Return gas pipe assembly, refrigeration system and refrigeration equipment

Abstract

This utility model discloses a return gas pipe assembly, a refrigeration system, and refrigeration equipment, belonging to the technical field of refrigeration equipment. The return gas pipe assembly includes a return gas pipe and a capillary tube. The return gas pipe has a silencing chamber with a first end and a second end. The first end is connected to the outlet of the evaporator, and the second end is connected to the inlet of the compressor. The refrigerant in the silencing chamber flows from the first end to the second end, and the cross-sectional area of ​​the silencing chamber first increases and then decreases along the direction from the first end to the second end. The capillary tube has a third end and a fourth end. The third end is connected to the outlet of the condenser, and the fourth end is connected to the inlet of the evaporator. A portion of the capillary tube's piping structure passes through the silencing chamber. This utility model reduces noise generation, improves the heat exchange efficiency and energy efficiency of the refrigeration system, and optimizes noise performance while maintaining sufficient heat exchange between the capillary tube and the return gas pipe.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration equipment technology, and in particular to a return gas pipe assembly, a refrigeration system and refrigeration equipment. Background Technology

[0002] In related technologies, to improve the energy efficiency of refrigeration equipment, a common practice is to wrap a capillary tube around the outer wall of the return gas pipe. This allows the high-temperature liquid refrigerant inside the capillary tube to exchange heat with the low-temperature gaseous refrigerant in the return gas pipe, thereby increasing the subcooling of the refrigerant entering the evaporator and enhancing the evaporator's heat absorption capacity. However, the intense heat exchange and phase change can easily cause vibration and abnormal flow, resulting in significant noise generation. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a return gas pipe assembly that can reduce noise generation while maintaining sufficient heat exchange between the capillary tube and the return gas pipe.

[0004] This utility model also proposes a refrigeration system and refrigeration equipment including the above-mentioned return gas pipe assembly.

[0005] According to a first aspect of the present invention, a return pipe assembly is applied to a refrigeration system having an evaporator, a compressor, and a condenser, comprising: a return pipe and a capillary tube, wherein the return pipe is provided with a silencing cavity, the silencing cavity having a first end and a second end, the first end being connected to the outlet of the evaporator, the second end being connected to the inlet of the compressor, the refrigerant in the silencing cavity flowing from the first end to the second end, and the cross-sectional area of ​​the silencing cavity first increasing and then decreasing along the direction from the first end to the second end; the capillary tube having a third end and a fourth end, the third end being connected to the outlet of the condenser, the fourth end being connected to the inlet of the evaporator, and a portion of the capillary tube's piping structure passing through the silencing cavity.

[0006] The return air pipe assembly according to the embodiments of this utility model has at least the following beneficial effects:

[0007] The return pipe assembly of this utility model incorporates a silencing cavity within the return pipe, with a heat exchange section built into it. Gaseous refrigerant flows from the first end to the second end, while liquid refrigerant flows from the third end to the fourth end. The two exchange heat effectively through the outer wall of the heat exchange section, enhancing the evaporator's heat absorption capacity and reducing the risk of liquid slugging in the compressor. Furthermore, by configuring the silencing cavity with a cross-sectional area that first increases and then decreases along the direction from the first end to the second end, the sudden expansion or contraction of its cross-section attenuates the pulsating noise propagating within the silencing cavity, thus achieving noise reduction. While maintaining sufficient heat exchange between the capillary tube and the return pipe, this reduces noise generation, improving not only the heat exchange efficiency and energy efficiency of the refrigeration system but also optimizing its noise performance.

[0008] According to some embodiments of the present invention, the silencing cavity includes a first cavity, a second cavity, and a third cavity connected sequentially along the direction from the first end to the second end. Along the direction from the first end to the second end, the cross-sectional area of ​​the first cavity gradually increases, and the cross-sectional area of ​​the third cavity gradually decreases.

[0009] According to some embodiments of the present invention, the first cavity and the third cavity are conical, the maximum cross-sectional area of ​​the first cavity is a, the minimum cross-sectional area of ​​the first cavity is b; the maximum cross-sectional area of ​​the third cavity is c, the minimum cross-sectional area of ​​the third cavity is d, satisfying: 10≤a / b≤20, 10≤c / d≤20.

[0010] According to some embodiments of the present invention, the maximum inner diameter of the first cavity is D1, the minimum inner diameter of the first cavity is D2; the maximum inner diameter of the third cavity is D3, the minimum inner diameter of the third cavity is D4, satisfying: 10mm≤D1≤30mm, 3mm≤D2≤7mm, 10mm≤D3≤30mm, 3mm≤D4≤7mm.

[0011] According to some embodiments of the present invention, the first end is located at the end of the first cavity away from the second cavity, the second end is located at the end of the third cavity away from the second cavity, and the maximum distance between the first end and the second end is L, satisfying: 4cm≤L≤9cm.

[0012] According to some embodiments of the present invention, the capillary tube includes a heat exchange section, which is disposed within the silencing cavity.

[0013] According to some embodiments of the present invention, the return pipe includes a first inlet section and a first outlet section. The first inlet section is connected to the port of the first cavity, and the first outlet section is connected to the port of the third cavity. The capillary tube also includes a second inlet section and a second outlet section. The second inlet section and the second outlet section are respectively connected to the two ends of the heat exchange section. The second outlet section passes through the first inlet section, and the second inlet section passes through the first outlet section.

[0014] or,

[0015] The side wall of the third cavity is provided with an opening, through which the second inlet section extends, and the outer peripheral wall of the second inlet section is sealed to the inner wall of the opening.

[0016] According to some embodiments of the present invention, the heat exchange section is spirally wound along the direction from the first end toward the second end.

[0017] A refrigeration system according to a second aspect of the present invention includes a compressor, a condenser, an evaporator, and a return pipe assembly as described in the first aspect embodiment. The compressor, the condenser, the capillary tube, the evaporator, and the return pipe are connected in sequence, and the return pipe is connected to the compressor to form a loop for refrigerant flow.

[0018] The refrigeration system according to the embodiments of this utility model has at least the following beneficial effects:

[0019] The refrigeration system of this embodiment adopts the return pipe assembly of the first aspect embodiment. By setting a silencing cavity in the return pipe and embedding the heat exchange section in the silencing cavity, the gaseous refrigerant flows from the first end to the second end, and the liquid refrigerant flows from the third end to the fourth end. The two exchange heat fully through the outer wall of the heat exchange section, which not only enhances the heat absorption capacity of the evaporator, but also reduces the risk of liquid slugging in the compressor. Furthermore, by configuring the silencing cavity with a cross-sectional area that first increases and then decreases along the direction from the first end to the second end, the sudden expansion or contraction of its cross-section attenuates the pulsating noise propagating in the silencing cavity, thereby achieving a noise reduction effect. While maintaining sufficient heat exchange between the capillary tube and the return pipe, the generation of noise is reduced, which not only improves the heat exchange efficiency and energy efficiency of the refrigeration system, but also optimizes the noise performance of the refrigeration system.

[0020] The refrigeration device according to the third aspect of the present invention includes the refrigeration system described in the second aspect embodiment. The refrigeration device has a compressor compartment and an insulation layer inside. When the return gas pipe assembly is installed in the compressor compartment, the first end is arranged laterally towards the second end; when the return gas pipe assembly passes through the insulation layer, the first end is arranged vertically towards the second end.

[0021] The refrigeration device according to the embodiments of this utility model has at least the following beneficial effects:

[0022] The refrigeration equipment of this utility model adopts the refrigeration system of the second aspect embodiment. By optimizing the structural design of the return gas pipe assembly, while maintaining sufficient heat exchange between the capillary tube and the return gas pipe, the generation of noise is reduced. This not only improves the refrigeration efficiency and energy efficiency ratio of the refrigeration equipment, but also reduces the low-frequency noise and beat frequency noise generated during the operation of the refrigeration equipment, thereby enhancing the user experience.

[0023] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0024] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0025] Figure 1 This is a schematic diagram of the structure of a return air pipe assembly according to an embodiment of the present invention;

[0026] Figure 2 This is a partial structural diagram of a refrigeration system according to an embodiment of the present invention;

[0027] Figure 3 This is another structural schematic diagram of the return air pipe assembly according to an embodiment of the present utility model;

[0028] Figure 4 This is a schematic diagram of the structure of a refrigeration device according to an embodiment of the present invention;

[0029] Figure 5 This is a schematic diagram of the structure of a refrigeration device according to another embodiment of the present invention.

[0030] Icon labels:

[0031] Return gas pipe assembly 1000; Refrigeration system 2000;

[0032] 100 return air pipe; 110 silencer chamber; 111 first chamber; 112 second chamber; 113 third chamber; 120 first end; 130 second end; 140 first inlet section; 150 first outlet section; 160 silencer section; 170 connecting section;

[0033] Capillary tube 200; Third end 210; Fourth end 220; Heat exchange section 230; Second inlet section 240; Second outlet section 250;

[0034] Evaporator 300; Dryer filter 400; Compressor 500; Condenser 600. Detailed Implementation

[0035] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0036] In the description of this utility model, it should be understood that the orientation descriptions, such as up, down, etc., are based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0037] In the description of this utility model, the use of "first" and "second" is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features or the order of the technical features.

[0038] In the description of this utility model, unless otherwise explicitly defined, terms such as "setting," "installation," and "connection" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0039] To improve the energy efficiency of refrigerators, a capillary tube is commonly used in their refrigeration systems. This design allows the high-temperature liquid refrigerant in the capillary tube to be cooled by the low-temperature gaseous refrigerant in the return pipe, resulting in a lower temperature of the liquid refrigerant before it enters the evaporator, thus enhancing the evaporator's heat absorption capacity. On the other hand, the low-temperature gaseous refrigerant in the return pipe is heated by the high-temperature liquid refrigerant in the capillary tube, ensuring that the gas returning to the compressor has a higher dryness and temperature, reducing the risk of liquid slugging caused by the compressor drawing in liquid refrigerant.

[0040] However, because the liquid refrigerant in the capillary tube and the gaseous refrigerant in the return pipe flow in opposite directions and have a large temperature difference, the heat exchange between them is very intense. This intense heat exchange causes rapid and drastic fluctuations in the temperature, pressure, and flow rate of the refrigerant in both pipes, triggering vibrations and generating low-frequency noise. Furthermore, the heat exchange effect of the capillary tube wrapped around the return pipe is not ideal, resulting in excessively dry refrigerant flowing out of the capillary tube. Upon entering the evaporator, this gas-liquid mixture generates beat frequency noise.

[0041] In short, while using capillary-wound return pipes for heat exchange to improve refrigerator energy efficiency is necessary, it inevitably generates various types of noise, severely interfering with the user experience. Eliminating the winding process would reduce noise, but would lead to a decline in refrigerator performance.

[0042] To address the aforementioned problems, some embodiments of this utility model propose a return pipe assembly 1000, suitable for a refrigeration system 2000 having an evaporator 300, a compressor 500, and a condenser 600. This assembly reduces noise generation while maintaining sufficient heat exchange between the capillary tube 200 and the return pipe 100. See details below. Figures 1 to 5 The return air pipe assembly 1000 is described in the figure.

[0043] It should be noted that, in this embodiment of the present invention, the return pipe assembly 1000 includes a return pipe 100 and a capillary tube 200. The compressor 500, condenser 600, capillary tube 200, evaporator 300, and return pipe 100 are sequentially connected to form a closed-loop refrigerant circulation circuit. Specifically, the compressor 500 compresses the gaseous refrigerant into a high-temperature, high-pressure state and outputs it to the condenser 600. The condenser 600 then causes the high-temperature, high-pressure gaseous refrigerant to release heat and condense, converting it into a high-pressure, room-temperature liquid refrigerant, which is then transported to the capillary tube 200. The capillary tube 200 throttles and reduces the pressure of the high-pressure liquid refrigerant, outputting a low-temperature, low-pressure gas-liquid two-phase refrigerant to the evaporator 300. The evaporator 300 absorbs ambient heat, causing the low-temperature, low-pressure gas-liquid two-phase refrigerant to completely evaporate into a low-temperature, low-pressure gaseous refrigerant. The return pipe 100 then transports the low-temperature, low-pressure gaseous refrigerant output from the evaporator 300 back to the compressor 500, completing the cycle.

[0044] Specifically, refer to Figure 1 As shown in this embodiment of the present invention, the return pipe 100 is provided with a silencer 110. For example, the inner cavity of one section of the return pipe 100 is formed with a silencer 110. The silencer 110 has a first end 120 and a second end 130. The first end 120 and the second end 130 are arranged opposite to each other. The first end 120 is connected to the outlet of the evaporator 300, and the second end 130 is connected to the inlet of the compressor 500. Based on this, the refrigerant in the silencer 110 flows from the first end 120 to the second end 130.

[0045] Combination Figure 2 As shown, in one example, the return pipe 100 includes a silencer section 160 and two connecting sections 170. A silencer cavity 110 is disposed within the silencer section 160. The two connecting sections 170 are respectively connected to two ports of the silencer section 160. One connecting section 170 is connected to the evaporator 300, and the other connecting section 170 is connected to the compressor 500. In this embodiment, the evaporator 300 is a blow-type evaporator 300.

[0046] Continue to refer to Figure 1 As shown, in this embodiment of the invention, the capillary tube 200 has a third end 210 and a fourth end 220. The third end 210 is connected to the outlet of the condenser 600, and the fourth end 220 is connected to the inlet of the evaporator 300. Based on this, the refrigerant from the condenser 600 flows from the third end 210 to the fourth end 220. In this embodiment, a portion of the pipe structure of the capillary tube 200 passes through the silencing cavity 110 to achieve heat exchange between the liquid refrigerant in the capillary tube 200 and the gaseous refrigerant in the silencing cavity 110.

[0047] In this embodiment of the utility model, the capillary tube 200 includes a bent heat exchange section 230, which passes through the silencing cavity 110. Specifically, the bent arrangement of the heat exchange section 230 of the capillary tube 200 means that the pipe through which the liquid refrigerant flows forms a non-straight path in the silencing cavity 110, which can be achieved by using a spiral or serpentine bending structure.

[0048] Understandably, when the capillary tube 200 is wound around the outer wall of the return pipe 100, the two refrigerants only conduct heat through the pipe wall, and the heat exchange efficiency is limited by the contact area. In contrast, in this embodiment of the invention, after the capillary tube 200 is built in, the liquid refrigerant is directly exposed to the gaseous refrigerant flow field, which prolongs the residence time of the liquid refrigerant in the silencing cavity 110. This allows the liquid refrigerant in the heat exchange section 230 to fully exchange heat with the gaseous refrigerant in the silencing cavity 110, enabling the liquid refrigerant in the capillary tube 200 to be cooled by the gaseous refrigerant and the gaseous refrigerant in the silencing cavity 110 to be heated by the liquid refrigerant, thus maintaining the performance advantages brought by the original heat exchange between the capillary tube 200 and the return pipe 100.

[0049] It should be noted that, in this embodiment of the invention, the liquid refrigerant in the heat exchange section 230 and the gaseous refrigerant in the silencing cavity 110 flow in opposite directions. Figure 1 Taking the vertical direction as an example, the liquid refrigerant in the heat exchange section 230 flows from bottom to top, while the gaseous refrigerant in the silencing cavity 110 flows from top to bottom. It should be emphasized that although the gaseous refrigerant in the silencing cavity 110 may flow in multiple directions locally, from a macroscopic perspective, its overall flow direction is from top to bottom.

[0050] To suppress noise generation, refer to Figure 1 As shown, in this embodiment of the invention, the cross-sectional area of ​​the silencing cavity 110 first increases and then decreases along the direction from the first end 120 to the second end 130. Specifically, continuing with... Figure 1 Taking the vertical direction as an example, in this embodiment, the cross-sectional area first increases and then decreases means that the flow cross-section of the silencing cavity 110 exhibits a continuous change from top to bottom, first expanding and then contracting. Specifically, it can be formed by combining conical pipe sections, which can adjust the flow velocity distribution of the gaseous refrigerant through cross-sectional changes.

[0051] Continue to refer to Figure 1 As shown in this embodiment of the invention, when the refrigerant enters the silencing cavity 110 from the evaporator 300, it first flows through a region with a gradually increasing cross-sectional area, where the flow velocity decreases, reducing pressure fluctuations. When it enters the region with the largest cross-sectional area, the airflow tends to stabilize. Subsequently, in the region with a gradually decreasing cross-sectional area, the airflow is accelerated and directed to the compressor 500, avoiding kinetic energy loss. At the same time, the liquid refrigerant in the capillary tube 200 flows slowly in the curved heat exchange section 230, fully exchanging heat with the gaseous refrigerant in the silencing cavity 110. Due to the extended path of the liquid refrigerant, the heat transferred per unit time is more uniform, avoiding sudden temperature changes caused by localized intense heat exchange.

[0052] Understandably, if the cross-section of a pipe suddenly expands or contracts, it can attenuate pulsations of a specific frequency as they propagate within the pipe, thus achieving a noise reduction effect. Based on this, the cross-sectional variation design of the silencing cavity 110 effectively suppresses airflow pulsations, significantly reducing pressure fluctuations and mechanical vibrations caused by intense heat exchange, thereby reducing noise generation. Furthermore, it avoids the noise problem of the evaporator 300 caused by excessively dry refrigerant.

[0053] The return pipe assembly 1000 of this utility model provides a silencing cavity 110 in the return pipe 100 and incorporates a heat exchange section 230 within the silencing cavity 110. The refrigerant flows from the first end 120 to the second end 130 and from the third end 210 to the fourth end 220, with both flowing through the outer wall of the heat exchange section 230 to exchange heat effectively. This enhances the heat absorption capacity of the evaporator 300 and reduces the risk of liquid slugging in the compressor 500. Furthermore, by configuring the silencing cavity 110 with a cross-sectional area that first increases and then decreases along the direction from the first end 120 to the second end 130, the sudden expansion or contraction of its cross-section attenuates the pulsating noise propagating within the silencing cavity 110, thereby achieving a noise reduction effect. While maintaining sufficient heat exchange between the capillary tube 200 and the return pipe 100, this reduces noise generation, improving not only the heat exchange efficiency and energy efficiency of the refrigeration system 2000 but also optimizing its noise performance.

[0054] Reference Figure 1 As shown in the embodiment of this utility model, the silencing cavity 110 includes a first cavity 111, a second cavity 112, and a third cavity 113. The first cavity 111, the second cavity 112, and the third cavity 113 are connected sequentially along the direction from the first end 120 to the second end 130 to form the silencing cavity 110. Specifically, along the direction from the first end 120 to the second end 130, the cross-sectional area of ​​the first cavity 111 gradually increases, forming a gradually expanding cavity structure. This can be achieved through a tapered pipe section or a gradually expanding pipe structure, used to slow down the flow rate of the gaseous refrigerant and reduce flow resistance.

[0055] Continue to refer to Figure 1 As shown in this embodiment of the invention, the cross-sectional area of ​​the second cavity 112 is constant, that is, the second cavity 112 is cylindrical, which can be implemented by a straight pipe section of equal diameter, and is used to stabilize the flow state of the gaseous refrigerant. The cross-sectional area of ​​the third cavity 113 gradually decreases, forming a tapered cavity structure, which can be implemented by a tapered pipe section or a tapered pipe structure, and is used to accelerate the flow of the gaseous refrigerant and suppress the generation of turbulence.

[0056] Specifically, continue to refer to Figure 1 As shown in this embodiment of the invention, after the refrigerant enters the first cavity 111 from the evaporator 300, its flow velocity decreases in the space with a gradually increasing cross-sectional area, and the flow energy is dispersed, thereby reducing pressure fluctuations caused by sudden changes in flow velocity. Subsequently, the refrigerant enters the second cavity 112, maintaining a stable flow state in a pipe section with a constant cross-sectional area, avoiding drastic changes in flow velocity. Finally, the refrigerant enters the third cavity 113, where its flow velocity is gradually increased in a space with a gradually decreasing cross-sectional area. The flow direction is guided by the tapering structure, suppressing turbulence and vortex formation. This three-cavity combination structure, by adjusting the refrigerant flow state in stages, makes pressure changes tend to be gradual.

[0057] Understandably, in designs where the return pipe 100 employs a single-cavity structure, the refrigerant flow rate changes are concentrated and drastic, easily leading to pressure fluctuations and vibration noise. In contrast, this embodiment of the invention separates the refrigerant's deceleration, stabilization, and acceleration processes, gradually weakening the pressure fluctuation amplitude and thus reducing vibration energy. This effectively suppresses vibration noise caused by sudden pressure changes when the gaseous refrigerant flows within the return pipe 100, while maintaining the stability of the refrigerant flow and avoiding fluctuations in heat exchange efficiency caused by drastic changes in flow rate.

[0058] Reference Figure 3 As shown, in this embodiment of the present invention, the first cavity 111 and the third cavity 113 are conical. In one example, the first cavity 111 and the third cavity 113 are implemented with a conical structure, wherein the first cavity 111 is a forward conical shape and the third cavity 113 is an inverted conical shape. In this embodiment, the maximum cross-sectional area of ​​the first cavity 111 is a, and the minimum cross-sectional area of ​​the first cavity 111 is b; the maximum cross-sectional area of ​​the third cavity 113 is c, and the minimum cross-sectional area of ​​the third cavity 113 is d, satisfying: 10≤a / b≤20, 10≤c / d≤20. For example, a / b takes values ​​of 10, 11, 12.5, 14, 16, 18, 19, etc., and c / d takes values ​​of 10, 11, 12.5, 14, 16, 18, 19, etc.

[0059] It should be noted that a / b represents the ratio of the maximum to the minimum cross-section in the first cavity 111, and c / d represents the ratio of the maximum to the minimum cross-section in the third cavity 113. Both can be controlled by adjusting the cone angle or the axial length. Multiple experiments have shown that the refrigerant pulsation noise in the refrigerator is mainly concentrated in the low-frequency range. By using the acoustic-vibration coherence method to identify the noise spectrum, it was determined that the main noise distribution is in the 200Hz to 500Hz frequency range. The speed of sound in R600a refrigerant is 110m / s. Simulation calculations of transmission loss revealed that the larger the expansion ratio of the silencing cavity, the greater the noise reduction; however, if the expansion ratio is too large, the cross-sectional change is too drastic, which can generate secondary turbulence.

[0060] Therefore, this embodiment of the invention reasonably limits the value ranges of a / b and c / d to ensure that the cavity has a sufficient expansion and contraction gradient to buffer pressure pulsations, while also avoiding secondary turbulence caused by excessively drastic changes in cross-section. During this process, the refrigerant flow transitions from severe turbulence to laminar flow, and the pressure fluctuation amplitude is effectively attenuated. It should be noted that in this embodiment, the values ​​of a / b and c / d can be the same or different; this embodiment does not impose any limitation on this.

[0061] Furthermore, referring to Figure 3 As shown, in this embodiment of the present invention, the maximum inner diameter of the first cavity 111 is D1, and the minimum inner diameter of the first cavity 111 is D2; the maximum inner diameter of the third cavity 113 is D3, and the minimum inner diameter of the third cavity is D4, satisfying the following conditions: 10mm≤D1≤30mm, 3mm≤D2≤7mm, 10mm≤D3≤30mm, 3mm≤D4≤7mm. For example, D1 can take values ​​of 10mm, 12mm, 15mm, 18.5mm, 20mm, 26mm, 30mm, etc.; D2 can take values ​​of 3mm, 4mm, 5.5mm, 6mm, 6mm, etc.; D3 can take values ​​of 10mm, 12mm, 15mm, 18.5mm, 20mm, 26mm, 30mm, etc.; and D4 can take values ​​of 3mm, 4mm, 5.5mm, 6mm, 6mm, etc.

[0062] by Figure 1Taking the vertical direction as an example, the maximum inner diameter of the first cavity 111 is the inner diameter of its lower end, and the minimum inner diameter of the first cavity 111 is the inner diameter of its upper end. The maximum inner diameter of the third cavity 113 is the inner diameter of the upper end of the first cavity 111, and the minimum inner diameter of the first cavity 111 is the inner diameter of the lower end of the third cavity 113. It can be understood that this embodiment of the invention prevents the refrigerant from forming eddies due to a sudden drop in flow velocity in the expansion section, or from experiencing pressure shocks due to a sudden change in cross-sectional area in the contraction section, by reasonably limiting the value ranges of D1, D2, D3, and D4. The flow velocity drop in the expansion section is controlled within the range that the compressor 500 can withstand, while the acceleration process in the contraction section is limited by the minimum inner diameter at the end, thereby effectively eliminating pressure oscillations caused by sudden changes in flow velocity.

[0063] Continue to refer to Figure 3 As shown, in this embodiment of the present invention, the first end 120 is located at the end of the first cavity 111 away from the second cavity 112, and the second end 130 is located at the end of the third cavity 113 away from the second cavity 112. The maximum distance between the first end 120 and the second end 130 is L, which satisfies the condition: 4cm ≤ L ≤ 9cm, for example, 4cm, 5cm, 6.5cm, 8cm, 9cm, etc. It should be noted that the maximum distance between the first end 120 and the second end 130 refers to the maximum straight-line distance between the first end 120 and the second end 130.

[0064] Simulation experiments and transmission loss calculations revealed that a longer anechoic cavity 110 results in a wider attenuation bandwidth; however, excessive length of the anechoic cavity 110 leads to excessive flow resistance. Therefore, this embodiment of the invention, by reasonably limiting the range of L, ensures that the axial length of the anechoic cavity 110 matches the refrigerant flow velocity. This avoids both excessively short length leading to aggravated pressure fluctuations and excessively long length causing excessive flow resistance, effectively buffering pressure fluctuations and reducing sudden changes in flow velocity, thereby effectively suppressing noise generation.

[0065] Reference Figure 1 As shown, in this embodiment of the present invention, the return air pipe 100 includes a first inlet section 140 and a first outlet section 150. The first inlet section 140 is connected to the port of the first cavity 111, and the first outlet section 150 is connected to the port of the third cavity 113. Specifically, the first inlet section 140 refers to the tubular structure connected to the inlet end of the silencing cavity 110, and the first outlet section 150 refers to the tubular structure connected to the outlet end of the silencing cavity 110. In one example, the first inlet section 140 is integrally formed with the first cavity 111, and the first outlet section 150 is integrally formed with the third cavity 113.

[0066] Continue to refer to Figure 1As shown in the embodiment of this utility model, the capillary tube 200 further includes a second inlet section 240 and a second outlet section 250. The second inlet section 240 refers to the section of the capillary tube 200 that connects to the outlet of the condenser 600, and the second outlet section 250 refers to the section of the capillary tube 200 that connects to the inlet of the evaporator 300. The second inlet section 240 and the second outlet section 250 are respectively connected to the two ends of the heat exchange section 230.

[0067] Understandably, referring to Figure 1 As shown, in one example, the second inlet section 240 is inserted into the first outlet section 150, and the second outlet section 250 is inserted into the first inlet section 140. By arranging the second inlet section 240 into the first outlet section 150, the liquid refrigerant can pre-exchange heat with the gaseous refrigerant before entering the heat exchange section 230. Then, by arranging the liquid refrigerant to enter the first inlet section 140 in the opposite direction, the liquid refrigerant can still maintain counter-current heat exchange with the gaseous refrigerant after flowing out of the heat exchange section 230.

[0068] Reference Figure 2 As shown, in one example, the second outlet section 250 passes through the first inlet section 140. The side wall of the third cavity 113 is provided with an opening. The opening penetrates the side wall of the third cavity 113 and is configured to allow the second inlet section 240 to pass through the opening. The outer peripheral wall of the second inlet section 240 is sealed to the inner wall of the opening. Specifically, the gap between the outer peripheral wall of the second inlet section 240 and the inner wall of the opening can be sealed by welding, thereby preventing refrigerant leakage.

[0069] Understandably, in this embodiment, the second inlet section 240 can be directly inserted through an opening and welded to the dryer filter 400. This design avoids the welding process between the second inlet section 240 and other capillary tube sections 200, which not only improves sealing reliability but also reduces processing difficulty.

[0070] Reference Figure 1 As shown in this embodiment of the present invention, the heat exchange section 230 is spirally wound along the direction from the first end 120 toward the second end 130. In this embodiment, the heat exchange section 230 can be formed by bending copper or aluminum tubes into a spiral structure. The curved path formed by the spiral winding can prolong the flow time of the liquid refrigerant in the silencing cavity 110. Moreover, the continuous curved surface of the spiral structure can guide the gaseous refrigerant to form a stable flow. Specifically, the continuous flow channel formed by the spiral winding can suppress the violent fluctuation of the gaseous refrigerant flow rate, so that the pressure change in the silencing cavity 110 tends to be gradual.

[0071] Reference Figure 2As shown, an embodiment of this utility model also proposes a refrigeration system 2000, including a compressor 500, a condenser 600, an evaporator 300 and a return pipe assembly 1000 as described in the above embodiment. The compressor 500, condenser 600, capillary tube 200, evaporator 300 and return pipe 100 are connected in sequence, and the return pipe 100 is connected to the compressor 500 to form a loop for refrigerant flow.

[0072] Specifically, during the operation of the refrigeration system 2000, gaseous refrigerant enters the silencer chamber 110 of the return pipe 100 from the outlet of the evaporator 300, flowing along the cavity with varying cross-sectional area, gradually decreasing in velocity and reducing pressure fluctuations. Liquid refrigerant enters the capillary tube 200 from the outlet of the condenser 600, exchanging heat with the gaseous refrigerant as it flows through the heat exchange section 230 within the silencer chamber 110. After the liquid refrigerant's temperature decreases, it enters the evaporator 300, while the gaseous refrigerant's temperature increases and it returns to the compressor 500. The silencer chamber 110 structure suppresses sudden changes in flow velocity, reducing vibrations in the gas-liquid two-phase fluid. Simultaneously, the heat exchange section 230 within the capillary tube 200, through its curved or spiral design, extends the heat exchange time, balancing the heat exchange intensity.

[0073] The refrigeration system 2000 of this utility model adopts the return pipe assembly 1000 of the above embodiment. By setting a silencing cavity 110 in the return pipe 100 and embedding the heat exchange section 230 in the silencing cavity 110, gaseous refrigerant flows from the first end 120 to the second end 130, and liquid refrigerant flows from the third end 210 to the fourth end 220. The two exchange heat fully through the outer wall of the heat exchange section 230, which not only enhances the heat absorption capacity of the evaporator 300, but also reduces the risk of liquid slugging to the compressor 500. Furthermore, by configuring the silencing cavity 110 such that its cross-sectional area first increases and then decreases along the direction from the first end 120 to the second end 130, the sudden expansion or contraction of its cross-section attenuates the pulsating noise propagating within the silencing cavity 110, thereby achieving a noise reduction effect. While maintaining sufficient heat exchange between the capillary tube 200 and the return pipe 100, the generation of noise is reduced. This not only improves the heat exchange efficiency and energy efficiency of the refrigeration system 2000, but also optimizes the noise performance of the refrigeration system 2000.

[0074] In one example, the evaporator 300, the return pipe 100, and the capillary tube 200 inserted therein can be supplied directly by the manufacturer as a single unit. That is, the section of piping from the capillary tube 200 into the silencing cavity 110 until it is inserted into the evaporator 300 is provided to the user or installer as a complete finished product.

[0075] Since the refrigeration system 2000 adopts all the technical solutions of the return pipe assembly 1000 of the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be repeated here.

[0076] Reference Figure 4 and Figure 5 As shown, an embodiment of this utility model also proposes a refrigeration device, including the refrigeration system 2000 of the above embodiment. The refrigeration device has a compressor compartment and an insulation layer inside. When the return pipe assembly 1000 is installed in the compressor compartment, the first end 120 is arranged laterally towards the second end 130; when the return pipe assembly 1000 passes through the insulation layer, the first end 120 is arranged vertically towards the second end 130. In one example, the refrigeration device is a refrigerator. It should be noted that the refrigeration device can also be a freezer, wine cabinet, fresh food cabinet, etc., and this embodiment does not limit it to this.

[0077] The refrigeration equipment of this utility model embodiment adopts the refrigeration system 2000 of the above embodiment. The refrigeration equipment is provided with a compressor compartment and an insulation layer. When the return pipe assembly 1000 is installed in the compressor compartment, the first end 120 is arranged horizontally towards the second end 130; when the return pipe assembly 1000 is inserted into the insulation layer, the first end 120 is arranged vertically towards the second end 130.

[0078] It is understood that a horizontal arrangement refers to the return pipe assembly 1000 extending horizontally within the compressor compartment. Specifically, this can be achieved by installing the silencing cavity 110 with its axis parallel to the ground, thus adapting to the compact layout of the compressor compartment's horizontal space. A vertical arrangement refers to the return pipe assembly 1000 extending vertically within the insulation layer. Specifically, this can be achieved by installing the silencing cavity 110 with its axis perpendicular to the ground, thus fully utilizing the vertical space within the insulation layer. This embodiment of the invention adjusts the spatial orientation of the return pipe assembly 1000 according to differences in installation position, improving the space utilization rate inside the refrigeration equipment.

[0079] Since the refrigeration equipment adopts all the technical solutions of the refrigeration system 2000 of the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be repeated here.

[0080] Of course, this utility model is not limited to the above-described embodiments. Those skilled in the art can make equivalent modifications or substitutions without departing from the spirit of this utility model. All such equivalent modifications or substitutions are included within the scope defined by the claims of this application.

Claims

1. A return gas pipe assembly, used in a refrigeration system having an evaporator, a compressor, and a condenser, characterized in that, include: The return pipe is provided with a silencer cavity, which has a first end and a second end. The first end is connected to the outlet of the evaporator, and the second end is connected to the inlet of the compressor. The refrigerant in the silencer cavity flows from the first end to the second end, and the cross-sectional area of ​​the silencer cavity first increases and then decreases along the direction from the first end to the second end. The capillary tube has a third end and a fourth end. The third end is connected to the outlet of the condenser, and the fourth end is connected to the inlet of the evaporator. A portion of the capillary tube's tubing structure passes through the silencing cavity.

2. The return air duct assembly of claim 1, wherein, The silencing cavity includes a first cavity, a second cavity, and a third cavity connected sequentially along the direction from the first end to the second end. Along the direction from the first end to the second end, the cross-sectional area of ​​the first cavity gradually increases, and the cross-sectional area of ​​the third cavity gradually decreases.

3. The air return tube assembly of claim 2, wherein, The first cavity and the third cavity are conical. The maximum cross-sectional area of ​​the first cavity is a, and the minimum cross-sectional area of ​​the first cavity is b. The maximum cross-sectional area of ​​the third cavity is c, and the minimum cross-sectional area of ​​the third cavity is d, satisfying: 10≤a / b≤20, 10≤c / d≤20.

4. The return air duct assembly of claim 3, wherein, The maximum inner diameter of the first cavity is D1, and the minimum inner diameter of the first cavity is D2; the maximum inner diameter of the third cavity is D3, and the minimum inner diameter of the third cavity is D4, satisfying: 10mm≤D1≤30mm, 3mm≤D2≤7mm, 10mm≤D3≤30mm, 3mm≤D4≤7mm.

5. The air return tube assembly of claim 2, wherein, The first end is located at the end of the first cavity away from the second cavity, and the second end is located at the end of the third cavity away from the second cavity. The maximum distance between the first end and the second end is L, which satisfies: 4cm≤L≤9cm.

6. The air return tube assembly of claim 2, wherein, The capillary tube includes a heat exchange section, which is inserted into the silencing cavity.

7. The air return tube assembly of claim 6, wherein, The return gas pipe includes a first inlet section and a first outlet section. The first inlet section is connected to the port of the first cavity, and the first outlet section is connected to the port of the third cavity. The capillary tube also includes a second inlet section and a second outlet section. The second inlet section and the second outlet section are respectively connected to the two ends of the heat exchange section. The second outlet section passes through the first inlet section, and the second inlet section passes through the first outlet section. or, The side wall of the third cavity is provided with an opening, through which the second inlet section extends, and the outer peripheral wall of the second inlet section is sealed to the inner wall of the opening.

8. The return air duct assembly of claim 6, wherein, The heat exchange section is formed by spiraling around the first end toward the second end.

9. A refrigeration system characterized by, The device includes a compressor, a condenser, an evaporator, and a return pipe assembly as described in any one of claims 1 to 8, wherein the compressor, the condenser, the capillary tube, the evaporator, and the return pipe are connected in sequence, and the return pipe is connected to the compressor to form a loop for refrigerant flow.

10. A refrigeration appliance characterised in that, The refrigeration system of claim 9, wherein the interior of the refrigeration appliance is provided with a compressor compartment and an insulation layer, and when the suction tube assembly is installed in the compressor compartment, the first end is disposed in a transverse direction toward the second end; and when the suction tube assembly is disposed in the insulation layer, the first end is disposed in a vertical direction toward the second end.

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