pipeline and the third input pipeline; the technical problem solved by the application is that in the existing heat pump system, the maximum refrigerant medium is in the refrigeration main mode, after the refrigerant medium is filled into the heat pump system, in other refrigeration modes, heating modes and heating main modes, the excessive refrigerant liquid is retained in the condenser, which causes the refrigerant medium to be over-cooled too much, the condensation temperature of the refrigerant medium is increased, and thus the heat exchange effect of the heat pump system is affected.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat pumps, in particular to a control method for a heat pump system and the heat pump system. BACKGROUND

[0002] As a kind of high-efficiency energy-saving device that makes full use of low-grade heat energy, heat pump system has air conditioning function (including refrigeration function and heating function), hot water function and refrigeration water function in practical application, which meets the user's hot water demand and air conditioning demand.

[0003] However, at least one of the following problems exists in the related art: in the existing heat pump system, the maximum refrigerant volume (herein referred to as volume L, not flow kg / s) of the refrigerant medium is in the refrigeration main mode, after filling the refrigerant volume into the heat pump system, the excess refrigerant liquid is retained in the condenser in other refrigeration modes, heating modes and heating main modes, which causes the refrigerant medium to have too large supercooling degree, and the refrigerant medium condensing temperature rises, thereby affecting the heat exchange effect of the heat pump system. SUMMARY

[0004] The technical problem solved by the present application is that in the existing heat pump system, the maximum refrigerant volume (herein referred to as volume L, not flow kg / s) of the refrigerant medium is in the refrigeration main mode, after filling the refrigerant volume into the heat pump system, the excess refrigerant liquid is retained in the condenser in other refrigeration modes, heating modes and heating main modes, which causes the refrigerant medium to have too large supercooling degree, and the refrigerant medium condensing temperature rises, thereby affecting the heat exchange effect of the heat pump system.

[0005] To solve the above problems, on the one hand, the present application provides a heat pump system, the heat pump system comprises a compressor, a hot water heat exchanger, an outdoor air heat exchanger, a cold water heat exchanger and a gas-liquid separator connected by a circulating pipeline assembly for circulating refrigerant medium, the circulating pipeline assembly comprises: an output pipe arranged at the liquid discharge side of the hot water heat exchanger; a first input pipe arranged at the first connection end of the hot water heat exchanger and connected with the output pipe; a second input pipe arranged at the second connection end of the hot water heat exchanger; and a third input pipe, one end of which is connected with the first input pipe and the other end of which is connected with the second input pipe; wherein a first pipeline assembly arranged at the liquid side of the outdoor air heat exchanger is connected with a second pipeline assembly composed of the first input pipe and the output pipe, a third pipeline assembly composed of the second input pipe and the third input pipe, and a first connecting pipe arranged between the cold water heat exchanger and the gas-liquid separator.

[0006] Compared with the prior art, the technical effects achieved by the technical scheme are: the first pipeline assembly is communicated with the second pipeline assembly and the third pipeline assembly, so that after the heat pump system is filled with the required amount of refrigerant in the refrigeration main mode, the excess refrigerant medium can be stored in the stopped warm water heat exchanger in the refrigeration mode, the excess refrigerant medium can be stored in the stopped cold water heat exchanger in the heating mode, and the excess refrigerant medium can be stored in the gas-liquid separator in the heating main mode, thereby avoiding the situation that the refrigerant medium in the heat pump system is too large in supercooling degree, the condensation temperature of the refrigerant medium is increased, and the heat exchange effect of the heat pump system is improved.

[0007] In an example of the present application, the first pipeline assembly includes a first branch pipe arranged between the outdoor heat exchanger and the second pipeline assembly, and a second branch pipe arranged between the second pipeline assembly and the third pipeline assembly, and the heat pump system further includes: a tee pipe a arranged at the connection between the third pipeline assembly and the second pipeline assembly to communicate the second branch pipe, the second input pipe and the third input pipe; a switching valve a arranged in the second branch pipe; wherein when the switching valve a is in an open state, the third pipeline assembly is communicated with the second pipeline assembly, and when the switching valve a is in a closed state, the communication between the third pipeline assembly and the second pipeline assembly is closed.

[0008] Compared with the prior art, the technical effects achieved by the technical scheme are: the open and closed states of the switching valve a are controlled to accurately control the flow direction of the refrigerant medium in the second branch pipe when the heat pump system executes the refrigeration main mode, the refrigeration mode, the heating mode and the heating main mode, thereby improving the heat exchange effect of the heat pump system.

[0009] In an example of the present application, the first pipeline assembly further includes a third branch pipe, and the heat pump system further includes: a switching valve b arranged at one end of the second input pipe close to the tee pipe a; a switching valve c arranged at one end of the second input pipe close to the first input pipe; wherein the third branch pipe is arranged between the switching valve b and the switching valve c, and when the switching valve b is in an open state and the switching valve c is in a closed state, the third branch pipe is used to communicate the first connecting pipe with the second input pipe; and when the switching valve b is in a closed state and the switching valve c is in an open state, the third branch pipe is used to communicate the first connecting pipe with the third input pipe.

[0010] Compared with the prior art, the technical effects achieved by the technical scheme are: the open and closed states of the switching valve b and the switching valve c are controlled to switch the flow direction of the refrigerant medium between the first connecting pipe and the second input pipe or the third input pipe, unnecessary refrigerant circulation of the refrigerant medium is avoided, the energy consumption of the heat pump system is reduced, and the heat exchange effect of the heat pump system is improved.

[0011] In an example of the present application, the circulating pipeline further comprises: a second connecting pipe for connecting the exhaust end of the compressor with the hot water heat exchanger; a fourth pipeline assembly arranged at the gas side of the outdoor air heat exchanger, and the fourth pipeline assembly is communicated with the second connecting pipe through a three-way pipe b; a switching valve d arranged between the second connecting pipe and the three-way pipe b; a switching valve e arranged between the outdoor air heat exchanger and the three-way pipe b; wherein, when the switching valve d is in an open state and the switching valve e is in a closed state, the compressor is communicated with the hot water heat exchanger; when the switching valve d is in a closed state and the switching valve e is in an open state, the compressor is communicated with the outdoor air heat exchanger; when the switching valve d and the switching valve e are both in an open state, the compressor is communicated with the hot water heat exchanger and the outdoor air heat exchanger respectively.

[0012] Compared with the prior art, the technical effects achieved by adopting the technical scheme are: by controlling the open and closed states of the switching valve d and the switching valve e, the flow direction of the refrigerant medium flowing through the compressor, the hot water heat exchanger and the outdoor air heat exchanger is switched when the heat pump system operates in different modes, thereby improving the energy utilization efficiency of the heat pump system.

[0013] In an example of the present application, the first pipeline assembly further comprises a fourth branch pipe, one end of the fourth branch pipe is communicated between the switching valve e and the outdoor air heat exchanger, and the other end is connected with the third branch pipe and the first connecting pipe through a four-way valve b, and the circulating pipeline further comprises: a switching valve f arranged in the fourth branch pipe; a switching valve g arranged at one end of the first connecting pipe close to the cold water heat exchanger; wherein, when the switching valve f is in an open state, the outdoor air heat exchanger is communicated with the gas-liquid separator, and when the switching valve f is in a closed state, the communication between the outdoor air heat exchanger and the gas-liquid separator is closed; when the switching valve g is in an open state, the cold water heat exchanger is communicated with the gas-liquid separator, and when the switching valve g is in a closed state, the communication between the cold water heat exchanger and the gas-liquid separator is closed.

[0014] Compared with the prior art, the technical effects achieved by adopting the technical scheme are: by controlling the open and closed states of the switching valve f and the switching valve g, the communication between the gas-liquid separator and the outdoor air heat exchanger or the cold water heat exchanger is adjusted, so as to ensure that the gas and the liquid can be effectively separated in the heating mode, the cooling mode, the heating main mode or the cooling main mode, and the situation that the liquid enters the compressor and causes damage to the compressor is avoided, thereby prolonging the service life of the compressor.

[0015] In an example of the present application, the first pipe assembly and the second pipe assembly are communicated by a four-way valve a, and the heat pump system further comprises: a first expansion valve arranged in the first branch pipe; a switching valve h arranged in the first branch pipe and connected in parallel with the first expansion valve; a second expansion valve arranged in the first input pipe close to one end of the four-way valve a; and a switching valve i arranged in the output pipe close to one end of the four-way valve a; wherein when any one of the first expansion valve and the switching valve h is in an open state, the liquid side of the outdoor heat exchanger is communicated with the first pipe assembly.

[0016] Compared with the prior art, the technical effects achieved by the technical scheme are: the first expansion valve and the second expansion valve are arranged to regulate the flow of the liquid refrigerant medium, so as to prevent the liquid refrigerant medium from entering the compressor, thereby avoiding the liquid hammer phenomenon and prolonging the service life of the compressor.

[0017] On the other hand, the present application also provides a control method of a heat pump system, the control method being used for controlling the heat pump system according to any one of the technical schemes above, and the control method comprising: acquiring a refrigerant parameter of a refrigerant medium during operation of the heat pump system in a user set mode; judging whether the refrigerant medium is in a supercooling state according to the refrigerant parameter; and controlling the heat pump system to enter a refrigerant recovery mode if the refrigerant medium is in the supercooling state; wherein the user set mode comprises a heating mode, a heating main mode and a cooling mode.

[0018] Compared with the prior art, the technical effects achieved by the technical scheme are: the refrigerant parameter of the refrigerant medium is monitored, so that the state of the refrigerant medium in the system can be known in real time, the instability of the system caused by the supercooling of the refrigerant medium is avoided, and the heat pump system is controlled to enter the refrigerant recovery mode when the refrigerant medium is detected to be in the supercooling state, so that the situation that the refrigerant medium in the heat pump system is too supercooled to cause the condensation temperature of the refrigerant medium to rise is avoided, and the heat exchange effect of the heat pump system is improved.

[0019] In an example of the present application, the refrigerant parameter comprises a first temperature when the refrigerant medium flows through the four-way valve a and a first pressure of the discharge side of the compressor; and judging whether the refrigerant medium is in a supercooling state according to the refrigerant parameter comprises: acquiring a saturation temperature of the refrigerant medium at the first pressure; acquiring a supercooling degree of the refrigerant medium according to the first temperature and the saturation temperature; and regulating the circulating pipe according to the supercooling degree to make the heat pump system enter the refrigerant recovery mode.

[0020] Compared with the prior art, the technical effects achieved by adopting the technical scheme are: the scheme judges whether the refrigerant medium is in a supercooling state by the first temperature of the refrigerant medium flowing through the four-way valve a, the first pressure of the exhaust side of the compressor, and the saturation temperature of the refrigerant medium at the first pressure, thereby improving the accuracy of the supercooling degree judgment result of the refrigerant medium.

[0021] In an example of the present application, when the user sets the mode to the cooling mode, the first expansion valve, the switching valve c, the switching valve d, the switching valve f and the switching valve i are all in the closed state, and the second expansion valve, the switching valve e, the switching valve g and the switching valve h are all in the open state; the circulating pipeline is regulated according to the supercooling degree, comprising:

[0022] When A

[0023] When A

[0024] When A1

[0025] Wherein, A is the supercooling degree, A1 and A2 are preset values, and A1

[0026] Compared with the prior art, the technical effects achieved by adopting the technical scheme are: in the cooling mode, the scheme precisely controls the flow direction of the refrigerant medium according to the supercooling degree of the refrigerant medium, avoids the excessive refrigerant medium remaining in the outdoor heat exchanger, and prevents the refrigerant medium from having too large supercooling degree and causing the condensation temperature of the refrigerant medium to rise, thereby further improving the heat exchange effect of the heat pump system in the cooling mode.

[0027] In an example of the present application, when the user sets the mode to the heating mode, the switching valve d, the first expansion valve and the switching valve f are all in the open state, and the switching valve a, the switching valve b, the switching valve e, the switching valve g, the switching valve h and the switching valve i are all in the closed state; the circulating pipeline is regulated according to the supercooling degree, comprising:

[0028] When A

[0029] When A

[0030] When A3

[0031] Wherein, A is the supercooling degree, A3 and A4 are preset values, and A3

[0032] Compared with the prior art, the technical effects achieved by adopting the technical scheme are as follows: in the heating mode, the flow direction of the refrigerant medium is accurately controlled according to the supercooling degree of the refrigerant medium, so that the excessive refrigerant medium is prevented from being retained in the hot water heat exchanger, and the heat exchange effect of the heat pump system in the heating mode is further improved.

[0033] In an example of the present application, when the user sets the mode to the heating main mode, the first expansion valve, the second expansion valve, the switching valve d, the switching valve f, the switching valve g and the switching valve i are all in the open state, and the switching valve a, the switching valve c, the switching valve e and the switching valve h are all in the closed state; the circulating pipeline is regulated according to the supercooling degree, comprising:

[0034] When A < A5, the switching valve b is controlled to be closed;

[0035] When A > A6, the switching valve b is controlled to be opened;

[0036] Wherein, A is the supercooling degree, A5 and A6 are preset values, and A5 < A6.

[0037] Compared with the prior art, the technical effects achieved by adopting the technical scheme are as follows: in the heating main mode, the flow direction of the refrigerant medium is accurately controlled according to the supercooling degree of the refrigerant medium, so that the excessive refrigerant medium is prevented from being retained in the hot water heat exchanger, and the heat exchange effect of the heat pump system in the heating main mode is further improved.

[0038] After adopting the technical scheme of the present application, the following technical effects can be achieved:

[0039] (1) The heat pump system provided by the present application is communicated by the first pipeline assembly, the second pipeline assembly and the third pipeline assembly, so that after the heat pump system is filled with the required amount of refrigerant in the refrigeration main mode, the excessive refrigerant medium can be stored in the stopped hot water heat exchanger in the refrigeration mode, the excessive refrigerant medium can be stored in the stopped cold water heat exchanger in the heating mode, and the excessive refrigerant medium can be stored in the gas-liquid separator in the heating main mode, thereby avoiding the situation that the supercooling degree of the refrigerant medium in the heat pump system is too large, the condensation temperature of the refrigerant medium is increased, and the heat exchange effect of the heat pump system is improved.

[0040] (2) The control method for the heat pump system can monitor the refrigerant parameters of the refrigerant medium in real time, so as to understand the state of the refrigerant medium in the system, avoid the situation that the system is unstable due to the overcooling of the refrigerant medium, and control the heat pump system to enter the refrigerant recovery mode when the refrigerant medium is in the overcooling state, thereby avoiding the situation that the supercooling degree of the refrigerant medium in the heat pump system is too large, the condensation temperature of the refrigerant medium is increased, and the heat exchange effect of the heat pump system is improved. Attached Figure Description

[0041] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings to be used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0042] Figure 1 This is a schematic diagram of the structure of a heat pump device provided in an embodiment of the present invention;

[0043] Figure 2 A schematic diagram of the refrigerant in the main cooling mode of a heat pump device provided in an embodiment of the present invention;

[0044] Figure 3 One of the schematic diagrams of the refrigerant in the cooling mode of a heat pump device provided in an embodiment of the present invention;

[0045] Figure 4 A second schematic diagram of the refrigerant in the cooling mode of a heat pump device provided in an embodiment of the present invention;

[0046] Figure 5 A third schematic diagram of the refrigerant in the cooling mode of a heat pump device provided in an embodiment of the present invention;

[0047] Figure 6 One of the schematic diagrams of the refrigerant in the heating mode of a heat pump device provided in an embodiment of the present invention;

[0048] Figure 7 A second schematic diagram of the refrigerant in the heating mode of a heat pump device provided in an embodiment of the present invention;

[0049] Figure 8 A third schematic diagram of the refrigerant in the heating mode of a heat pump device provided in an embodiment of the present invention;

[0050] Figure 9 One of the refrigerant schematic diagrams of a heat pump device in heating mode provided by an embodiment of the present invention;

[0051] Figure 10 This is a second schematic diagram of the refrigerant in the main heating mode of a heat pump device provided in an embodiment of the present invention.

[0052] Explanation of reference numerals in the attached figures:

[0053] 100, compressor; 110, first pressure sensor; 200, hot water heat exchanger; 210, second connection end; 220, second water inlet; 230, second water outlet; 240, hot water temperature sensor; 300, outdoor air heat exchanger; 400, cold water heat exchanger; 410, first connection end; 420, first connection pipe; 421, switching valve g; 430, second connection pipe; 431, three-way pipe b; 432, switching valve d; 440, first water inlet; 450, first water outlet; 460, cold water temperature sensor; 500, gas-liquid separator; 510, second pressure sensor; 520, second temperature sensor; 600, first pipe assembly; 610, first branch pipe; 611, three-way pipe a; 612, first expansion valve; 613, switching valve h; 620, second branch pipe; 621, switching valve a; 630, third branch pipe; 640, fourth branch pipe; 641, switching valve f; 650, four-way valve a; 660, four-way valve b; 700, second pipe assembly; 710, output pipe; 711, switching valve i; 720, first input pipe; 721, second expansion valve; 730, first temperature sensor; 800, third pipe assembly; 810, second input pipe; 820, third input pipe; 821, switching valve b; 822, switching valve c; 900, fourth pipe assembly; 910, switching valve e. DETAILED DESCRIPTION

[0054] In order to make the above objectives, features and advantages of the present application more obvious and easy to understand, the specific embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0055] The technical problem solved by the present application is that in the existing heat pump system, the maximum amount of refrigerant medium (here, referring to volume L instead of flow kg / s) is in the refrigeration main mode, and after filling the refrigerant amount into the heat pump system, in other refrigeration modes, heating modes, and heating main modes, the excess refrigerant is retained in the condenser, causing the refrigerant medium to be too large in supercooling degree, causing the refrigerant medium condensing temperature to rise, thereby affecting the heat exchange effect of the heat pump system.

[0056] To solve the above problems, on the one hand, as Figures 1 to 10As shown, the present invention provides a heat pump device, which includes a compressor 100, a hot water heat exchanger 200, an outdoor air heat exchanger 300, a cold water heat exchanger 400, and a gas-liquid separator 500 connected by a circulation pipeline assembly through which a cooling medium flows. The circulation pipeline assembly includes an output pipe 710, a first input pipe 720, a second input pipe 810, and a third input pipe 820. The output pipe 710 is located on the drain side of the hot water heat exchanger 200, the first input pipe 720 is located on the first connection end 410 of the hot water heat exchanger 200 and is connected to the output pipe 710, the second input pipe 810 is located on the second connection end 210 of the hot water heat exchanger 200, one end of the third input pipe 820 is connected to the first input pipe 720 and the other end is connected to the second input pipe 810, and the first pipeline assembly 600 located on the liquid side of the external gas heat exchanger 300 is connected to the second pipeline assembly 700 composed of the first input pipe 720 and the output pipe 710, the third pipeline assembly 800 composed of the second input pipe 810 and the third input pipe 820, and the first connection pipe 420 located between the cold water heat exchanger 400 and the gas-liquid separator 500.

[0057] This solution connects the first piping assembly 600 with the second piping assembly 700 and the third piping assembly 800, allowing the heat pump device to be filled with the required amount of refrigerant in the main cooling mode. In cooling mode, excess refrigerant can be stored in the stopped warm water heat exchanger; in heating mode, excess refrigerant can be stored in the stopped cold water heat exchanger 400; and in the main heating mode, excess refrigerant can be stored in the gas-liquid separator 500. This avoids excessive supercooling of the refrigerant in the heat pump device, which would cause the condensation temperature of the refrigerant to rise, thereby improving the heat exchange efficiency of the heat pump device.

[0058] Furthermore, such as Figure 1 As shown, the first piping assembly 600 includes a first branch pipe 610 disposed between the external air heat exchanger 300 and the second piping assembly 700, and a second branch pipe 620 disposed between the second piping assembly 700 and the third piping assembly 800. The heat pump device also includes a tee pipe a611 and a switching valve a621. The tee pipe a611 is disposed at the connection between the third piping assembly 800 and the second piping assembly 700 to connect the second branch pipe 620, the second input pipe 810, and the third input pipe 820. The switching valve a621 is disposed on the second branch pipe 620, and when the switching valve a621 is in the open state, the third piping assembly 800 is connected to the second piping assembly 700; when the switching valve a621 is in the closed state, the connection between the third piping assembly 800 and the second piping assembly 700 is closed.

[0059] The scheme controls the opening and closing state of the switching valve a621 to accurately control the flow direction of the refrigerant medium in the second branch pipe 620 when the heat pump device is executing the refrigeration main mode, the refrigeration mode, the heating mode and the heating main mode, thereby improving the heat exchange effect of the heat pump device.

[0060] Further, as shown in Figure 1 The first pipeline assembly 600 further includes a third branch pipe 630, and the heat pump device further includes a switching valve b821 and a switching valve c822. The switching valve b821 is arranged at one end of the second input pipe 810 close to the three-way pipe a611, the switching valve c822 is arranged at one end of the second input pipe 810 close to the first input pipe 720, the third branch pipe 630 is arranged between the switching valve b821 and the switching valve c822, and when the switching valve b821 is in an open state and the switching valve c822 is in a closed state, the third branch pipe 630 is used to connect the first connecting pipe 420 and the second input pipe 810; when the switching valve b821 is in a closed state and the switching valve c822 is in an open state, the third branch pipe 630 is used to connect the first connecting pipe 420 and the third input pipe 820.

[0061] The opening and closing state of the switching valve b821 and the switching valve c822 is used to switch the flow direction of the refrigerant medium between the first connecting pipe 420 and the second input pipe 810 or the third input pipe 820, which avoids unnecessary refrigerant circulation of the refrigerant medium, thereby reducing the energy consumption of the heat pump device and improving the heat exchange effect of the heat pump device.

[0062] Further, as shown in Figure 1 The circulating pipeline further includes a second connecting pipe 430, a fourth pipeline assembly 900, a switching valve d432 and a switching valve e910. Specifically, the second connecting pipe 430 is used to connect the exhaust end of the compressor 100 and the hot water heat exchanger 200, the fourth pipeline assembly 900 is arranged at the air side of the outdoor air heat exchanger 300, the fourth pipeline assembly 900 and the second connecting pipe 430 are connected through a three-way pipe b431, the switching valve d432 is arranged between the second connecting pipe 430 and the three-way pipe b431, and the switching valve e910 is arranged between the outdoor air heat exchanger 300 and the three-way pipe b431; when the switching valve d432 is in an open state and the switching valve e910 is in a closed state, the compressor 100 and the hot water heat exchanger 200 are connected; when the switching valve d432 is in a closed state and the switching valve e910 is in an open state, the compressor 100 and the outdoor air heat exchanger 300 are connected; when the switching valve d432 and the switching valve e910 are both in an open state, the compressor 100 is connected with the hot water heat exchanger 200 and the outdoor air heat exchanger 300 respectively.

[0063] The present scheme controls the opening and closing states of the switching valve d432 and the switching valve e910 to switch the flow direction of the refrigerant medium flowing through the compressor 100, the hot water heat exchanger 200, and the outdoor air heat exchanger 300 when the heat pump device operates in different modes, thereby improving the energy utilization efficiency of the heat pump device.

[0064] Further, as shown in Figure 1 The first pipeline assembly 600 and the second pipeline assembly 700 are connected by the four-way valve a650, and the heat pump device further comprises a first expansion valve 612, a second expansion valve 721, a switching valve h613, and a switching valve i711. Specifically, the first expansion valve 612 is arranged in the first branch pipe 610, the switching valve h613 is arranged in the first branch pipe 610, and the switching valve h613 is connected in parallel with the first expansion valve 612, the second expansion valve 721 is arranged at one end of the first input pipe 720 close to the four-way valve a650, and the switching valve i711 is arranged at one end of the output pipe 710 close to the four-way valve a650; wherein when any one of the first expansion valve 612 and the switching valve h613 is in an open state, the liquid side of the outdoor air heat exchanger 300 is connected with the first pipeline assembly 600.

[0065] The present scheme controls the opening and closing states of the switching valve f641 and the switching valve g421 to adjust the connection of the gas-liquid separator 500 with the outdoor air heat exchanger 300 or the cold water heat exchanger 400, so as to ensure effective separation of gas and liquid in the heating mode, the cooling mode, the heating main mode or the cooling main mode, thereby avoiding the situation that liquid enters the compressor 100 and causes damage to the compressor 100, thereby prolonging the service life of the compressor 100.

[0066] Further, as shown in Figure 1 The first pipeline assembly 600 and the second pipeline assembly 700 are connected by the four-way valve a650, and the heat pump device further comprises a first expansion valve 612, a second expansion valve 721, a switching valve h613, and a switching valve i711. Specifically, the first expansion valve 612 is arranged in the first branch pipe 610, the switching valve h613 is arranged in the first branch pipe 610, and the switching valve h613 is connected in parallel with the first expansion valve 612, the second expansion valve 721 is arranged at one end of the first input pipe 720 close to the four-way valve a650, and the switching valve i711 is arranged at one end of the output pipe 710 close to the four-way valve a650; wherein when any one of the first expansion valve 612 and the switching valve h613 is in an open state, the liquid side of the outdoor air heat exchanger 300 is connected with the first pipeline assembly 600.

[0067] The first expansion valve 612 and the second expansion valve 721 are arranged to regulate the flow of the liquid refrigerant medium, prevent the liquid refrigerant medium from entering the compressor 100, avoid the liquid hammer phenomenon, and prolong the service life of the compressor 100.

[0068] Further, as shown in Figure 1 The first pressure sensor 110 is arranged at the exhaust side of the compressor 100 to detect the first pressure at the exhaust side of the compressor 100, and the first temperature sensor 730 is arranged at the connection between the first pipeline assembly 600 and the second pipeline assembly 700 to detect the first temperature of the refrigerant medium flowing through the four-way valve a 650.

[0069] Further, as shown in Figure 1 Further, as shown in The second pressure sensor 510 and the second temperature sensor 520 are arranged at one end of the first connecting pipe 420 close to the liquid-gas separator to detect the second temperature and the second pressure of the refrigerant medium before entering the liquid-gas separator. Specifically, the second pressure sensor 510 and the second temperature sensor 520 are in communication connection with the first expansion valve 612 and the second expansion valve 721, so as to adjust the superheat degree of the heat pump device by adjusting the opening degree of the second expansion valve 721 during the execution of the refrigeration mode, the refrigeration main mode or the heating main mode of the heat pump device, and adjust the superheat degree of the heat pump device by adjusting the opening degree of the first expansion valve 612 during the execution of the heating mode of the heat pump device.

[0070] Figure 1 Further, as shown in The first water inlet 440 and the first water outlet 450 are arranged on the cold water heat exchanger 400, and the cold water temperature sensor 460 is arranged at the first water outlet 450. The cold water temperature sensor 460 is in communication connection with the compressor 100 and the first expansion valve 612, so as to adjust the measured value of the cold water temperature sensor 460 to the first preset value set by the user by adjusting the rotating speed of the compressor 100 during the execution of the refrigeration mode and the refrigeration main mode of the heat pump device, and adjust the measured value of the cold water temperature sensor 460 to the second preset value set by the user by adjusting the opening degree of the first expansion valve 612 during the execution of the heating main mode of the heat pump device.

[0071] Figure 1As shown, the hot water heat exchanger 200 is provided with a second water inlet 220 and a second water outlet 230, and a hot water temperature sensor 240 is arranged at the second water outlet 230, which is in communication connection with the compressor 100 and the first expansion valve 612, so that in the process of operating the heat pump device in the heating mode and the main heating mode, the user adjusts the rotating speed of the compressor 100 to make the measured value of the hot water temperature sensor 240 reach the third preset value set by the user; in the process of operating the heat pump device in the main cooling mode, the user adjusts the opening degree of the first expansion valve 612 to make the measured value of the hot water temperature sensor 240 reach the fourth preset value set by the user.

[0072] In another aspect, the application also provides a control method of a heat pump device, the control method being used for controlling the heat pump device according to any one of the above technical solutions, and the control method comprising: acquiring a refrigerant parameter of a refrigerant medium in the process of operating the heat pump device according to a user set mode; judging whether the refrigerant medium is in a supercooling state according to the refrigerant parameter; and controlling the heat pump device to enter a refrigerant recovery mode if the refrigerant medium is in the supercooling state; wherein the user set mode comprises a heating mode, a main heating mode and a cooling mode.

[0073] The present application can realize real-time understanding of the state of the refrigerant medium in the system by monitoring the refrigerant parameter of the refrigerant medium, avoids the situation that the system is unstable due to the supercooling of the refrigerant medium, and controls the heat pump device to enter the refrigerant recovery mode when it is detected that the refrigerant medium is in the supercooling state, thereby avoiding the situation that the supercooling degree of the refrigerant medium in the heat pump device is too large, the condensation temperature of the refrigerant medium rises, and the heat exchange effect of the heat pump device is improved.

[0074] Further, the refrigerant parameter comprises a first temperature when the refrigerant medium flows through a four-way valve a 650 and a first pressure of an exhaust side of the compressor 100; the judgment of whether the refrigerant medium is in the supercooling state according to the refrigerant parameter comprises: acquiring a saturation temperature of the refrigerant medium at the first pressure; acquiring a supercooling degree of the refrigerant medium according to the first temperature and the saturation temperature; and regulating the circulating pipeline according to the supercooling degree to make the heat pump device enter the refrigerant recovery mode.

[0075] The present application judges whether the refrigerant medium is in the supercooling state by the first temperature when the refrigerant medium flows through the four-way valve a 650, the first pressure of the exhaust side of the compressor 100 and the saturation temperature of the refrigerant medium at the first pressure, thereby improving the accuracy of the judgment result of the supercooling degree of the refrigerant medium.

[0076] As Figure 2As shown, when the user sets the mode to the refrigeration main body mode, the first expansion valve 612, the second expansion valve 721, the switching valve d 432, the switching valve e 910, the switching valve g 421 and the switching valve i 711 are all in the open state; the switching valve a 621, the switching valve b 821, the switching valve c 822, the switching valve f 641 and the switching valve h 613 are all in the closed state, at this time the heat pump device does not perform the supercooling degree control.

[0077] Further, as shown in the figure, Figures 3 to 5 As shown, when the user sets the mode to the refrigeration mode, the first expansion valve 612, the switching valve c 822, the switching valve d 432, the switching valve f 641 and the switching valve i 711 are all in the closed state, the second expansion valve 721, the switching valve e 910, the switching valve g 421 and the switching valve h 613 are all in the open state; according to the supercooling degree, the circulating pipeline is regulated and controlled, including:

[0078] When A < A1, the switching valve b 821 is controlled to be opened, and the switching valve a 621 is controlled to be closed;

[0079] When A > A2, the switching valve b 821 is controlled to be closed, and the switching valve a 621 is controlled to be opened;

[0080] When A1≤A≤A2, the switching valve b 821 and the switching valve a 621 are controlled to be closed;

[0081] Wherein, A is the supercooling degree, A1, A2 are preset values, and A1 < A2.

[0082] It should be noted that when A > A2, the switching valve b 821 is controlled to be closed, and the switching valve a 621 is controlled to be opened, at this time, the refrigerant medium flows from the circulating pipeline assembly to the stopped hot water heat exchanger 200 for temporary storage, when A < A1, the switching valve b 821 is controlled to be opened, and the switching valve a 621 is controlled to be closed, at this time, the refrigerant medium flows from the stopped hot water heat exchanger 200 to the circulating pipeline assembly for heat exchange, when A1≤A≤A2, the switching valve b 821 and the switching valve a 621 are controlled to be closed, at this time, the communication between the stopped hot water heat exchanger 200 and the circulating pipeline assembly is closed, so that the refrigerant medium completely participates in the heat exchange work in the circulating pipeline assembly.

[0083] In the refrigeration mode, the flow direction of the refrigerant medium is accurately controlled according to the supercooling degree of the refrigerant medium, which avoids the excessive refrigerant medium remaining in the outdoor heat exchanger 300, causing the refrigerant medium to have too much supercooling degree, and the refrigerant medium condensation temperature rises, thereby further improving the heat exchange effect of the heat pump device in the refrigeration mode.

[0084] Further, as shown in the figure, Figures 6 to 8As shown, when the user sets the mode to the heating mode, the switching valve d432, the first expansion valve 612 and the switching valve f641 are all in the open state, the switching valve a621, the switching valve b821, the switching valve e910, the switching valve g421, the switching valve h613 and the switching valve i711 are all in the closed state; the circulating pipeline is regulated according to the supercooling degree, including:

[0085] When A < A3, the second expansion valve 721 is controlled to be closed, and the switching valve c822 is controlled to be opened;

[0086] When A > A4, the second expansion valve 721 is controlled to be opened, and the switching valve c822 is controlled to be closed;

[0087] When A3≤A≤A4, the second expansion valve 721 and the switching valve c822 are controlled to be closed;

[0088] Wherein, A is the supercooling degree, A3, A4 are preset values, and A3 < A4.

[0089] It should be noted that when A > A4, the second expansion valve 721 is controlled to be opened, and the switching valve c822 is controlled to be closed, at this time, the refrigerant medium flows from the circulating pipeline assembly to the stopped cold water heat exchanger 400 for temporary storage, when A < A3, the second expansion valve 721 is controlled to be closed, and the switching valve c822 is controlled to be opened, at this time, the refrigerant medium flows from the stopped cold water heat exchanger 400 to the circulating pipeline assembly for heat exchange, when A3≤A≤A4, the second expansion valve 721 and the switching valve c822 are controlled to be closed, at this time, the communication between the stopped hot water heat exchanger 400 and the circulating pipeline assembly is closed, so that all the refrigerant medium participates in the heat exchange work in the circulating pipeline assembly.

[0090] In the heating mode, the flow direction of the refrigerant medium is accurately controlled according to the supercooling degree of the refrigerant medium, which avoids the excessive refrigerant medium remaining in the hot water heat exchanger 200, thereby further improving the heat exchange effect of the heat pump device in the heating mode.

[0091] Further, as shown in Figure 9 and Figure 10 As shown, when the user sets the mode to the heating mode, the switching valve d432, the first expansion valve 612 and the switching valve f641 are all in the open state, the switching valve a621, the switching valve b821, the switching valve e910, the switching valve g421, the switching valve h613 and the switching valve i711 are all in the closed state; the circulating pipeline is regulated according to the supercooling degree, including:

[0092] When A < A5, the switching valve b821 is controlled to be closed;

[0093] When A>A6, the switching valve b821 is controlled to be opened.

[0094] A is the supercooling degree, A5 and A6 are preset values, and A5

[0095] It should be noted that when A>A6, the switching valve b821 is controlled to be opened, at this time, the refrigerant medium flows from the circulating pipeline assembly to the gas-liquid separator 500 for temporary storage, and when A

[0096] In the heating main mode, the flow direction of the refrigerant medium is accurately controlled according to the supercooling degree of the refrigerant medium, so that the excessive refrigerant medium is avoided to be retained in the hot water heat exchanger 200, thereby further improving the heat exchange effect of the heat pump device in the heating main mode.

[0097] Although the present application is disclosed as above, the present application is not limited to this. Any person skilled in the art can make various changes and modifications without departing from the spirit and scope of the present application, and the protection scope of the present application should be limited by the scope defined by the claims.

Claims

1. A heat pump system, characterized by, The heat pump system comprises a compressor (100), a hot water heat exchanger (200), an outdoor air heat exchanger (300), a cold water heat exchanger (400), a gas-liquid separator (500) connected by a circulating pipeline assembly for circulating a refrigerant medium, and the circulating pipeline assembly comprises: an output pipe (710) arranged at a liquid discharge side of the hot water heat exchanger (200); a first input pipe (720) arranged at a first connecting end (410) of the cold water heat exchanger (400), and the first input pipe (720) is in communication with the output pipe (710); a second input pipe (810) arranged at a second connecting end (210) of the hot water heat exchanger (200); a third input pipe (820) having one end in communication with the first input pipe (720) and the other end in communication with the second input pipe (810); wherein a first pipeline assembly (600) arranged at a liquid side of the outdoor air heat exchanger (300) is in communication with a second pipeline assembly (700) composed of the first input pipe (720) and the output pipe (710), a third pipeline assembly (800) composed of the second input pipe (810) and the third input pipe (820), and a first connecting pipe (420) arranged between the cold water heat exchanger (400) and the gas-liquid separator (500).

2. The heat pump system of claim 1, wherein, The first pipeline assembly (600) comprises a first branch pipe (610) arranged between the outdoor air heat exchanger (300) and the second pipeline assembly (700), and a second branch pipe (620) arranged between the second pipeline assembly (700) and the third pipeline assembly (800), and the heat pump system further comprises: a three-way pipe a (611) arranged at a connection between the third pipeline assembly (800) and the second pipeline assembly (700) to connect the second branch pipe (620), the second input pipe (810) and the third input pipe (820); a switching valve a (621) arranged at the second branch pipe (620); wherein when the switching valve a (621) is in an open state, the third pipeline assembly (800) is in communication with the second pipeline assembly (700), and when the switching valve a (621) is in a closed state, the communication between the third pipeline assembly (800) and the second pipeline assembly (700) is closed.

3. The heat pump system of claim 2, wherein, The first pipeline assembly (600) further comprises a third branch pipe (630), and the heat pump system further comprises: a switching valve b (821) arranged at one end of the second input pipe (810) close to the three-way pipe a (611); a switching valve c (822) arranged at one end of the second input pipe (810) close to the first input pipe (720); The third branch pipe (630) is arranged between the switching valve b (821) and the switching valve c (822), and when the switching valve b (821) is in the open state and the switching valve c (822) is in the closed state, the third branch pipe (630) is used for connecting the first connecting pipe (420) and the second input pipe (810); when the switching valve b (821) is in the closed state and the switching valve c (822) is in the open state, the third branch pipe (630) is used for connecting the first connecting pipe (420) and the third input pipe (820).

4. The heat pump system of claim 3, wherein, The circulating pipeline further comprises: A second connecting pipe (430) is used for connecting the exhaust end of the compressor (100) and the hot water heat exchanger (200); A fourth pipeline assembly (900) is arranged at the air side of the outdoor air heat exchanger (300), and the fourth pipeline assembly (900) is connected with the second connecting pipe (430) through a three-way pipe b (431); A switching valve d (432) is arranged between the second connecting pipe (430) and the three-way pipe b (431); A switching valve e (910) is arranged between the outdoor air heat exchanger (300) and the three-way pipe b (431); When the switching valve d (432) is in the open state and the switching valve e (910) is in the closed state, the compressor (100) is connected with the hot water heat exchanger (200); when the switching valve d (432) is in the closed state and the switching valve e (910) is in the open state, the compressor (100) is connected with the outdoor air heat exchanger (300); when the switching valve d (432) and the switching valve e (910) are both in the open state, the compressor (100) is connected with the hot water heat exchanger (200) and the outdoor air heat exchanger (300) respectively.

5. The heat pump system of claim 4, wherein, The first pipeline assembly (600) further comprises a fourth branch pipe (640), one end of the fourth branch pipe (640) is connected between the switching valve e (910) and the outdoor air heat exchanger (300), and the other end is connected with the third branch pipe (630) and the first connecting pipe (420) through a four-way valve b (660); the circulating pipeline further comprises: A switching valve f (641) is arranged in the fourth branch pipe (640); A switching valve g (421) is arranged at one end of the first connecting pipe (420) close to the cold water heat exchanger (400); When the switching valve f (641) is in the open state, the outdoor heat exchanger (300) is in communication with the gas-liquid separator (500), and when the switching valve f (641) is in the closed state, the communication between the outdoor heat exchanger (300) and the gas-liquid separator (500) is closed; when the switching valve g (421) is in the open state, the cold water heat exchanger (400) is in communication with the gas-liquid separator (500), and when the switching valve g (421) is in the closed state, the communication between the cold water heat exchanger (400) and the gas-liquid separator (500) is closed.

6. The heat pump system of claim 3, wherein, The first pipeline assembly (600) and the second pipeline assembly (700) are in communication through a four-way valve a (650), and the heat pump system further comprises: A first expansion valve (612) is arranged in the first branch pipe (610); A switching valve h (613) is arranged in the first branch pipe (610), and the switching valve h (613) is connected in parallel with the first expansion valve (612); A second expansion valve (721) is arranged at one end of the first input pipe (720) close to the four-way valve a (650); A switching valve i (711) is arranged at one end of the output pipe (710) close to the four-way valve a (650); When any one of the first expansion valve (612) and the switching valve h (613) is in the open state, the liquid side of the outdoor heat exchanger (300) is in communication with the first pipeline assembly (600).

7. A control method of a heat pump system, characterized by, The control method is used for controlling the heat pump system according to any one of claims 1 to 6, and the control method comprises: During operation of the heat pump system in a user set mode, a refrigerant parameter of the refrigerant medium is obtained; According to the refrigerant parameter, it is judged whether the refrigerant medium is in a supercooling state; If the refrigerant medium is in the supercooling state, the heat pump system is controlled to enter a refrigerant recovery mode; The user set mode includes a heating mode, a heating main mode and a refrigeration mode.

8. The control method according to claim 7, characterized by, The refrigerant parameter includes a first temperature of the refrigerant medium flowing through the four-way valve a (650) and a first pressure of the exhaust side of the compressor (100); according to the refrigerant parameter, it is judged whether the refrigerant medium is in a supercooling state, which comprises: The saturation temperature of the refrigerant medium at the first pressure is obtained; According to the first temperature and the saturation temperature, the supercooling degree of the refrigerant medium is obtained; According to the supercooling degree, the circulating pipeline is regulated to make the heat pump system enter the refrigerant recovery mode.

9. The control method according to claim 8, characterized by, When the user setting mode is the refrigeration mode, the first expansion valve (612), the switching valve c (822), the switching valve d (432), the switching valve f (641) and the switching valve i (711) are all in the closed state, the second expansion valve (721), the switching valve e (910), the switching valve g (421) and the switching valve h (613) are all in the open state; the regulating the circulation pipeline according to the supercooling degree comprises: When A When A When A When A 10. The control method according to claim 8, characterized by Wherein, A is the supercooling degree, A1, A2 are preset values, and A1 When the user setting mode is the heating mode, the switching valve d (432), the first expansion valve (612) and the switching valve f (641) are all in the open state, the switching valve a (621), the switching valve b (821), the switching valve e (910), the switching valve g (421), the switching valve h (613) and the switching valve i (711) are all in the closed state; the regulating the circulation pipeline according to the supercooling degree comprises: When A When A When A 11. The control method according to claim 8, characterized by, Wherein, A is the supercooling degree, A3, A4 are preset values, and A3 When the user setting mode is the heating mode, the switching valve d (432), the first expansion valve (612) and the switching valve f (641) are all in the open state, the switching valve a (621), the switching valve b (821), the switching valve e (910), the switching valve g (421), the switching valve h (613) and the switching valve i (711) are all in the closed state; the regulating the circulation pipeline according to the supercooling degree comprises: When A When A Wherein, A is the supercooling degree, A5, A6 are preset values, and A5

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