Parallel refrigeration system and refrigeration equipment
By using a liquid receiver to connect the evaporator and the compressor return port in a parallel refrigeration system, the mixing and energy exchange of the refrigerant within the liquid receiver are achieved, solving the problem of slow refrigerant migration and improving the refrigeration effect of the refrigeration evaporator and the performance of the compressor.
Patent Information
- Application Number
- CN202423013134.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-06
- Publication Date
- 2025-10-17
- Estimated Expiration
- 2034-12-06
AI Technical Summary
In parallel refrigeration systems, the refrigerant migration time is long when switching from the refrigeration evaporator to the refrigerator evaporator, resulting in insufficient refrigerant in the refrigerator evaporator, which affects the refrigeration effect and compressor performance.
The parallel refrigeration system is designed by connecting the evaporator outlet and the compressor return port through a liquid receiver. The mixing and energy exchange of the refrigerant in the liquid receiver are achieved by using jet and diversion pipes, ensuring sufficient refrigerant quantity, avoiding condensation in the return pipe, and improving compressor performance.
Accelerate refrigerant migration, ensure sufficient refrigerant in the refrigeration evaporator, prevent condensation in the return pipe, and improve compressor performance and system reliability.
Smart Images
Figure CN223448676U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model relates to refrigeration system technical field especially parallel refrigeration system and refrigeration plant. BACKGROUND
[0002] In the field of refrigeration technology, the design and optimization of refrigeration system are crucial for improving the performance of refrigeration equipment. With the increasing demand of consumers for the performance of refrigeration equipment, especially household refrigerators, the traditional single-cycle refrigeration system has been difficult to meet the market demand for independent temperature control of refrigeration and freezing compartments, prevention of odor mixing, and high efficiency and energy saving.
[0003] To address these challenges, the industry has begun to widely adopt double-cycle or multi-cycle refrigeration systems. Such systems achieve independent temperature control of refrigeration and freezing compartments by introducing independent refrigeration circuits, effectively avoiding odor mixing. Among them, series-parallel structure and pure parallel structure are two main forms of double-cycle or multi-cycle refrigeration systems.
[0004] In a series-parallel refrigeration system, although the refrigerant after throttling by the capillary tube can enter the evaporators of the refrigeration and freezing compartments in turn, the required evaporation temperature for the refrigeration compartment (5℃) is relatively high, while the required evaporation temperature for the freezing compartment (-18℃) is relatively low, resulting in a certain degree of rise in the freezing compartment evaporation temperature during refrigeration, affecting the cooling efficiency of the freezing compartment. At the same time, due to the large content volume and the need for more refrigerant, the load of the compressor increases when the series-parallel system is running, affecting the service life of the compressor and the energy consumption of the refrigerator.
[0005] In contrast, the temperature of each compartment in a parallel refrigeration system can be independently controlled, making it more flexible and energy-efficient. Generally, the refrigerant charge of a parallel refrigeration system is determined according to the refrigeration circuit with a larger content volume, i.e., the refrigerant charge is matched according to the operation of the freezing refrigeration circuit alone to ensure that the performance of the freezing refrigeration cycle reaches the best. However, due to the lower design temperature of the freezing compartment, the throttling effect of the freezing capillary tube will be designed to be greater than that of the refrigeration capillary tube, resulting in a smaller flow rate of the freezing capillary tube than that of the refrigeration capillary tube. When the freezing refrigeration circuit switches to the refrigeration refrigeration circuit, the refrigerant in the freezing evaporator will migrate to the refrigeration evaporator, which requires a long time, which may result in slow cooling speed and poor refrigeration performance of the refrigeration refrigeration circuit due to insufficient refrigerant.
[0006] Therefore, how to optimize the refrigeration performance of the parallel evaporator during switching is a technical problem that needs to be solved in the industry. SUMMARY
[0007] In order to solve the above-mentioned defects existing in the prior art, the utility model provides parallel refrigerating system and refrigerating equipment, the evaporator outlet of this parallel refrigerating system is connected with the liquid accumulator, the refrigerant of different evaporators is mixed and energy exchange is happened by using the special connection structure of the liquid accumulator, and then is sent back to the gas return port of the compressor, so as to solve the problem of insufficient refrigerant amount participating in refrigeration cycle when the evaporator switches work, avoid the condensation phenomenon of the gas return pipe, and improve the working performance of the compressor.
[0008] The utility model discloses a technical scheme is, design parallel refrigerating system, include: the compressor, condenser, throttling device and evaporator subassembly that form refrigerant circulation loop in proper order, the evaporator subassembly contains parallel first evaporator and second evaporator, the refrigeration temperature of second evaporator is lower than first evaporator. The evaporator subassembly is connected the gas return port of compressor through liquid accumulator, the liquid accumulator has the jet flow entrance, the drainage entrance and the mixed export, the jet flow entrance connects the outlet of first evaporator, the drainage entrance connects the outlet of second evaporator, and the mixed export connects the gas return port of compressor.
[0009] Further, the jet flow entrance is equipped with the jet flow pipe, the jet flow pipe has the jet flow necking section that stretches into the inner chamber of the liquid accumulator, the jet flow connecting section that is located the outside of the liquid accumulator and the jet flow intermediate section that is connected between the jet flow necking section and the jet flow connecting section, the inner diameter of the jet flow necking section is less than the inner diameter of the jet flow connecting section, and the jet flow connecting section connects the outlet of the first evaporator.
[0010] Further, the mixed export is equipped with the gas return pipe, the gas return pipe is equipped with the gas return necking section that is located in the mixed export, the gas return connecting section that is located the outside of the liquid accumulator and the gas return intermediate section that is connected between the gas return necking section and the gas return connecting section, the inner diameter of the gas return necking section is less than the inner diameter of the gas return connecting section, and the gas return connecting section connects the gas return port of the compressor.
[0011] Further, the drainage entrance is equipped with the drainage pipe, the outlet of the drainage pipe stretches into the inner chamber of the liquid accumulator and is close to the jet flow necking section, and the inlet of the drainage pipe is connected with the outlet of the second evaporator.
[0012] Further, the inner diameter of the jet flow necking section is less than the inner diameter of the gas return necking section, and the inner diameter of the drainage pipe is greater than the inner diameter of the gas return necking section.
[0013] In some embodiments, the inner diameter of the jet flow necking section is 1 / 3-1 / 4 of the inner diameter of the jet flow connecting section, the inner diameter of the gas return necking section is 1 / 2 of the inner diameter of the gas return connecting section, and the inner diameter of the drainage pipe remains consistent from the inlet to the outlet.
[0014] Further, the throttling device adopts a capillary tube, and an inner diameter of the jet flow necking section is greater than an inner diameter of the capillary tube.
[0015] Further, the parallel refrigeration system further comprises:
[0016] a first temperature sensor for detecting an actual temperature of a first chamber, and the first evaporator supplies cold to the first chamber;
[0017] a second temperature sensor for detecting an actual temperature of a second chamber, and the second evaporator supplies cold to the second chamber;
[0018] a return gas temperature sensor for detecting an actual return gas temperature of the compressor;
[0019] a controller receiving detection data of the first temperature sensor, the second temperature sensor and the return gas temperature sensor, and adjusting an operation state of the refrigerant circulation loop.
[0020] The utility model also provides a refrigeration equipment comprising the parallel refrigeration system.
[0021] In some embodiments, the refrigeration equipment is a refrigerator, the first evaporator is a refrigeration evaporator, and the second evaporator is a freezing evaporator.
[0022] Compared with the prior art, the utility model has at least one of the following beneficial effects:
[0023] 1, evaporator assembly is connected through liquid accumulator return gas port of compressor, two kinds of different pressure refrigerants produced by two evaporators enter the inner chamber of liquid accumulator from jet flow inlet and drainage inlet, are mixed and exchange energy, finally form a mixed fluid with moderate pressure to enter the mixing outlet of liquid accumulator, until return to the return gas port of compressor, avoid the condensation phenomenon of return gas pipe, improve the working performance of compressor;
[0024] 2, the actual return gas temperature of the compressor is detected by the return gas temperature sensor, and the operation state of the refrigerant circulation loop is adjusted according to the actual return gas temperature and the actual temperature of the evaporator corresponding chamber, to prevent the return gas temperature of the compressor from being too low, and ensure the reliability of the parallel refrigeration system operation. BRIEF DESCRIPTION OF DRAWINGS
[0025] The utility model will be explained in detail in combination with embodiments and drawings, in which:
[0026] Figure 1 is the connection schematic diagram of the refrigeration system of the utility model;
[0027] Figure 2 is the refrigerant flow direction schematic diagram when the first evaporator of the utility model works alone;
[0028] Figure 3 is the refrigerant flow direction schematic diagram of the second evaporator of the utility model working alone;
[0029] Figure 4 is the refrigerant flow direction schematic diagram of the two evaporators of the utility model working simultaneously;
[0030] Figure 5 is the structure schematic diagram of the liquid accumulator of the utility model;
[0031] Figure 6 is the refrigerant flow direction schematic diagram of the liquid accumulator of the utility model;
[0032] Figure 7 is the working process schematic diagram of the refrigerator of the utility model;
[0033] BRIEF DESCRIPTION OF DRAWINGS: 1, compressor; 2, condenser; 3, switching valve; 4, first capillary; 5, second capillary; 6, first evaporator; 7, second evaporator; 8, liquid accumulator; 9, drying filter; 10, anti-condensation pipe; 81, jet pipe; 811, jet necking section; 812, jet intermediate section; 813, jet connecting section; 82, return air pipe; 821, return air necking section; 822, return air intermediate section; 823, return air connecting section; 83, drainage pipe. DETAILED DESCRIPTION
[0034] In order to make the technical problems, technical solutions and beneficial effects to be solved by the utility model more clear and obvious, the utility model is further described in detail below in combination with the drawings and examples. It should be understood that the specific examples described herein are only used to explain the utility model, and are not used to limit the utility model.
[0035] The parallel refrigeration system usually determines the refrigerant filling amount according to the separate operation of the freezing evaporator. During the refrigeration operation of the parallel refrigeration system, the freezing evaporator and the refrigeration evaporator often appear switching work. When the freezing evaporator switches to the refrigeration evaporator, the refrigerant in the freezing evaporator needs a long time to migrate to the refrigeration evaporator. The refrigerant amount participating in the refrigeration cycle in the refrigeration system is insufficient, which has an influence on the refrigeration effect of the refrigeration evaporator and the working performance of the compressor. The reasons are as follows.
[0036] The refrigerant amount is insufficient to cause the refrigerating evaporator to reduce the refrigerating capacity, and the refrigerating capacity cannot meet the refrigerating requirement of the refrigerating compartment, the temperature in the compartment cannot be reduced to the set temperature range, and the use experience is affected. In addition, when the refrigerant amount is insufficient, the refrigerant amount in the refrigerating evaporator is reduced, and the heat absorption capacity is also reduced, which means that, compared with the normal refrigerant amount, the refrigerating evaporator needs a longer time or a higher temperature difference to achieve the same refrigerating effect when absorbing heat, which causes the refrigerant temperature and the refrigerant pressure flowing out of the refrigerating evaporator to be reduced, the refrigerant temperature and the refrigerant pressure sent to the return pipe are also reduced, when the refrigerant temperature in the return pipe is reduced to a certain extent, that is, lower than the dew point temperature in the air, the water vapor in the air is condensed into water droplets on the surface of the return pipe, and the condensation phenomenon is formed, and the low return pipe pressure causes the compression ratio of the compressor to be increased, and the compressor needs to consume more energy to complete the compression process, and the working performance is greatly reduced.
[0037] The parallel refrigeration system can be applied to a refrigeration device, and the refrigeration device includes but is not limited to a refrigerator.
[0038] As shown in Figures 1 to 4 The parallel refrigeration system includes a compressor 1, a condenser 2, a throttling device and an evaporator assembly connected in sequence to form a refrigerant circulation loop. The evaporator assembly includes a first evaporator 6 and a second evaporator 7 connected in parallel, the first evaporator 6 is used to cool the first compartment, and the second evaporator 7 is used to cool the second compartment, and the refrigeration temperature of the second evaporator 7 is lower than that of the first evaporator 6, that is, the refrigeration requirements of the two compartments are different. Taking a refrigerator as an example, the first evaporator 6 is a refrigerating evaporator, the first compartment is a refrigerating compartment, the second evaporator 7 is a freezing evaporator, and the second compartment is a freezing compartment, and the refrigeration temperature of the freezing evaporator is lower than that of the refrigerating evaporator, so as to provide a lower temperature environment for storing food.
[0039] In order to better match the refrigeration performance of the evaporator, the first evaporator 6 and the second evaporator 7 are each independently provided with a throttling element, and a switching valve 3 is designed between the throttling element and the condenser 2, and the switching valve 3 is used to switch the working state of the first evaporator 2 and / or the second evaporator 7. In some embodiments of the present application, the throttling device includes a first capillary tube 4 and a second capillary tube 5, the first evaporator 6 is connected to the outlet of the condenser 2 through the first capillary tube 4, and the second evaporator 7 is connected to the outlet of the condenser 2 through the second capillary tube 5.
[0040] The parallel refrigeration system determines the refrigerant filling amount according to the separate operation of the second evaporator 7, and the parallel refrigeration system is used to solve the problem that the refrigerant amount in the refrigeration system is insufficient when the second evaporator 7 is switched to the first evaporator 6.
[0041] Specifically, the evaporator assembly is connected to the return port of the compressor 1 through a liquid accumulator 8, the liquid accumulator 8 has a jet inlet, a flow inlet and a mixing outlet, the jet inlet is connected to the outlet of the first evaporator 6, the flow inlet is connected to the outlet of the second evaporator 7, and the mixing outlet is connected to the return port of the compressor 1.
[0042] When the first evaporator 6 is operated alone, a jet turbulent diffusion phenomenon is formed in the inner cavity of the liquid accumulator 8, that is, the high-temperature refrigerant running in the first evaporator 6 is used as a high-speed jet fluid, and the low-temperature refrigerant remaining in the second evaporator 7 is used as a flow fluid. The high-speed jet fluid forms a high-speed jet at the jet inlet to cause a local vacuum, so that its pressure is lower than that of the flow fluid, so that the flow fluid is automatically sucked into the liquid accumulator 8. The two refrigerants with different pressures are mixed with each other and exchange energy in the inner cavity of the liquid accumulator 8, and finally form a mixed fluid with moderate pressure into the mixing outlet of the liquid accumulator 8, and then return to the return port of the compressor 1.
[0043] The design of the liquid accumulator 8 can accelerate the migration of the refrigerant in the second evaporator 7 to the first evaporator 6, ensure the sufficient amount of refrigerant participating in the refrigeration cycle, avoid the condensation phenomenon of the return pipe, and improve the return pressure of the compressor 1, reduce the pressure ratio of the compressor, and improve the working performance of the compressor.
[0044] As shown in Figure 5 , 6 To improve the speed of the jet fluid into the liquid accumulator 8, the jet inlet is provided with a jet pipe 81, the jet pipe 81 has a jet necking section 811, a jet connecting section 813 and a jet intermediate section 812, the jet necking section 811 extends into the inner cavity of the liquid accumulator 8, the jet connecting section 813 is located outside the liquid accumulator 8, the jet intermediate section 812 is connected between the jet necking section 811 and the jet connecting section 813, the jet intermediate section 812 is tapered, the inner diameter of the jet necking section 811 is smaller than that of the jet connecting section 813, and the jet connecting section 813 is connected to the outlet of the first evaporator 6.
[0045] When the refrigerant of the first evaporator 6 passes through the jet necking section 811, the static pressure energy or thermal energy of the airflow is converted into kinetic energy, and the refrigerant fluid forms a high-speed jet at the necking section to cause a local vacuum, so that its pressure is lower than that of the flow fluid, so that the flow fluid is automatically sucked into the liquid accumulator 8.
[0046] In order to improve the back pressure of the mixed outlet, the mixed outlet is provided with a back gas pipe 82, the back gas pipe 82 is provided with a back gas necking section 821, a back gas connecting section 823 and a back gas intermediate section 822, the back gas necking section 821 is located in the mixed outlet, the back gas connecting section 823 is located outside the liquid accumulator 8, the back gas intermediate section 822 is connected between the back gas necking section 821 and the back gas connecting section 823, the back gas intermediate section 822 is tapered, the inner diameter of the back gas necking section 821 is smaller than the inner diameter of the back gas connecting section 823, and the back gas connecting section 823 is connected to the back gas port of the compressor 1.
[0047] When the mixed fluid in the liquid accumulator 8 enters the back gas necking section 821, the flow rate of the mixed fluid increases due to the decrease in the inner diameter, and then the mixed fluid enters the back gas intermediate section 822 and the back gas connecting section 823 with a larger inner diameter, and the flow rate is continuously slowed down due to the increase in the inner diameter, and the kinetic energy is converted into static pressure energy again. The mixed fluid is compressed to a certain back pressure in the back gas connecting section, thereby improving the back pressure of the back gas pipe 82, reducing the pressure ratio of the compressor 1, and improving the performance of the compressor 1.
[0048] In order to improve the drainage efficiency of the drainage inlet, the drainage inlet is provided with a drainage pipe 83, the outlet of the drainage pipe 83 extends into the inner cavity of the liquid accumulator 8, and the outlet of the drainage pipe 83 is close to the jet necking section 811, and the inlet of the drainage pipe 83 is connected to the outlet of the second evaporator 7.
[0049] When the refrigerant fluid flows out of the jet necking section 811 at a high speed to form a local vacuum, the outlet of the drainage pipe 83 is close to the jet necking section 811, so that the fluid in the drainage pipe 83 is smoothly drained into the inner cavity of the liquid accumulator 8. In the process of flowing to the mixed outlet, the drainage fluid is accelerated under the action of the jet fluid and accompanied by pressure rise, and forms a uniform and pressure centered mixed fluid at the inlet of the back gas necking section 821.
[0050] Based on the above design, the preferred scheme is that the inner diameter of the jet necking section 811 is smaller than the inner diameter of the back gas necking section 821, so as to increase the flow rate of the refrigerant when passing through the jet necking section 811. The high-speed jet fluid helps to improve the drainage effect and the refrigerant mixing effect. More preferably, the inner diameter of the drainage pipe 83 is larger than the inner diameter of the back gas necking section 821. The large inner diameter of the drainage pipe 83 can reduce the resistance of the refrigerant in the flow process, so that the refrigerant can flow more smoothly into the inner cavity of the liquid accumulator 8, and the drainage effect and the refrigerant mixing effect can be improved. In addition, the inner diameter of the jet necking section 811 is larger than the inner diameter of the capillary tube (the first capillary tube 4 and the second capillary tube 5), which helps to improve the smoothness of the refrigerant flow and the stability of the refrigeration system, and reduces the risk of capillary tube blockage.
[0051] In practical applications, the specific sizes of the jet pipe 81, the return pipe 82 and the drainage pipe 83 can be designed according to requirements, for example, the inner diameter of the jet nozzle section 811 is 1 / 3-1 / 4 of the inner diameter of the jet connecting section 813, the size range can enhance the jet effect and reduce unnecessary energy loss; the inner diameter of the return nozzle section 821 is about 1 / 2 of the inner diameter of the return connecting section 823, the size range helps to optimize the return pressure and reduce the return resistance; the inner diameter of the drainage pipe 83 remains basically unchanged from the inlet to the outlet, the size can ensure the stability of the fluid in the drainage pipe 83, and help the fluid to smoothly enter the inner cavity of the liquid reservoir 8.
[0052] In the preferred embodiment of the utility model, parallel refrigeration system still includes: first temperature sensor, second temperature sensor and return temperature sensor, first temperature sensor installs in first chamber, function is detecting actual temperature of first chamber, second temperature sensor installs in second chamber, function is detecting actual temperature of second chamber, return temperature sensor installs on return pipe 82, function is detecting actual return temperature of compressor 1.
[0053] Controller receives detection data of first temperature sensor, second temperature sensor and return temperature sensor, adjusts operating state of refrigerant circulation loop according to actual return temperature and actual temperature of evaporator corresponding chamber, prevents compressor return temperature too low, ensures reliability of parallel refrigeration system operation.
[0054] Taking the refrigerator as an example, the first evaporator 6 is a refrigeration evaporator, the first chamber is a refrigeration chamber, the first temperature sensor is a refrigeration chamber temperature control sensor, the second evaporator 7 is a freezing evaporator, the second chamber is a freezing chamber, and the second temperature sensor is a freezing chamber temperature sensor.
[0055] As shown in Figure 7 , the working process of the refrigerator is as follows:
[0056] The refrigerator is powered on for the first time;
[0057] The freezing chamber is preferentially controlled to refrigerate (the freezing evaporator works);
[0058] After the freezing chamber temperature control sensor reaches the shutdown point T d-off , the refrigeration chamber is switched to refrigerate (the refrigeration evaporator works);
[0059] During the refrigeration process of the refrigeration chamber, if the freezing chamber temperature control sensor rises to the start point T d-on + α ℃ (α ℃ is a set deviation, for example, 5 ℃), the freezing chamber is immediately switched to refrigerate, and if the freezing chamber temperature control sensor does not rise to the start point T d-onIf the temperature value Th collected by the return air temperature sensor is lower than the condensation point temperature of the environment where the return air pipe is located, the refrigeration compartment continues to refrigerate, and if not, the refrigeration compartment continues to refrigerate until the refrigeration compartment temperature control sensor drops to the stop point T c-off Afterwards, the compressor stops running.
[0060] The control logic of the above working process is executed by the controller, and the controller starts the two evaporators to refrigerate simultaneously when the return air temperature is too low, so as to ensure that the amount of refrigerant participating in the circulation is sufficient, and prevent the return air pipe from condensing when a single refrigeration circuit is running.
[0061] The utility model also proposes refrigeration equipment, including above-mentioned parallel refrigeration system, in some embodiments, refrigeration equipment is refrigerator.
[0062] It is to be noted that the terms used above are for the purpose of describing particular embodiments only and are not intended to limit exemplary embodiments according to the utility model. When the terms "comprising" and / or "including" are used in the specification, they indicate the presence of a feature, step, operation, device, component, and / or combinations thereof. The order of actions, steps, etc. in the devices and methods shown in the specification and drawings can be implemented in any order as long as the output of the previous processing is not used in the subsequent processing, unless the order is specifically limited. The similar ordinal terms used for the purpose of convenience in description do not mean that the implementation must be in such an order.
[0063] Techniques, methods, and devices known to those of ordinary skill in the relevant art can not be discussed in detail herein, but should be considered part of the description of the application, where appropriate. In all examples shown and discussed herein, any specific values should be interpreted as merely exemplary and not as a limitation. Thus, other examples of the exemplary embodiments can have different values. It should be noted that like reference numerals and letters refer to like items in the following drawings, and thus, once an item is defined in one drawing, it need not be discussed further in subsequent drawings.
[0064] The above only describes the preferred embodiments of the utility model, and does not limit the utility model, and any modification, equivalent replacement and improvement, etc. within the spirit and principle of the utility model should be included in the protection scope of the utility model.
Claims
1. Parallel refrigeration system, including: A compressor, a condenser, a throttling device, and an evaporator assembly are sequentially connected to form a refrigerant circulation loop, wherein the evaporator assembly includes a first evaporator and a second evaporator connected in parallel, wherein the cooling temperature of the second evaporator is lower than that of the first evaporator; It is characterized in that the evaporator assembly is connected to the return air port of the compressor through a liquid reservoir, and the liquid reservoir has a jet inlet, a drainage inlet and a mixing outlet, the jet inlet is connected to the outlet of the first evaporator, the drainage inlet is connected to the outlet of the second evaporator, and the mixing outlet is connected to the return air port of the compressor.
2. The parallel refrigeration system according to claim 1, characterized in that: The jet inlet is provided with a jet tube, which has a jet contraction section extending into the inner cavity of the liquid reservoir, a jet connecting section located outside the liquid reservoir, and a jet intermediate section connected between the jet contraction section and the jet connecting section. The inner diameter of the jet contraction section is smaller than the inner diameter of the jet connecting section, and the jet connecting section is connected to the outlet of the first evaporator.
3. The parallel refrigeration system according to claim 2, characterized in that: The mixing outlet is provided with a return air pipe, which is provided with a return air contraction section located inside the mixing outlet, a return air connecting section located outside the liquid reservoir, and a return air intermediate section connected between the return air contraction section and the return air connecting section. The inner diameter of the return air contraction section is smaller than the inner diameter of the return air connecting section, and the return air connecting section is connected to the return air port of the compressor.
4. The parallel refrigeration system according to claim 3, characterized in that: The drainage inlet is provided with a drainage tube, the outlet of the drainage tube extends into the inner cavity of the liquid reservoir and is close to the jet constriction section, and the inlet of the drainage tube is connected to the outlet of the second evaporator.
5. The parallel refrigeration system according to claim 4, characterized in that: The inner diameter of the jet constriction section is smaller than the inner diameter of the return air constriction section, and the inner diameter of the drainage tube is larger than the inner diameter of the return air constriction section.
6. The parallel refrigeration system according to claim 4, characterized in that: The inner diameter of the jet constriction section is 1 / 3 to 1 / 4 of the inner diameter of the jet connection section, the inner diameter of the return air constriction section is 1 / 2 of the inner diameter of the return air connection section, and the inner diameter of the drainage tube remains consistent from the inlet to the outlet.
7. The parallel refrigeration system according to claim 2, characterized in that: The throttling device adopts a capillary tube, and the inner diameter of the jet constriction section is larger than the inner diameter of the capillary tube.
8. The parallel refrigeration system according to any one of claims 1 to 7, characterized in that: The parallel refrigeration system further comprises: a first temperature sensor for detecting an actual temperature of a first compartment, the first evaporator providing cooling for the first compartment; a second temperature sensor for detecting an actual temperature of a second compartment, the second evaporator providing cooling for the second compartment; a return air temperature sensor, configured to detect the actual return air temperature of the compressor; A controller receives detection data from the first temperature sensor, the second temperature sensor, and the return air temperature sensor, and adjusts the operating state of the refrigerant circulation loop.
9. Refrigeration equipment, characterized in that The refrigeration equipment comprises the parallel refrigeration system according to any one of claims 1 to 8.
10. The refrigeration equipment according to claim 9, characterized in that The refrigeration device is a refrigerator, the first evaporator is a refrigeration evaporator, and the second evaporator is a freezing evaporator.