Refrigerant accumulator, thermal management system and vehicle

Abstract

The utility model provides a refrigerant energy accumulator, a heat management system and a vehicle, and relates to the technical field of heat management. The refrigerant energy accumulator comprises a shell and an inner cylinder assembly, the shell comprises an outer cylinder, a first end cover and a second end cover, the first end cover and the second end cover are arranged at openings in the two ends of the outer cylinder correspondingly, the first end cover is provided with a low-pressure refrigerant inlet and a high-pressure refrigerant outlet, and the second end cover is provided with a low-pressure refrigerant outlet and a high-pressure refrigerant inlet; the inner barrel assembly comprises an inner barrel body located in the outer barrel body and a heat exchange pipe, a first cavity is formed in the inner side of the inner barrel body, a second cavity is formed between the inner barrel body and the outer barrel body, the first cavity and the second cavity communicate with the low-pressure refrigerant inlet and the low-pressure refrigerant outlet correspondingly, and the heat exchange pipe is located in the second cavity; the two ends of the heat exchange pipe communicate with the high-pressure refrigerant inlet and the high-pressure refrigerant outlet correspondingly. According to the refrigerant energy accumulator provided by the invention, efficient heat exchange between a high-temperature refrigerant and a low-temperature refrigerant can be realized.

Description

Technical Field

[0001] The present application relates to the technical field of thermal management, and particularly to a refrigerant accumulator, a thermal management system, and a vehicle. Background Art

[0002] The refrigerant accumulator is crucial in the vehicle thermal management system. The refrigerant accumulator is used to store excess liquid refrigerant, balance the load of the thermal management system, and ensure a stable supply of refrigerant under different working conditions. With the complexity of the thermal management system, adding a heat exchanger can improve the energy efficiency coefficient of the thermal management system. By the cooperative work of the accumulator and the heat exchanger, energy loss can be reduced, and the overall efficiency of the thermal management system can be improved.

[0003] In the prior art, the heat exchanger is usually built into the accumulator, and the heat exchanger is directly or indirectly combined with the energy storage material in the accumulator to achieve heat exchange between the heat exchanger and the accumulator.

[0004] However, currently, the combined structure of the heat exchanger and the accumulator has a problem of low heat exchange efficiency, resulting in insufficient heat exchange amount between high and low temperature refrigerants. Summary of the Utility Model

[0005] The present application provides a refrigerant accumulator, a thermal management system, and a vehicle to solve the problem that the combined structure of the heat exchanger and the accumulator in the current situation has a low heat exchange efficiency, resulting in insufficient heat exchange amount between high and low temperature refrigerants.

[0006] To achieve the above object, the technical solution of the present application is as follows:

[0007] In a first aspect, the present application provides a refrigerant accumulator, including: a housing, including an outer cylinder, a first end cap, and a second end cap, the outer cylinder having openings at both ends along the axial direction, the first end cap and the second end cap being respectively disposed at the openings at both ends of the outer cylinder, the first end cap being provided with a low-pressure refrigerant inlet and a high-pressure refrigerant outlet, and the second end cap being provided with a low-pressure refrigerant outlet and a high-pressure refrigerant inlet; an inner cylinder assembly, including an inner cylinder and a heat exchange tube, the inner cylinder being located inside the outer cylinder, a first cavity being defined inside the inner cylinder, a second cavity being defined between the inner cylinder and the outer cylinder, the first cavity being communicated with the low-pressure refrigerant inlet, the second cavity being communicated with the low-pressure refrigerant outlet, an air flow channel being provided between the first cavity and the second cavity, the heat exchange tube being located in the second cavity, and both ends of the heat exchange tube being respectively communicated with the high-pressure refrigerant inlet and the high-pressure refrigerant outlet.

[0008] In a possible implementation manner, for the refrigerant accumulator provided by the present application, at least a part of the structure of the heat exchange tube spirally extends around the outer peripheral wall of the inner cylinder and forms a spiral structure.

[0009] In a possible implementation, for the refrigerant accumulator provided by the present application, the spiral structure includes a plurality of turns; the pitch between two adjacent turns is 6 mm - 15 mm; and / or, the number of turns is 4 - 10.

[0010] In a possible implementation, for the refrigerant accumulator provided by the present application, the inner cylinder assembly further includes: a flow guide vane, the extending direction of the flow guide vane is parallel to the extending direction of the spiral structure, and the flow guide vane covers the outside of the spiral structure, and the flow guide vane and the inner wall of the outer cylinder jointly define a gas flow channel.

[0011] In a possible implementation, for the refrigerant accumulator provided by the present application, the outer diameter of the heat exchange tube ranges from 4 mm to 8 mm; and / or, the wall thickness of the heat exchange tube ranges from 0.3 mm to 1 mm.

[0012] In a possible implementation, for the refrigerant accumulator provided by the present application, along the radial direction of the inner cylinder, at least part of the structure of the heat exchange tube is embedded in the outer wall of the inner cylinder; a sleeve is further sleeved on the outer wall of the inner cylinder, and the sleeve is located at the lower part of the inner cylinder.

[0013] In a possible implementation, for the refrigerant accumulator provided by the present application, a through hole is provided on the side wall of the inner cylinder, and the inner cylinder assembly further includes: an exhaust pipe, the exhaust pipe defines a gas flow channel, the exhaust pipe is provided with an air inlet and an exhaust outlet, the air inlet is located in the first cavity, and one end of the exhaust pipe provided with the exhaust outlet is inserted into the through hole.

[0014] In a possible implementation, for the refrigerant accumulator provided by the present application, the exhaust pipe includes a first pipe section, a second pipe section and a transition pipe section, at least part of the structures of the first pipe section and the second pipe section extend along the axial direction of the inner cylinder, the air inlet is located at one end of the first pipe section facing the first end cover, both ends of the transition pipe section are respectively connected to the second pipe section and one end of the first pipe section facing the second end cover, and the exhaust outlet is located at one end of the second pipe section away from the transition pipe section.

[0015] In a possible implementation, for the refrigerant accumulator provided by the present application, an oil return hole is provided on the transition pipe section.

[0016] In a possible implementation, for the refrigerant accumulator provided by the present application, a balance hole is provided at a position of the second pipe section adjacent to the exhaust outlet.

[0017] In a possible implementation, for the refrigerant accumulator provided by the present application, one end of the exhaust pipe provided with the air inlet includes a flared section, the inner side of the flared section defines the air inlet, and along the axial direction of the exhaust pipe and away from the inside of the exhaust pipe, the inner diameter of the flared section gradually increases.

[0018] In a possible implementation, for the refrigerant accumulator provided by the present application, the included angle between the inner wall of the flared section and the central axis of the flared section is 20° - 60°.

[0019] In a possible implementation, for the refrigerant accumulator provided by the present application, one end of the inner cylinder body facing the first end cap is provided with an opening, one end of the inner cylinder body facing the second end cap includes an end plate, and the inner cylinder assembly further includes: an inner cover body, the inner cover body is covered at the opening, a connecting pipe is provided on the inner cover body, and the connecting pipe is used to connect the low-pressure refrigerant inlet and the first cavity. There is a gap between the end plate and the second end cap, and the gap communicates the second cavity and the low-pressure refrigerant outlet.

[0020] In a possible implementation, for the refrigerant accumulator provided by the present application, a support protrusion is provided on one side of the second end cap facing the first end cap, and the support protrusion abuts against the end plate to define a gap between the end plate and the second end cap.

[0021] In a possible implementation, for the refrigerant accumulator provided by the present application, the heat exchange tube and the inner cylinder body are integrally die-cast.

[0022] In a possible implementation, for the refrigerant accumulator provided by the present application, the inner cylinder assembly further includes: a drying device, and the drying device is arranged in the first cavity to absorb moisture in the first cavity.

[0023] In a possible implementation, for the refrigerant accumulator provided by the present application, a filter element is further included, and the filter element is arranged at the low-pressure refrigerant outlet.

[0024] In a second aspect, the present application provides a thermal management system, including: a compressor, a condenser, an evaporator, a throttling device, and the above-mentioned refrigerant accumulator. The compressor, the condenser, the refrigerant accumulator, the throttling device, and the evaporator are connected in sequence to form a refrigeration circuit.

[0025] In a third aspect, the present application provides a vehicle, including: the above-mentioned thermal management system.

[0026] The refrigerant accumulator, thermal management system, and vehicle provided by the present application. The refrigerant accumulator includes a housing and an inner cylinder assembly. The housing includes an outer cylinder body and a first end cap and a second end cap covering the openings at both ends of the outer cylinder body. The first end cap is provided with a low-pressure refrigerant inlet and a high-pressure refrigerant outlet, and the second end cap is provided with a low-pressure refrigerant outlet and a high-pressure refrigerant inlet for allowing high- and low-temperature refrigerants to enter or flow out of the refrigerant accumulator. The inner cylinder assembly includes an inner cylinder body and a heat exchange tube. A first cavity is defined inside the inner cylinder body, and a second cavity is defined between the inner cylinder body and the outer cylinder body. The first cavity is connected to the low-pressure refrigerant inlet, and the second cavity is communicated with the low-pressure refrigerant outlet. An air flow channel is provided between the first cavity and the second cavity for the flow of low-temperature and low-pressure refrigerant. The heat exchange tube is located in the second cavity, and the low-temperature and low-pressure refrigerants in the first cavity and the second cavity and the high-temperature and high-pressure refrigerant in the heat exchange tube exchange heat efficiently through heat conduction, improving the heat exchange amount between the high- and low-temperature refrigerants. Description of the Drawings

[0027] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0028] Figure 1 It is a schematic exploded view of the refrigerant accumulator provided by the embodiment of the present application;

[0029] Figure 2 It is Figure 1 a partial structural schematic diagram of the inner cylinder assembly in

[0030] Figure 3 It is Figure 1 a structural schematic diagram of the first end cap in

[0031] Figure 4 It is Figure 1 a structural schematic diagram of the second end cap in

[0032] Figure 5 It is Figure 1 a structural schematic diagram of the exhaust pipe in

[0033] Figure 6 It is Figure 1 a structural schematic diagram of the inner cover body in

[0034] Figure 7 It is a structural schematic diagram of the refrigerant accumulator provided by the embodiment of the present application;

[0035] Figure 8 It is Figure 7 a cross-sectional view of the A-A section in

[0036] Figure 9 Another perspective schematic diagram of Figure 7 ;

[0037] Figure 10 Is Figure 9 The sectional view of the B-B section in

[0038] Figure 11 The connection schematic diagram of the thermal management system provided by the embodiment of the present application.

[0039] Explanation of reference numerals:

[0040] 10 - Refrigerant accumulator;

[0041] 100 - Outer shell;

[0042] 110 - Outer cylinder; 111 - Second cavity;

[0043] 120 - First end cap; 121 - Low-pressure refrigerant inlet; 122 - High-pressure refrigerant outlet;

[0044] 130 - Second end cap; 131 - Low-pressure refrigerant outlet; 132 - High-pressure refrigerant inlet; 133 - Support protrusion;

[0045] 140 - Gap;

[0046] 200 - Inner cylinder assembly;

[0047] 210 - Inner cylinder; 211 - First cavity; 212 - Through hole; 213 - Open end; 214 - End plate; 215: Sleeve;

[0048] 220 - Heat exchange tube; 221 - Spiral structure; 2211 - Spiral coil;

[0049] 230 - Flow guide vane;

[0050] 240 - Exhaust pipe; 241 - Air inlet; 242 - Exhaust port; 243 - First pipe section; 244 - Second pipe section; 2441 - Balance hole; 245 - Transition pipe section; 2451 - Oil return hole; 246 - Flared section;

[0051] 250 - Inner cover body; 251 - Connecting pipe;

[0052] 260 - Drying device;

[0053] 300 - Filter element;

[0054] 20 - Compressor;

[0055] 30 - Condenser;

[0056] 40 - Evaporator;

[0057] 50 - Throttle device.

[0058] Through the above - mentioned drawings, specific embodiments of the present application have been shown, and there will be a more detailed description hereinafter. These drawings and textual descriptions are not intended to limit the scope of the concept of the present application in any way, but to illustrate the concept of the present application to those skilled in the art by referring to specific embodiments. Detailed description of specific embodiments

[0059] To make the objectives, technical solutions, and advantages of the present application clearer, the technical solutions in the embodiments of the present application will be described in more detail below with reference to the drawings in the preferred embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all of the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present application without creative efforts shall fall within the scope of protection of the present application.

[0060] It should be noted that in the description of the embodiments of the present application, the terms indicating orientation or positional relationships such as "upper", "lower", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, and are only for the convenience of description, rather than indicating or implying that the device or component must have a specific orientation, be constructed and operated in a specific orientation, and thus cannot be construed as a limitation to the embodiments of the present application.

[0061] In addition, it should also be noted that the terms "first" and "second" are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, "a plurality" means two or more unless otherwise specifically defined.

[0062] In the present application, unless otherwise clearly specified and defined, terms such as "installation", "connection", "fixation", etc. should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection, an electrical connection, or a connection that can communicate with each other; it may be a direct connection, or an indirect connection through an intermediate medium, and may be the internal communication of two components or the interaction relationship between two components. For those of ordinary skill in the art, the specific meanings of the above - mentioned terms in the present application can be understood according to specific circumstances.

[0063] The refrigerant accumulator is crucial in the vehicle thermal management system. The refrigerant accumulator is used to store excess liquid refrigerant, balance the load of the thermal management system, and ensure a stable supply of refrigerant under different working conditions. As the thermal management system becomes more complex, adding a heat exchanger can improve the energy efficiency coefficient of the thermal management system. By the collaborative work of the accumulator and the heat exchanger, energy loss can be reduced and the overall efficiency of the thermal management system can be improved.

[0064] In the prior art, the heat exchanger is usually built into the accumulator, and the heat exchanger is directly or indirectly combined with the energy storage material in the accumulator to achieve heat exchange between the heat exchanger and the accumulator. However, the current combined structure of the heat exchanger and the accumulator has a problem of low heat exchange efficiency, resulting in insufficient heat exchange between high and low temperature refrigerants.

[0065] In view of this, the refrigerant accumulator, thermal management system and vehicle provided by this application. The refrigerant accumulator includes a housing and an inner cylinder assembly. The housing includes an outer cylinder body, a first end cover and a second end cover covering the openings at both ends of the outer cylinder body. The first end cover is provided with a low-pressure refrigerant inlet and a high-pressure refrigerant outlet, and the second end cover is provided with a low-pressure refrigerant outlet and a high-pressure refrigerant inlet for high and low temperature refrigerants to enter or flow out of the refrigerant accumulator. The inner cylinder assembly includes an inner cylinder body and a heat exchange tube. The inner side of the inner cylinder body defines a first cavity, and a second cavity is defined between the inner cylinder body and the outer cylinder body. The first cavity is connected to the low-pressure refrigerant inlet, and the second cavity is communicated with the low-pressure refrigerant outlet. There is an air flow channel between the first cavity and the second cavity for the low-temperature and low-pressure refrigerant to flow. The heat exchange tube is located in the second cavity. The low-temperature and low-pressure refrigerants in the first cavity and the second cavity and the high-temperature and high-pressure refrigerant in the heat exchange tube exchange heat efficiently through heat conduction, improving the heat exchange amount between the high and low temperature refrigerants.

[0066] The following will combine the drawings and specific embodiments to elaborate on this application in detail.

[0067] See Figures 1 to 4, this application provides a refrigerant accumulator 10, including: a housing 100, which includes an outer cylinder 110, a first end cap 120 and a second end cap 130. The outer cylinder 110 is provided with openings at both ends along the axial direction. The first end cap 120 and the second end cap 130 are respectively arranged at the openings at both ends of the outer cylinder 110. The first end cap 120 is provided with a low-pressure refrigerant inlet 121 and a high-pressure refrigerant outlet 122, and the second end cap 130 is provided with a low-pressure refrigerant outlet 131 and a high-pressure refrigerant inlet 132; an inner cylinder assembly 200, which includes an inner cylinder 210 and heat exchange tubes 220. The inner cylinder 210 is located inside the outer cylinder 110. A first cavity 211 is defined inside the inner cylinder 210, and a second cavity 111 is defined between the inner cylinder 210 and the outer cylinder 110. The first cavity 211 is communicated with the low-pressure refrigerant inlet 121, and the second cavity 111 is communicated with the low-pressure refrigerant outlet 131. An air flow channel is provided between the first cavity 211 and the second cavity 111. The heat exchange tubes 220 are located in the second cavity 111, and both ends of the heat exchange tubes 220 are respectively communicated with the high-pressure refrigerant inlet 132 and the high-pressure refrigerant outlet 122.

[0068] In some embodiments, the housing 100 provides structural support for the refrigerant accumulator 10 and plays a role in protecting the internal structure of the housing 100 and ensuring the sealing performance of the refrigerant accumulator 10. That is to say, the housing 100 can be made of materials with high strength to withstand the pressure changes inside the housing 100, prevent refrigerant leakage, and protect the internal structure of the housing 100 (such as the inner cylinder 210 and the heat exchange tubes 220) from the external environment, thereby ensuring the operation reliability of the refrigerant accumulator 10.

[0069] Furthermore, the housing 100 includes an outer cylinder 110, a first end cap 120 and a second end cap 130. The outer cylinder 110 is provided with openings at both ends along its axial direction, and each opening is closed by the first end cap 120 and the second end cap 130 respectively. That is to say, the first end cap 120 and the second end cap 130 are respectively covered on the openings, and then the first end cap 120 and the second end cap 130 are fixedly connected to the outer cylinder 110 by welding to seal the openings. The welded connection has the advantages of good connection sealing performance and large structural stiffness. Designed in this way, the sealing performance of the housing 100 is ensured.

[0070] Among them, the first end cap 120 has a low-pressure refrigerant inlet 121 and a high-pressure refrigerant outlet 122. Correspondingly, the second end cap 130 has a low-pressure refrigerant outlet 131 and a high-pressure refrigerant inlet 132.

[0071] It should be noted that the inner cylinder assembly 200 is used to realize the conversion and storage of the refrigerant. The inner cylinder assembly 200 includes an inner cylinder body 210 and heat exchange tubes 220. The inner cylinder body 210 is located in the inner space of the outer cylinder body 110. A second cavity 111 is formed between the inner cylinder body 210 and the outer cylinder body 110, and a first cavity 211 is provided inside the inner cylinder body 210. With such a design, the structural strength of the refrigerant accumulator 10 is improved, providing space for the storage and heat exchange of the refrigerant.

[0072] See Figures 7 to 10 , during operation, the low-temperature and low-pressure refrigerant enters the refrigerant accumulator 10 through the low-pressure refrigerant inlet 121. Part of the liquid low-temperature and low-pressure refrigerant sinks to the bottom of the first cavity 211 due to gravity. Part of the gaseous low-temperature and low-pressure refrigerant enters the second cavity 111 and exchanges heat with the high-temperature and high-pressure refrigerant, and then flows out of the refrigerant accumulator 10 through the low-pressure refrigerant outlet 131. The high-temperature and high-pressure refrigerant enters the heat exchange tubes 220 through the high-pressure refrigerant inlet 132. After exchanging heat with part of the liquid low-temperature and low-pressure refrigerant, part of the liquid low-temperature and low-pressure refrigerant evaporates into gaseous refrigerant and then flows out of the refrigerant accumulator 10. The high-temperature and high-pressure refrigerant flows out of the refrigerant accumulator 10 through the high-pressure refrigerant outlet 122 after heat exchange. In this way, the smooth conversion and storage of the refrigerant under different temperature and pressure states are realized.

[0073] Among them, the first cavity 211 is communicated with the low-pressure refrigerant inlet 121, ensuring that the low-temperature and low-pressure refrigerant can smoothly enter and accumulate in the first cavity 211. The second cavity 111 is connected to the low-pressure refrigerant outlet 131, providing a channel for the further flow and release of the refrigerant.

[0074] In specific implementation, the inner cylinder body 210 and the heat exchange tubes 220 can be integrally formed to improve the overall strength and sealing performance of the inner cylinder assembly 200. The inner cylinder body 210 and the heat exchange tubes 220 can also be connected by other connection methods, which are not limited in this embodiment. The heat exchange tubes 220 are located in the second cavity 111, and their two ends are respectively butted against the high-pressure refrigerant inlet 132 and the high-pressure refrigerant outlet 122, forming an efficient high-temperature and high-pressure refrigerant circulation loop. When the low-temperature and low-pressure refrigerant flows in the air flow channel, it can fully exchange heat with the high-temperature and high-pressure refrigerant in the heat exchange tubes 220 through heat conduction, thereby realizing the effective transfer and storage of energy. Thus, the high-efficiency heat exchange between the high-temperature and low-temperature refrigerants is realized through the inner cylinder body 210 and the heat exchange tubes 220, improving the heat exchange amount between the high-temperature and low-temperature refrigerants.

[0075] See Figure 8 , in the embodiment of the present application, at least part of the structure of the heat exchange tubes 220 spirally extends around the outer peripheral wall of the inner cylinder body 210 and forms a spiral structure 221.

[0076] It should be noted that by setting the spiral structure 221, the turbulent flow effect of the high-temperature and high-pressure refrigerant during the flow process is promoted. The high-temperature and high-pressure refrigerant continuously changes its flow direction within the spiral structure 221, increasing the contact area and collision frequency with the heat exchange tube 220, thereby improving the heat exchange efficiency between the low-temperature and low-pressure refrigerant and the high-temperature and high-pressure refrigerant. Among them, the turbulent flow effect helps to break the thermal boundary layer, reduce the thermal resistance, enabling heat to be transferred from the high-temperature and high-pressure refrigerant to the low-temperature and low-pressure refrigerant more quickly.

[0077] See Figure 8 and Figure 10 , in the embodiment of the present application, the spiral structure 221 includes a plurality of turns 2211; the pitch between two adjacent turns 2211 is 6 mm - 15 mm; and / or, the number of turns 2211 is 4 - 10.

[0078] In specific implementation, if the pitch between two adjacent turns 2211 is too large, it will cause the flow path of the high-temperature and high-pressure refrigerant in the spiral structure 221 to become longer and the flow velocity to slow down. For example, when the pitch is greater than 15 mm, the pitch is too large, resulting in insufficient heat exchange between the high- and low-temperature refrigerants and a decrease in the heat exchange efficiency. At the same time, the too-long flow path may also increase the refrigerant pressure drop and affect the operating stability of the refrigerant accumulator 10. While if the pitch between two adjacent turns 2211 is too small, it will cause an increase in the flow resistance of the high-temperature and high-pressure refrigerant, thereby increasing the energy consumption of the refrigerant accumulator 10, such as when the pitch is less than 6 mm. Therefore, the pitch between two adjacent turns 2211 can be 7 mm, 8 mm, 10 mm, 12 mm, etc. Of course, this embodiment is not limited thereto. In this way, the pitch balances the flow velocity and heat exchange time of the high-temperature and high-pressure refrigerant, thereby improving the heat exchange efficiency and increasing the heat exchange amount between the high- and low-temperature refrigerants. At the same time, setting the pitch between 6 mm - 15 mm helps to reduce the pressure drop of the high-temperature and high-pressure refrigerant in the spiral structure 221 and maintain the stability and efficiency of the operation of the refrigerant accumulator 10.

[0079] In some embodiments, if the number of turns 2211 is too large, it will increase the flow resistance and pressure drop of the high-temperature and high-pressure refrigerant in the spiral structure 221. In this way, it will increase the energy consumption of the refrigerant accumulator 10 and also affect the flow stability of the high-temperature and high-pressure refrigerant. Correspondingly, if the number of turns 2211 is too small, it will result in too small a heat exchange area, a decrease in the heat exchange efficiency, and a reduction in the heat exchange amount between the high- and low-temperature refrigerants. Therefore, the number of turns 2211 can be 5, 7, 8, etc. Of course, this embodiment is not limited thereto. Thus, while ensuring there is sufficient heat exchange area to achieve efficient heat exchange, it helps to maintain the flow stability of the high-temperature and high-pressure refrigerant and keep the pressure drop within a reasonable range, reducing the energy consumption and failure risk of the refrigerant accumulator 10.

[0080] See Figure 2, in the embodiment of the present application, the inner cylinder assembly 200 further includes: a deflector 230, the extending direction of the deflector 230 is parallel to the extending direction of the spiral structure 221, and the deflector 230 is wrapped around the outside of the spiral structure 221. The deflector 230 and the inner wall of the outer cylinder 110 jointly define a gas guiding flow path.

[0081] Among them, the deflector 230 is tightly wrapped around the outside of the spiral structure 221 and forms a gas guiding flow path with the inner wall of the outer cylinder 110. The gas guiding flow path can be a spiral flow cavity. With such a design, the contact area between the low-pressure and low-temperature refrigerant and the heat exchange tube 220 is increased, the flow path length of the low-temperature and low-pressure refrigerant is increased, and the orderly flow of the low-pressure and low-temperature refrigerant in the gas guiding flow path is also guided, so that the heat exchange time between the low-pressure and low-temperature refrigerant and the heat exchange tube 220 is extended. Therefore, the heat exchange efficiency is significantly improved, and the heat exchange amount between the high-temperature and low-temperature refrigerants is further increased.

[0082] In the embodiment of the present application, the outer diameter of the heat exchange tube 220 ranges from 4 mm to 8 mm; and / or, the wall thickness of the heat exchange tube 220 ranges from 0.3 mm to 1 mm.

[0083] It should be noted that, for example, if the outer diameter of the heat exchange tube 220 is greater than 8 mm, the outer diameter is too large, which will cause an increase in flow resistance and reduce the operating performance of the refrigerant accumulator 10. When the outer diameter of the heat exchange tube 220 is less than 4 mm, the outer diameter is too small, which will cause insufficient heat exchange area and affect the heat exchange efficiency. Therefore, the outer diameter of the heat exchange tube 220 can be 5 mm, 6 mm, 7 mm, etc. Of course, this embodiment is not limited here. In this way, it can be ensured that the heat exchange tube 220 has a sufficient heat exchange area, so that the high-temperature and low-temperature refrigerants can fully exchange heat through the heat exchange tube 220, thereby improving the heat exchange efficiency of the refrigerant accumulator 10. At the same time, it helps to reduce the flow resistance of the high-temperature and high-pressure refrigerant in the heat exchange tube 220, maintain the stable flow state of the high-temperature and high-pressure refrigerant, and reduce the energy consumption of the refrigerant accumulator 10.

[0084] It should also be noted that when the wall thickness of the heat exchange tube 220 is set to be greater than 1 mm, the wall thickness is too thick, which will cause a decrease in the thermal conductivity of the heat exchange tube 220 and thus affect the heat exchange efficiency. When the wall thickness of the heat exchange tube 220 is set to be less than 0.3 mm, the wall thickness is too thin, which will cause insufficient strength of the heat exchange tube 220 and it is easy to be damaged due to internal pressure or external impact, thus affecting the operating stability and safety of the refrigerant accumulator 10. Therefore, the wall thickness of the heat exchange tube 220 can be 0.4 mm, 0.6 mm, 0.8 mm, etc. Of course, this embodiment is not limited here. In this way, it can be ensured that the heat exchange tube 220 has good thermal conductivity, so that the high-temperature and low-temperature refrigerants can exchange heat efficiently. At the same time, it can be ensured that the heat exchange tube 220 has sufficient strength and stiffness to withstand internal pressure and external environmental impacts.

[0085] SeeFigure 2 and Figure 8 In the embodiment of the present application, at least part of the structure of the heat exchange tube 220 is embedded in the outer wall of the inner cylinder 210 along the radial direction of the inner cylinder 210;

[0086] A sleeve 215 is further sleeved on the outer wall of the inner cylinder 210, and the sleeve 215 is located at the lower part of the inner cylinder 210.

[0087] In the present application, embedding at least part of the heat exchange tube 220 in the outer wall of the inner cylinder 210 can save the space inside the outer shell 100 compared with sleeving the heat exchange tube 220 outside the inner cylinder 210, making the overall structure more compact.

[0088] It can be understood that when using heat exchange tubes 220 of the same specification, embedding at least part of the heat exchange tube 220 in the outer wall of the inner cylinder 210 results in a larger volume of the inner cylinder 210 compared with sleeving it outside the inner cylinder 210. Thus, the liquid storage capacity of the refrigerant can be improved.

[0089] See Figure 2 and Figure 5 In the embodiment of the present application, a through hole 212 is formed in the side wall of the inner cylinder 210. The inner cylinder assembly 200 further includes an exhaust pipe 240. The exhaust pipe 240 defines an air flow channel. The exhaust pipe 240 is provided with an air inlet 241 and an air outlet 242. The air inlet 241 is located in the first cavity 211, and one end of the exhaust pipe 240 provided with the air outlet 242 is inserted into the through hole 212.

[0090] Specifically, the inner cylinder assembly 200 further includes an exhaust pipe 240. The exhaust pipe 240 can be an aluminum pipe fitting. The exhaust pipe 240 is located in the first cavity 211. An air flow channel is provided inside the exhaust pipe 240, ensuring that the gaseous low-temperature and low-pressure refrigerant can flow smoothly along the air flow channel inside the exhaust pipe 240. The air inlet 241 of the exhaust pipe 240 is located in the first cavity 211, enabling the exhaust pipe 240 to be directly connected to the gas environment inside the inner cylinder 210, effectively capturing and guiding the gaseous low-temperature and low-pressure refrigerant to enter the exhaust pipe 240 through the air inlet 241. The air outlet 242 is provided at the other end of the exhaust pipe 240, and this end is inserted into the through hole 212 in the side wall of the inner cylinder 210, thereby realizing the transfer of the gaseous low-temperature and low-pressure refrigerant from the inside of the inner cylinder 210 to the outside of the inner cylinder 210.

[0091] It should be noted that the exhaust pipe 240 functions as a gas-liquid separator. That is to say, when the low-temperature and low-pressure refrigerant enters the first cavity 211 through the low-pressure refrigerant inlet 121, due to the action of gravity, part of the liquid low-temperature and low-pressure refrigerant sinks to the bottom of the first cavity 211 and is stored therein, while part of the gaseous low-temperature and low-pressure refrigerant enters the exhaust pipe 240 through the air inlet 241, and then enters the second cavity 111 through the exhaust port 242. The gaseous low-temperature and low-pressure refrigerant sinks and flows in the second cavity 111, and exchanges heat further through the gas flow channel formed by the guide vane 230 and the inner wall of the outer cylinder 110, and finally flows out of the refrigerant accumulator 10 through the low-pressure refrigerant outlet 131.

[0092] In addition, a sleeve 215 is sleeved on the outer wall of the inner cylinder 210. In this way, when the gaseous low-temperature and low-pressure refrigerant exchanges heat with the high-temperature and high-pressure refrigerant through the gas flow channel and flows towards the low-pressure refrigerant outlet 131, through the isolation of the sleeve 215, the gaseous low-temperature and low-pressure refrigerant is separated from the outer wall of the inner cylinder 210, preventing the gaseous low-temperature and low-pressure refrigerant after heat exchange from being cooled by the inner cylinder 210.

[0093] It should be noted that the sleeve 215 can be made of plastic or other materials with low thermal conductivity, which is not limited in this embodiment. The purpose is to isolate the low-temperature and low-pressure refrigerant in the gas flow channel from the outer wall of the inner cylinder 210.

[0094] See Figure 5 , in the embodiment of the present application, the exhaust pipe 240 includes a first pipe section 243, a second pipe section 244 and a transition pipe section 245. At least part of the structures of the first pipe section 243 and the second pipe section 244 extend along the axial direction of the inner cylinder 210. The air inlet 241 is located at one end of the first pipe section 243 facing the first end cover 120. The two ends of the transition pipe section 245 are respectively connected to the second pipe section 244 and one end of the first pipe section 243 facing the second end cover 130. The exhaust port 242 is located at one end of the second pipe section 244 away from the transition pipe section 245.

[0095] Among them, at least part of the structure of the first pipe section 243 extends along the axial direction of the inner cylinder 210. In this way, the air inlet 241 can directly face the first end cover 120, so that the air inlet 241 can directly suck the gaseous low-temperature and low-pressure refrigerant from the first cavity 211, so that the gaseous low-temperature and low-pressure refrigerant can smoothly enter the second cavity 111 through the exhaust pipe 240.

[0096] Furthermore, the transition pipe section 245 is used to connect the first pipe section 243 and the second pipe section 244, and its two ends are respectively connected to the first pipe section 243 and the second pipe section 244. With such a design, it can ensure that the gaseous low-temperature and low-pressure refrigerant smoothly changes the flow direction between the first pipe section 243 and the second pipe section 244, reduces the flow resistance, and improves the exhaust efficiency.

[0097] It is understandable that at least a part of the structure of the second pipe section 244 also extends along the axial direction of the inner cylinder 210, and the exhaust port 242 is located at one end of the second pipe section 244 away from the transition pipe section 245. In this way, it is ensured that after the gaseous low-temperature and low-pressure refrigerant passes through the entire exhaust pipe 240, it can smoothly discharge from the exhaust port 242, avoiding the phenomenon of the gaseous low-temperature and low-pressure refrigerant staying or flowing back.

[0098] See Figure 5 , in the embodiment of the present application, an oil return hole 2451 is provided on the transition pipe section 245.

[0099] It should be noted that during operation, a small amount of compressor lubricating oil is carried in the low-temperature and low-pressure refrigerant. The lubricating oil is stored at the bottom of the first cavity 211 together with the liquid low-temperature and low-pressure refrigerant. Then, the lubricating oil and a small amount of liquid low-temperature and low-pressure refrigerant enter the exhaust pipe 240 through the oil return hole 2451, and follow the gaseous low-temperature and low-pressure refrigerant into the second cavity 111. The liquid low-temperature and low-pressure refrigerant exchanges heat with the high-temperature and high-pressure refrigerant and evaporates into a gaseous refrigerant. The lubricating oil flows out of the refrigerant accumulator 10 with the gaseous refrigerant and returns to the compressor.

[0100] See Figure 5 , in the embodiment of the present application, a balance hole 2441 is provided at a position of the second pipe section 244 adjacent to the exhaust port 242.

[0101] Among them, the balance hole 2441 can prevent the liquid refrigerant from entering the compressor due to pressure imbalance when the compressor starts. Thus, the stability of the overall operation is ensured.

[0102] See Figure 5 , in the embodiment of the present application, one end of the exhaust pipe 240 where the air inlet 241 is provided includes a flared section 246. The inner side of the flared section 246 defines the air inlet 241. Along the axial direction of the exhaust pipe 240 and away from the inside of the exhaust pipe 240, the inner diameter of the flared section 246 gradually increases.

[0103] Specifically, by providing the flared section 246, it is ensured that the gaseous refrigerant can accurately enter the inside of the exhaust pipe 240, reducing the flow resistance of the gaseous refrigerant.

[0104] Furthermore, along the axial direction of the exhaust pipe 240, the flared section 246 is arranged in a gradually expanding structure. Specifically, starting from the position where the air inlet 241 is located, along the direction away from the inside of the exhaust pipe 240, the inner diameter of the flared section 246 gradually increases. Such a setting enables the gaseous refrigerant to be distributed more evenly after entering the exhaust pipe 240, reducing the vortex and turbulence phenomena caused by uneven flow velocity.

[0105] See Figure 5, in the embodiment of the present application, the angle between the inner wall of the flared section 246 and the central axis of the flared section 246 is 20° - 60°.

[0106] It should be noted that if the angle between the inner wall of the flared section 246 and the central axis of the flared section 246 is too large, it will cause unstable flow of the gaseous refrigerant, increasing the risk of eddy currents and turbulence. If the angle is too small, the jet effect of the flared section 246 will be weakened, and the flow resistance of the gaseous refrigerant will be increased. Therefore, the angle can be 25°, 30°, 45°, etc. Of course, this embodiment is not limited here. In this way, the flow resistance of the gaseous refrigerant is effectively reduced, while helping to maintain the stability of the gaseous refrigerant, reducing the formation of eddy currents and turbulence, thereby improving the operating efficiency of the refrigerant accumulator 10.

[0107] See Figure 1 , Figure 6 and Figure 8 , in the embodiment of the present application, one end of the inner cylinder 210 facing the first end cap 120 is provided with an opening 213, one end of the inner cylinder 210 facing the second end cap 130 includes an end plate 214, and the inner cylinder assembly 200 further includes: an inner cover 250, the inner cover 250 is covered at the opening 213, and a connecting pipe 251 is provided on the inner cover 250, and the connecting pipe 251 is used to connect the low-pressure refrigerant inlet 121 and the first cavity 211. There is a gap 140 between the end plate 214 and the second end cap 130, and the gap 140 communicates the second cavity 111 and the low-pressure refrigerant outlet 131.

[0108] In some embodiments, one end of the inner cylinder 210 facing the first end cap 120 is designed as an opening 213. In order to close the opening 213 and ensure the sealing performance of the refrigerant accumulator 10, the inner cylinder assembly 200 further includes an inner cover 250, and the inner cover 250 is covered on the opening 213 to achieve the sealing of the opening 213. Further, through the connecting pipe 251 provided on the inner cover 250, the communication between the low-pressure refrigerant inlet 121 and the first cavity 211 is realized, so that the refrigerant can smoothly enter the interior of the inner cylinder 210 for subsequent refrigeration cycles.

[0109] In addition, an end plate 214 is provided at one end of the inner cylinder 210 facing the second end cap 130. The end plate 214 serves as the closed end of the inner cylinder 210, and a gap 140 is maintained between the end plate 214 and the second end cap 130. With this setting, the second cavity 111 and the low-pressure refrigerant outlet 131 are effectively connected. During operation, the refrigerant after heat exchange and pressure change will flow out smoothly through this gap 140 and finally flow out of the refrigerant accumulator 10 through the low-pressure refrigerant outlet 131. Thus, the flow path of the refrigerant is optimized, and the overall efficiency and reliability of the refrigerant accumulator 10 are improved.

[0110] It can be understood that the inner cover body 250 can be made of plastic material. Of course, the material of the inner cover body 250 can be set according to actual needs, and this embodiment does not limit it here.

[0111] See Figure 4 and Figure 8 In the embodiment of the present application, on the side of the second end cover 130 facing the first end cover 120, there is provided a support convex portion 133, and the support convex portion 133 abuts against the end plate 214, so as to define a gap 140 between the end plate 214 and the second end cover 130.

[0112] Among them, the support convex portion 133 tightly abuts against the end plate 214 of the inner cylinder body 210 to form a stable support, and forms a gap 140 between the end plate 214 and the second end cover 130, ensuring the communication between the second cavity 111 and the low-pressure refrigerant outlet 131. The support convex portion 133 enhances the structural strength, and also optimizes the refrigerant flow path through the formed gap 140, improving the overall efficiency and stability of the refrigerant accumulator 10.

[0113] In the embodiment of the present application, the heat exchange tube 220 and the inner cylinder body 210 are integrally die-cast.

[0114] It should be noted that the integral die-casting makes the heat exchange tube 220 and the inner cylinder body 210 closely combined. Thus, the heat exchange tube 220 is seamlessly embedded on the inner cylinder body 210, forming a stable and efficient heat exchange structure. The heat exchange tube 220 and the inner cylinder body 210 are integrally die-cast, simplifying the production process, improving the production efficiency, and also ensuring the high-strength connection between the heat exchange tube 220 and the inner cylinder body 210, reducing the risk of thermal resistance that may be generated at the joint, thereby optimizing the heat exchange performance of the refrigerant accumulator 10 and extending the service life of the refrigerant accumulator 10.

[0115] See Figure 1 and Figure 8 In the embodiment of the present application, the inner cylinder assembly 200 further includes: a drying device 260, and the drying device 260 is arranged in the first cavity 211 to absorb moisture in the first cavity 211.

[0116] Specifically, the drying device 260 is installed in the internal space of the first cavity 211, ensuring that the drying device 260 can directly act on the target area, that is, the inside of the first cavity 211. It also utilizes the internal space of the inner cylinder assembly 200, avoiding additional occupation of external space and making the overall structure more compact.

[0117] Furthermore, the main function of the drying device 260 lies in its high moisture absorption capacity. The drying device 260 can effectively absorb and remove the excess moisture in the first cavity 211 through various forms such as physical adsorption, chemical absorption, or thermal desorption. This embodiment does not limit it here.

[0118] See Figure 1 Figure 1 , in the embodiment of the present application, a filter member 300 is further included, and the filter member 300 is disposed at the low-pressure refrigerant outlet 131.

[0119] Among them, the low-pressure refrigerant outlet 131 serves as an outflow node in the low-temperature and low-pressure refrigerant cycle, and the quality of the outflowing refrigerant will affect the working efficiency of subsequent operations. By arranging the filter member 300 at the low-pressure refrigerant outlet 131, it is possible to effectively intercept and remove adverse factors such as tiny impurities, particulate matter, or oil stains that may be carried in the refrigerant.

[0120] It can be understood that the filter member 300 can be set as a filter net, and the material, mesh density, etc. of the filter net are set according to actual needs to ensure that the filter member 300 can efficiently filter impurities and maintain a low flow resistance to avoid hindering the flow of the refrigerant. In addition, the filter member 300 can be injection-molded and connected to the second end cap 130.

[0121] The following describes the thermal management system according to the second aspect embodiment of the present application.

[0122] See Figure 11 Figure 11 , in the embodiment of the present application, the thermal management system includes: a compressor 20, a condenser 30, an evaporator 40, a throttling device 50, and the above-mentioned refrigerant accumulator 10. The compressor 20, the condenser 30, the refrigerant accumulator 10, the throttling device 50, and the evaporator 40 are sequentially connected in communication to form a refrigeration circuit.

[0123] Among them, the compressor 20 is connected in communication with the low-pressure refrigerant outlet 131, the condenser 30 is connected in communication with the high-pressure refrigerant inlet 132, the throttling device 50 is connected in communication with the high-pressure refrigerant outlet 122, and the evaporator 40 is connected in communication with the low-pressure refrigerant inlet 121.

[0124] Specifically, the high-temperature and high-pressure refrigerant flows out of the compressor 20, enters the condenser 30, exchanges heat with the cooling medium in the condenser 30, then enters the refrigerant accumulator 10, and then passes through the throttling device 50 to be depressurized into a gas-liquid two-phase low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant enters the evaporator 40 to evaporate and absorb heat. The evaporated low-temperature and low-pressure refrigerant enters the refrigerant accumulator 10 again, flows through the gas guide channel formed by the second cavity 111 and the guide vane 230 to exchange heat with the high-temperature and high-pressure refrigerant in the heat exchange tube 220, and then the temperature rises. Then it flows out of the refrigerant accumulator 10 and returns to the compressor 20 to complete a refrigeration cycle.

[0125] The following describes the vehicle according to the third aspect embodiment of the present application.

[0126] The vehicle of this embodiment can be a new energy vehicle or a hybrid vehicle. Of course, this embodiment is not limited here. The vehicle may include: a vehicle body and the thermal management system of the above embodiment, and the thermal management system is provided on the vehicle body.

[0127] Finally, it should be noted that: the above embodiments are only used to illustrate the technical solutions of the present application, rather than limiting them; although the present application has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that: it is still possible to modify the technical solutions recorded in the foregoing embodiments, or perform equivalent replacements on some or all of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present application.

Claims

1. A refrigerant accumulator, characterized in that: include: The outer shell comprises an outer cylinder, a first end cover and a second end cover, the outer cylinder is provided with openings at both ends along the axial direction, the first end cover and the second end cover are respectively provided at the openings at both ends of the outer cylinder, the first end cover is provided with a low-pressure refrigerant inlet and a high-pressure refrigerant outlet, and the second end cover is provided with a low-pressure refrigerant outlet and a high-pressure refrigerant inlet; The inner cylinder assembly includes an inner cylinder body and a heat exchange tube, the inner cylinder body is located on the inner side of the outer cylinder body, the inner side of the inner cylinder body defines a first cavity, a second cavity is defined between the inner cylinder body and the outer cylinder body, the first cavity is connected to the low-pressure refrigerant inlet, the second cavity is connected to the low-pressure refrigerant outlet, an air flow channel is provided between the first cavity and the second cavity, the heat exchange tube is located in the second cavity, and both ends of the heat exchange tube are respectively connected to the high-pressure refrigerant inlet and the high-pressure refrigerant outlet.

2. The refrigerant accumulator according to claim 1, characterized in that At least a portion of the heat exchange tube extends spirally around the outer peripheral wall of the inner cylinder to form a spiral structure.

3. The refrigerant accumulator according to claim 2, characterized in that The spiral structure includes a plurality of spiral coils; The pitch between two adjacent spiral coils is 6 mm to 15 mm; and / or, The number of the spiral coils is 4-10.

4. The refrigerant accumulator according to claim 2, characterized in that The inner cylinder assembly further includes a guide vane, the extension direction of which is parallel to the extension direction of the spiral structure and covers the outer side of the spiral structure. The guide vane and the inner wall of the outer cylinder together define an air guide channel.

5. The refrigerant accumulator according to claim 1, characterized in that The outer diameter of the heat exchange tube is in the range of 4 mm to 8 mm; and / or the wall thickness of the heat exchange tube is in the range of 0.3 mm to 1 mm.

6. The refrigerant accumulator according to claim 1, characterized in that Along the radial direction of the inner cylinder, at least a portion of the heat exchange tube is embedded in the outer wall of the inner cylinder; A sleeve is also sleeved on the outer wall of the inner cylinder, and the sleeve is located at the lower part of the inner cylinder.

7. The refrigerant accumulator according to claim 1, characterized in that The side wall of the inner cylinder is provided with a through hole, and the inner cylinder assembly further comprises: An exhaust pipe defines the airflow channel, the exhaust pipe is provided with an air inlet and an exhaust port, the air inlet is located in the first cavity, and one end of the exhaust pipe provided with the exhaust port is inserted into the through hole.

8. The refrigerant accumulator according to claim 7, characterized in that The exhaust pipe comprises a first pipe section, a second pipe section and a transition pipe section, wherein at least a portion of the first pipe section and the second pipe section respectively extend along the axial direction of the inner cylinder. The air inlet is located at one end of the first pipe segment facing the first end cover, the two ends of the transition pipe segment are respectively connected to the second pipe segment and one end of the first pipe segment facing the second end cover, and the exhaust port is located at one end of the second pipe segment away from the transition pipe segment.

9. The refrigerant accumulator according to claim 8, characterized in that The transition pipe section is provided with an oil return hole.

10. The refrigerant accumulator according to claim 8, characterized in that A balancing hole is provided at a position of the second pipe section adjacent to the exhaust port.

11. The refrigerant accumulator according to claim 7, characterized in that The end of the exhaust pipe provided with the air inlet includes a flared section, and the inner side of the flared section defines the air inlet. Along the axial direction of the exhaust pipe and in a direction away from the interior of the exhaust pipe, the inner diameter of the expansion section gradually increases.

12. The refrigerant accumulator according to claim 11, characterized in that The angle between the inner wall of the expansion section and the central axis of the expansion section is 20°-60°.

13. The refrigerant accumulator according to any one of claims 1 to 12, characterized in that: The end of the inner cylinder facing the first end cover is provided with an opening, and the end of the inner cylinder facing the second end cover includes an end plate. The inner cylinder assembly also includes: an inner cover body, which is covered at the open position, and a connecting pipe is provided on the inner cover body, and the connecting pipe is used to connect the low-pressure refrigerant inlet and the first cavity. There is a gap between the end plate and the second end cover, and the gap connects the second cavity and the low-pressure refrigerant outlet.

14. The refrigerant accumulator according to claim 13, characterized in that A supporting protrusion is provided on a side of the second end cover facing the first end cover, and the supporting protrusion abuts against the end plate, so that the gap is defined between the end plate and the second end cover.

15. The refrigerant accumulator according to any one of claims 1 to 12, characterized in that: The heat exchange tube and the inner cylinder are integrally die-cast.

16. The refrigerant accumulator according to any one of claims 1 to 12, characterized in that: The inner cylinder assembly further includes a drying device, which is disposed in the first cavity to absorb moisture in the first cavity.

17. The refrigerant accumulator according to any one of claims 1 to 12, characterized in that: It also includes a filter element, which is arranged at the low-pressure refrigerant outlet.

18. A thermal management system, characterized in that: include: A compressor, a condenser, an evaporator, a throttling device and a refrigerant accumulator according to any one of claims 1 to 17, wherein the compressor, the condenser, the refrigerant accumulator, the throttling device and the evaporator are connected in sequence to form a refrigeration circuit.

19. A vehicle, characterized in that: include: The thermal management system of claim 18.

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