Car refrigerator

Abstract

To improve temperature uniformity in the cooling chamber of a vehicle refrigerator and enhance heat exchange efficiency. [Solution] The in-vehicle refrigerator includes a housing provided with a spaced-apart cooling chamber and a first storage chamber, a first evaporator provided in the first storage chamber, a first fan provided in the first storage chamber and including a first air intake and a first air outlet communicating with the cooling chamber, and an air duct assembly provided in the first storage chamber and extending from the first air intake to the cooling chamber, with a first end connected to the cooling chamber and a second end connected to the first air intake. The first fan forms a circulating airflow, generating heat exchange by forced convection between the air near the walls of the housing and the air in the center of the cooling chamber. This conducts the cold heat from the walls of the housing to the center of the cooling chamber more quickly, improving the temperature uniformity of the refrigerator's cooling chamber.

Description

Technical Field

[0001] This application relates to the technical field of refrigerators, particularly to in-vehicle refrigerators.

Background Art

[0002] Conventional in-vehicle refrigerators are basically mainly direct cooling. Since the evaporator used in a direct-cooling in-vehicle refrigerator is directly attached and fixed to the inner wall of the housing, the refrigeration speed near the wall surface of the housing is much faster than the central position of the internal space of the housing, resulting in uneven refrigeration inside the in-vehicle refrigerator. Moreover, since the heat exchange method of a direct-cooling refrigerator is heat exchange by natural convection, the heat exchange efficiency is low and the refrigeration speed is slow.

Summary of the Invention

Problems to be Solved by the Invention

[0003] This application provides an in-vehicle refrigerator to solve the technical problems in a conventional direct-cooling in-vehicle refrigerator, where the heat exchange efficiency of heat exchange by natural convection is low, the refrigeration speed near the wall surface of the housing is much faster than the central position of the internal space of the housing, resulting in a slow refrigeration speed and uneven refrigeration.

Means for Solving the Problems

[0004] In a first aspect, the in-vehicle refrigerator according to this application includes a housing provided with a cooling chamber and a first accommodation chamber arranged separately, a first evaporator provided in the first accommodation chamber and capable of heat exchange with the wall surface of the housing to form cold air in the cooling chamber, a first fan provided in the first accommodation chamber, including a first air inlet and a first air outlet communicating with the cooling chamber, an air duct assembly provided in the first accommodation chamber and including a duct extending from the first air inlet to the cooling chamber, with a first end communicating with the cooling chamber and a second end communicating with the first air inlet, The first fan sends a high-speed airflow into the cooling chamber, and the cold air in the cooling chamber is driven to flow from the second end of the duct to the first fan before flowing into the cooling chamber, thereby creating a circulating airflow within the vehicle refrigerator.

[0005] In one possible implementation, a first ventilation opening is provided at the first end of the duct, and a second intake opening is provided in the housing that communicates with the cooling chamber, and the first ventilation opening communicates with the second intake opening, The first fan includes a case and an impeller, the impeller being housed in a case with a first air intake, and the second end of the duct having a second ventilation opening that communicates with the first air intake. The case is provided with a first air outlet, and the housing is provided with a second air outlet that communicates with the cooling chamber, with the second air outlet communicating with the first air outlet.

[0006] In one possible implementation, the second air intake and the second air outlet are positioned opposite each other horizontally.

[0007] In one possible implementation, the case is provided with a first groove, the second end of the duct is fitted into the first groove, and the first air intake is provided in the first groove.

[0008] In one possible implementation, a first wall is provided on the side of the impeller case that is close to the impeller, and a second wall is provided on the side of the case that is close to the impeller. There is a gap between the first and second walls, and the numerical range of this gap is 0.5 mm to 3.5 mm.

[0009] In one possible implementation, a third air intake is provided on the first wall, the first air intake is provided on the second wall and communicates with the third air intake, and a plurality of third outlets are provided on the circumferential side of the impeller, uniformly arranged in the circumferential direction of the impeller, the third outlets communicate with the first outlets.

[0010] In one possible implementation, the case is provided with a baffle, the baffle covering the orthographic projection of the impeller in the vertical plane with its orthographic projection portion in the vertical plane. In one possible implementation, there are multiple first outlets and multiple second outlets, with a one-to-one correspondence between the multiple second outlets and the multiple first outlets.

[0011] In one possible implementation, the air duct assembly further includes a first ventilation grille provided at a first ventilation opening, and / or a second ventilation grille provided at a first outlet of the case.

[0012] In one possible implementation, the air duct assembly further includes a second evaporator located within the duct so that when the first fan is operating, the airflow within the duct and the second evaporator exchange heat.

[0013] In one possible implementation, a heat-insulating layer is provided within the first containment chamber, surrounding the cooling chamber.

[0014] The above-described technical means according to the embodiment of the present application has the following advantages compared to the prior art.

[0015] In the vehicle-mounted refrigerator according to the embodiment of the present invention, when the first fan is operating, it can stably generate a high-pressure, high-speed airflow. The high-speed airflow enters the cooling chamber from the first outlet of the first fan, and the cold air from the cooling chamber flows from the second end of the duct to the first fan before flowing into the cooling chamber, thereby forming a circulating airflow within the vehicle-mounted refrigerator. During the airflow circulation process, heat exchange occurs between the heat load and the cold air, causing a decrease in temperature. Heat conduction also occurs between the first evaporator and the wall surface of the housing, and the cold heat from the first evaporator is transferred to the wall surface of the housing. Forced convection heat exchange occurs between the air near the wall surface of the housing and the air in the center of the cooling chamber. As a result, the cold heat from the wall surface of the housing is conducted to the center of the cooling chamber more quickly, rapidly lowering the temperature in the center of the cooling chamber. This improves the temperature uniformity of the refrigerator's cooling chamber, accelerates the freezing speed, and improves the heat exchange efficiency.

[0016] Here, the drawings are incorporated into the specification and form a part of the specification, showing embodiments consistent with the present application and explaining the principles of the present application together with the specification.

[0017] To more clearly explain the technical means in the embodiments of the present application or the prior art, the drawings necessary for the description of the embodiments or the prior art will be briefly described below. Obviously, those skilled in the art can obtain other drawings based on these drawings without creative labor.

[0018] One or more embodiments are exemplarily illustrated by the figures in the corresponding drawings. These exemplary descriptions do not limit the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. Unless otherwise specified, the figures in the drawings do not limit the proportions.

Brief Description of the Drawings

[0019] [Figure 1] It is a schematic configuration diagram of an in-vehicle refrigerator according to an embodiment of the present application. [Figure 2] It is a front view of the in-vehicle refrigerator shown in FIG. 1. [Figure 3] It is a cross-sectional view taken along the A-A direction of FIG. 2. [Figure 4] It is a schematic diagram of the operating state of the in-vehicle refrigerator shown in FIG. 1. Here, the cover is not shown, and the direction of the arrow is the direction of the airflow. [Figure 5] It is an enlarged schematic view of part B of FIG. 4. [Figure 6] It is a schematic configuration diagram of the air duct assembly of the in-vehicle refrigerator shown in FIG. 1. [Figure 7] It is a schematic assembly diagram of the air duct assembly and the first fan of the in-vehicle refrigerator shown in FIG. 1. [Figure 8] It is a schematic configuration diagram of the case of the first fan shown in FIG. 7. [Figure 9] It is a schematic configuration diagram of the impeller of the first fan shown in FIG. 7. [Figure 10] It is a schematic configuration diagram of the housing of the in-vehicle refrigerator shown in FIG. 1. [Figure 11]It is a perspective sectional view of an in-vehicle refrigerator shown in FIG. 1.

Mode for Carrying Out the Invention

[0020] In order to make the objectives, technical means, and advantages of the embodiments of the present application clearer, hereinafter, while referring to the drawings in the embodiments of the present application, the technical means in the embodiments of the present application will be described clearly and completely. Obviously, the described embodiments are only a part of the embodiments of the present application, not all of the embodiments. Based on the embodiments of the present application, all other embodiments that can be conceived by those skilled in the art without creative efforts all fall within the protection scope of the present application.

[0021] The following disclosure provides many different embodiments or examples to realize different structures of the present application. To simplify the disclosure of the present application, hereinafter, the components and settings of specific examples will be described. Naturally, these are only exemplary and not for limiting the present application. Also, the present application can repeatedly use reference numerals and / or reference alphabets in different examples. Such repetition is for the purpose of simplification and clarification and does not itself indicate the relationship between the various embodiments and / or arrangements considered.

[0022] For ease of explanation, the specification may use spatial relational terms to describe the relative position or motion of one element or feature relative to other elements or features as shown in the figures, such as “inside,” “outside,” “inside,” “outside,” “bottom,” “downward,” “top,” “upward,” “front,” and “back.” Such spatial relational terms include different orientations of the device during use or operation other than those shown in the drawings. For example, if the device in the figures undergoes a reversal of position, a change in orientation, or a change in motion, the indications of these orientations will also change accordingly. For example, an element described as “below another element or feature” or “below another element or feature” may subsequently be oriented as “above another element or feature” or “above another element or feature.” Thus, the exemplary term “below…” may include the up and down orientations. The device may be further oriented (rotated 90 degrees or to other directions), and the spatial relational descriptors used herein will be interpreted accordingly.

[0023] Conventional direct-cooling in-car refrigerators suffer from low heat exchange efficiency due to natural convection, and the freezing rate near the walls of the enclosure is much faster than at the center of the internal space of the enclosure, resulting in slower freezing and uneven freezing. To address these technical problems, this invention provides an in-car refrigerator in which forced convection generates heat exchange between the air near the walls of the enclosure and the air in the center of the cooling chamber. This allows the cold heat from the walls of the enclosure to be conducted more quickly to the center of the cooling chamber, rapidly lowering the temperature in the center of the cooling chamber. As a result, the temperature uniformity of the cooling chamber is improved, the freezing rate is accelerated, and the heat exchange efficiency is improved.

[0024] Figures 1 to 3 show an in-vehicle refrigerator according to the present invention, which includes a housing 1, a first evaporator 2, a first fan 3, and an air duct assembly 4. The housing 1 is provided with a spaced-apart cooling chamber 101 and a first storage chamber 102. The cooling chamber 101 is for storing items to be cooled (heat load), such as food and beverages. The first evaporator 2 is provided in the first storage chamber 102, and cool air is formed in the cooling chamber 101 by heat exchange between the first evaporator 2 and the wall surface of the housing 1. The first fan 3 is provided in the first storage chamber 102 and includes a first air intake 301 and a first air outlet 302 (shown in Figure 8) connected to the cooling chamber 101. The air duct assembly 4 is provided in the first containment chamber 102 and includes a duct 41 that extends from the first air intake 301 to the cooling chamber 101, with its first end communicating with the cooling chamber 101 and its second end communicating with the first air intake 301 of the first fan 3. The first fan 3 sends a high-speed airflow to the cooling chamber 101 and drives the cold air in the cooling chamber 101 to flow from the second end of the duct 41 to the first fan 3 before flowing back into the cooling chamber 101, thereby forming a circulating airflow within the vehicle refrigerator.

[0025] To make it easier to understand, as shown in Figure 4, when the first fan 3 is operating, it can stably generate a high-pressure, high-speed airflow. The high-speed airflow enters the cooling chamber 101 from the first outlet 302 of the first fan 3, and drives the cold air from the cooling chamber 101 to flow from the second end of the duct 41 of the air duct assembly 4 to the first fan 3 before flowing back into the cooling chamber 101, thereby forming a circulating airflow within the vehicle refrigerator. During the airflow circulation process, heat exchange occurs between the heat load and the cold air, causing it to cool down. Heat conduction also occurs between the first evaporator 2 and the wall surface of the housing 1, transferring the cold from the first evaporator 2 to the wall surface of the housing 1. Forced convection heat exchange occurs between the air near the wall surface of the housing 1 and the air in the center of the cooling chamber 101. As a result, the cold from the wall surface of the housing 1 is conducted more quickly to the center of the cooling chamber 101, rapidly lowering the temperature of the center of the cooling chamber 101. This improves the temperature uniformity of the cooling chamber 101 of the refrigerator, accelerates the freezing speed, and improves the heat exchange efficiency.

[0026] Naturally, the in-vehicle refrigerator according to this embodiment can also operate even when the first fan 3 is stopped, and the first evaporator 2 and the wall surface of the housing 1 transfer cold energy by heat conduction, and this cold energy is transferred to the cooling chamber 101 by natural convection, thereby lowering the temperature of the heat load.

[0027] Furthermore, a heat-insulating layer is provided within the first containment chamber 102, positioned around the cooling chamber 101. The heat-insulating layer serves to block heat conduction, preventing cold and heat from leaking to the outside of the enclosure. Exemplarily, the heat-insulating layer may be formed by filling and curing a urethane prepolymer, foaming agent, catalyst, and chain-extending crosslinking agent, or it may be formed by directly filling it with other heat-insulating materials.

[0028] Preferably, the first fan 3 is a centrifugal fan, which improves the airflow circulation effect by applying pressure to the air and increasing the airflow speed. This enhances the heat exchange efficiency.

[0029] Exemplary, the housing 1 includes an inner layer plate 11 and an outer layer plate 12, the outer layer plate 12 being fitted around the periphery of the inner layer plate 11, and a first housing chamber 102 being enclosed between the inner layer plate 11 and the outer layer plate 12. The housing 1 may be cylindrical or rectangular, and this application does not specifically limit it.

[0030] Specifically, the cross-section of the duct 41 may be set to a square. If the housing is set to a rectangular tube shape, the duct 41 may be provided extending along the outer wall surface of the inner layer plate 11. In one preferred embodiment, the duct 41 may be connected in contact with the side of the inner layer plate 11 facing the first storage chamber 102. In this case, the duct 41 is provided close to the cooling chamber 101, thereby shortening the flow path of the circulating airflow and reducing the pressure loss of the circulating airflow. This avoids a decrease in airflow velocity, allowing the cold heat from the wall surface of the housing 1 to be conducted more quickly to the center of the cooling chamber 101, thereby rapidly lowering the central temperature of the cooling chamber 101, improving temperature uniformity inside the refrigerator, increasing the freezing rate, and improving heat exchange efficiency. In another embodiment, the duct 41 may be provided in the middle of the first storage chamber 102.

[0031] In one embodiment, as shown in Figures 6 and 10, a first ventilation opening 411 is provided at the first end of the duct 41, and a second air intake 103 is provided in the housing 1 that communicates with the cooling chamber 101. The first ventilation opening 411 of the duct 41 communicates with the second air intake 103 of the housing 1. As shown in Figures 7 and 8, the first fan 3 includes a case 32 and an impeller 31, the impeller 31 being located inside the case 32. The case 32 is provided with a first air intake 301, and a second ventilation opening 412 is provided at the second end of the duct 41. The second ventilation opening 412 of the duct 41 is connected to the first air intake 301. The case 32 is provided with the first air outlet 302, and the housing 1 is provided with a second air outlet 104 (shown in Figure 1) that communicates with the cooling chamber 101. The second air outlet 104 of the housing 1 is connected to the first air outlet 302. To understand this, when the impeller 31 of the first fan 3 rotates, outside air flows axially into the case 32, compressing the air within the case 32 of the first fan 3 and generating a stable, high-pressure, high-speed airflow. The high-speed airflow rotates 90 degrees and flows radially, subsequently entering the cooling chamber 101 through the first air outlet 302 of the first fan 3 and the second air outlet 104 of the housing 1. The high-speed airflow in this section drives the cold air from the cooling chamber 101 into the duct 41 through the second air intake 103 of the housing 1 and the first ventilation opening 411 of the duct 41, and then into the first air intake 301 of the first fan 3 through the second ventilation opening 412 of the duct 41. The centrifugal force of the impeller 31 creates a high-speed airflow, thereby forming a circulating airflow. During the airflow circulation process, heat exchange occurs between the heat load and the cold air, causing it to cool down. Heat conduction also occurs between the first evaporator 2 and the wall surface of the housing 1, transferring the cold from the first evaporator 2 to the wall surface of the housing 1. Forced convection heat exchange occurs between the wall surface of the housing 1 and the air in the cooling chamber 101. As a result, the cold from the wall surface of the housing 1 is conducted more quickly to the center of the cooling chamber 101, rapidly lowering the temperature at the center of the cooling chamber 101. This improves temperature uniformity inside the refrigerator, accelerates the freezing speed, and improves heat exchange efficiency.

[0032] The first ventilation opening 411 of the air duct assembly 4 is connected to the second intake port 103 of the housing 1, and specifically, it may be provided such that the orthographic projection of the first ventilation opening 411 of the air duct assembly 4 in the vertical plane and the orthographic projection of the first intake port 301 of the case 32 in the vertical plane overlap. When provided in this manner, the airflow of the air duct assembly 4 passes through the first intake port 301 more smoothly, improving airflow circulation efficiency and accelerating the cooling rate of the cooling chamber 101.

[0033] The first ventilation opening 411 may be circular, rectangular, or of other shape, and this application does not specifically limit it. In one example, the first ventilation opening 411 is set to be circular, and the second intake opening 103 is set to correspond to the circular shape, so that the cold air from the cooling chamber 101 passes better through the second intake opening 103 to the first ventilation opening 411. In another example, as shown in Figure 6, the first ventilation opening 411 is set to be rectangular, and the second intake opening 103 is provided to correspond to the rectangle. The second ventilation opening 412 may be circular, rectangular, or of other shape, and this application does not specifically limit it. In a preferred example, a centrifugal fan may be used for the first fan 3, and the first intake opening 301 of the centrifugal fan is set to be circular, and the second ventilation opening 412 is set to correspond to the circular shape.

[0034] In one embodiment, the second air intake port 103 and the second air outlet port 104 of the housing 1 are provided facing each other in the horizontal direction. For the sake of explanation and understanding, as shown in Figure 10, the horizontal direction may also be the X direction shown in the figure. For example, if the housing 1 is set in the shape of a rectangular tube, the second air intake port 103 and the second air outlet port 104 are provided on opposite sides of the housing 1. By providing the second air intake port 103 and the second air outlet port 104 facing each other, the convection effect in the cooling chamber 101 can be enhanced, thereby allowing the cold air in the cooling chamber 101 to circulate more quickly and the temperature of the cooling chamber 101 to become uniform more quickly.

[0035] Naturally, the second air intake 103 and the second air outlet 104 may be provided on adjacent sides of the housing 1, respectively.

[0036] In one embodiment, as shown in Figures 7 and 8, the case 32 is provided with a first groove 321, the second end of the duct 41 is fitted into the first groove 321, and the first air intake 301 is provided in the first groove 321 such that the vertical plane in which the first air intake 301 is located and the vertical plane in which the first air outlet 302 is located are not on the same plane. With this configuration, the case 32 is provided with the first groove 321 and the second end of the duct 41 is fitted into the first groove 321, thereby improving the assembly stability of the duct 41 while also improving the aesthetic appearance of the wall surface inside the housing 1. If the case 32 is not provided with the first groove 321, it is necessary to provide a groove in the inner layer plate for attaching the duct 41. With this design, a protrusion exists inside the cooling chamber 101, which not only spoils the appearance but may also interfere with the user when taking out items such as food and beverages.

[0037] As shown in Figure 5, the second end of the duct 41 is fitted into the first groove 321, and specifically, the second end of the duct 41 can be positioned so as to be in close contact with the first groove 321.

[0038] In one embodiment, as shown in Figure 5, a first wall surface 311 is provided on the side of the impeller 31 that is close to the case 32, and a second wall surface 324 is provided on the side of the case 32 that is close to the impeller 31. There is a gap t between the first wall surface 311 and the second wall surface 324, and the numerical range of the gap t is 0.5 mm to 3.5 mm. In this embodiment, as shown in Figure 9, a third air intake port 312 is provided on the first wall surface 311 of the impeller 31, and a first air intake port 301 is provided on the second wall surface 324 and communicates with the third air intake port 312. On the circumferential side of the impeller 31, a plurality of third air outlets 313 are provided, uniformly arranged in the circumferential direction of the impeller 31, and the third air outlets 313 communicate with the first air outlets 302. With this design, external air flows axially from the first intake port 301 of the case 32 to the third intake port 312 of the impeller 31. The air in this section is pressurized and stabilized by the impeller 31, forming a high-pressure, high-speed airflow. The high-speed airflow flows out from the third outlet port 313 of the impeller 31, passes through the first outlet port 301 of the case 32 to the second outlet port 104 of the housing 1, and then enters the cooling chamber 101.

[0039] Furthermore, the larger the gap, the greater the possibility that the air discharged from the third outlet 313 will be drawn into the third intake port 312. Conversely, the smaller the gap, the greater the possibility of interference between the impeller 31 and the case 32 during installation. Therefore, the gap cannot be made too small in order to avoid collision between the impeller 31 and the case 32 during installation. On the other hand, the gap cannot be made too small in order to reduce the possibility that the air discharged from the third outlet 313 will be drawn into the third intake port 312. Specifically, the gap may be set to 1 mm, 1.5 mm, 2 mm, 2.5 mm, 3 mm, etc.

[0040] In one embodiment, as shown in Figure 8, the case 32 is provided with a baffle 322, which may be provided parallel to the vertical plane, and the orthographic projection of the baffle 322 in the vertical plane partially covers the orthographic projection of the impeller 31 in the vertical plane. The baffle 322 can block the side of the first fan 3, thereby reducing the possibility that the air discharged from the third outlet 313 is drawn into the third intake port 312.

[0041] Furthermore, as shown in Figure 5, the baffle 322 includes a third wall surface, the third wall surface being located on the side of the baffle 322 facing the first fan 31, and the third wall surface and the second wall surface 324 are flush. That is, there is a gap t between the third wall surface and the first wall surface, and the numerical range of t can be found in the above embodiment, which will not be explained here.

[0042] The baffle 322 may be set to a fan shape, rectangle, or other shape. Preferably, the baffle 322 may be set to a fan shape.

[0043] Multiple first outlets 302 and multiple second outlets 104 are provided, with a one-to-one correspondence between the multiple second outlets 104 and the multiple first outlets 302. For example, as shown in Figure 8, two first outlets 302 are provided, each on either side of the duct 41, and two second outlets 104 are provided, each corresponding to one of the two first outlets 302. By providing two first outlets 302 and two second outlets 104, the area through which high-speed airflow passes can be increased, thereby improving the airflow entering the cooling chamber 101, enhancing convection efficiency, and accelerating the cooling speed. Naturally, three first outlets 302 may be provided, and correspondingly, three second outlets 104 may also be provided. The first air outlet 302 may be set in an annular shape, and the second air outlet 104 may also be set in an annular shape accordingly.

[0044] In some embodiments, as shown in Figure 6, the air duct assembly 4 further includes a first ventilation grille 42. The first ventilation grille 42 is provided at the first ventilation opening 411 and serves to provide ventilation while preventing other foreign objects from entering the duct 41 and clogging the duct 41. In some embodiments, as shown in Figure 7, a second ventilation grille 323 is provided at the first outlet 302 of the case 32. The second ventilation grille 323 serves to provide ventilation while preventing other foreign objects from entering the duct 41 and clogging the duct 41 when the first fan 3 is stopped.

[0045] In conventional technology, direct-cooling in-vehicle refrigerators may experience frost formation on the walls inside their enclosure. When the refrigerator is stopped, this frost melts and condenses into water, affecting the user experience.

[0046] In one embodiment, as shown in Figure 11, the air duct assembly 4 further includes a second evaporator 43, which is located within the duct 41, so that when the first fan 3 is operating, heat exchange occurs between the airflow in the duct 41 and the second evaporator 43. As can be understood, when the first fan 3 is operating, the circulating airflow in the duct 41 passes over the surface of the second evaporator 43, heat exchange occurs between the second evaporator 43 and the circulating airflow, and the cold from the second evaporator 43 can be delivered to the cooling chamber 101 of the refrigerator. By having the air pass over the surface of the second evaporator 43, the heat exchange capacity of the second evaporator 43 can be greatly enhanced, improving the freezing capacity of the refrigerator. At the same time, moisture in the circulating airflow can condense on the surface of the second evaporator 43, and since the amount of water vapor in the cooling chamber 101 is constant, the amount of frost in the duct 41 increases, and the amount of frost on the walls of the housing 1 decreases accordingly. As airflow circulates continuously, the amount of moisture in the cooling chamber 101 decreases, thereby reducing the probability of frost formation on the walls of the enclosure 1. In other words, the probability of condensation forming in the cooling chamber 101 is reduced, significantly improving the user experience.

[0047] Furthermore, coil-type evaporators or expansion-type evaporators can be used for the first evaporator 2 and the second evaporator 43. The first evaporator 2 and the second evaporator 43 may be directly connected to form at least a partial structure in the refrigeration circulation circuit, and of course, the first evaporator 2 and the second evaporator 43 may be an integrated structure. That is, some of the evaporator pipes are provided inside the duct 41, and other parts of the pipes are provided outside the duct 41.

[0048] Naturally, the in-vehicle refrigerator according to this embodiment can also operate even when the first fan 3 is stopped. The cooling energy of the second evaporator 43 is transferred to the duct 41 and the wall surface of the housing 1 by heat conduction, and the cooling energy of this part is transferred to the cooling chamber 101 by natural convection, thereby lowering the temperature of the heat load.

[0049] Furthermore, as shown in Figure 1, the in-vehicle refrigerator further includes a cover 5 rotatably mounted on the top of the housing 1 to open and close the cooling chamber 101. A sealing strip may be provided on the side of the cover 5 facing the cooling chamber 101, and when the cover 5 covers the top of the housing 1, the sealing strip can improve the airtightness and prevent the cold air in the cooling chamber 101 from leaking out of the housing 1.

[0050] A heat-insulating layer may also be provided inside the cover 5, which serves to block heat conduction and prevent cold or hot air from leaking out of the housing 1.

[0051] In one embodiment, as shown in Figure 11, the vehicle-mounted refrigerator includes a compressor and a condenser, and the housing is provided with a second storage chamber 105. The compressor and condenser are located in the second storage chamber 105, and the first storage chamber 102 and the second storage chamber 105 are spaced apart. The compressor, condenser, and first evaporator 2 are connected to form at least a partial structure in the refrigeration circulation circuit. The vehicle-mounted refrigerator may further include a throttling device.

[0052] Specifically, the compressor's outlet is connected to the refrigerant inlet of the condenser, and the compressor's intake is connected to the refrigerant outlet of the first evaporator 2. The refrigerant outlet of the condenser is connected to the refrigerant inlet of the throttling device, and the refrigerant outlet of the throttling device is connected to the refrigerant inlet of the first evaporator 2. The compressor, condenser, throttling device, and first evaporator 2 constitute a refrigeration circulation circuit. The compressor draws in low-pressure refrigerant from the first evaporator 2, increases the refrigerant's pressure from low to high, and circulates the refrigerant continuously within the refrigeration circulation circuit. The refrigerant condenses in the condenser to become a high-pressure, high-temperature refrigerant liquid, and this refrigerant liquid enters the throttling device, is throttled by the throttling device, and then enters the first evaporator 2. Heat exchange occurs between the low-temperature refrigerant in the first evaporator 2 and the wall surface of the housing 1, thereby lowering the temperature of the cooling chamber 101. The refrigerant absorbs heat in the first evaporator 2 and evaporates to become low-pressure refrigerant vapor, which enters the compressor's intake, thus achieving refrigerant circulation.

[0053] Preferably, the throttling device restricts the high-pressure refrigerant liquid from the condenser to reduce the pressure to low-pressure refrigerant liquid and adjusts the flow rate of the refrigerant entering the first evaporator 2. When the throttling device is adjusted to its maximum opening, the refrigerant flows at its maximum rate in the refrigeration pipe. The throttling device may be, but is not limited to, a capillary tube, a throttling pipe, a thermal expansion valve, an electronic expansion valve, a floating valve, a throttling hole plate, a manual expansion valve, etc.

[0054] Furthermore, the vehicle-mounted refrigerator is located in the second storage compartment 105 and includes a second fan for dissipating heat from the condenser. To facilitate heat dissipation, the housing 1 may be provided with a heat dissipation port communicating with the second storage compartment 105.

[0055] It should be understood that the terms used herein are for the purpose of describing specific exemplary embodiments only and are not intended to be limiting. Unless explicitly indicated in the context, the singular forms “1,” “one,” and “the foregoing” used herein may also include the plural form. The terms “include,” “equip,” “contain,” and “have” are inclusive and indicate the presence of the described features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The steps, processes, and operations of the methods described herein should not be construed as having to be performed in a specific order described or explained unless the order of execution is explicitly indicated. It should be understood that additional or alternative steps may be used.

[0056] Terms such as "first," "second," and "third" may be used to describe various elements, components, regions, layers, and / or parts, but these elements, components, regions, layers, and / or parts should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or part from other regions, layers, or parts. Unless explicitly indicated in the context, terms such as "first," "second," and other numeral terms do not imply order or rank in this specification. Accordingly, in the following description, a first element, component, region, layer, or part may be referred to as a second element, component, region, layer, or part without departing from the teaching of the exemplary embodiments.

[0057] The above description is merely a specific embodiment of the present application, and a person skilled in the art can understand or implement it. Various modifications to these embodiments are obvious to a person skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Accordingly, the present application is not limited to these embodiments described herein, but conforms to the broadest scope that is consistent with the principles and novel features disclosed herein. [Explanation of Symbols]

[0058] 1 cabinet 11 Inner layer 12 Outer layer plate 101 Cooling room 102 First Confinement Room 103 Second air intake 104 2nd outlet 105 Second Confinement Room 2. First evaporator 3 First Fan 31 Impeller 311 First Wall 312 Third air intake 313 3rd outlet 32 cases 321 1st groove 322 Baffle 323 Second ventilation grille 324 Second Wall 301 First air intake 302 1st outlet 4. Air duct assembly 41 Duct 411 First ventilation opening 412 Second ventilation opening 42. First ventilation grille 43. Second evaporator 5 Cover

Claims

1. It is a car refrigerator, A housing comprising a cooling chamber and a first housing chamber arranged at a distance from each other, A first evaporator is provided in the first containment chamber and is capable of heat exchange with the wall surface of the housing so as to form cold air in the cooling chamber, A first fan is provided in the first containment chamber and includes a first air intake and a first air outlet communicating with the cooling chamber. The present invention includes an air duct assembly provided in the first containment chamber, extending from the first air intake to the cooling chamber, with a first end communicating with the cooling chamber and a second end communicating with the first air intake, An in-vehicle refrigerator characterized in that the first fan supplies a high-speed airflow to the cooling chamber, and drives the cold air in the cooling chamber to flow from the second end of the duct to the first fan before flowing into the cooling chamber, thereby forming a circulating airflow within the in-vehicle refrigerator.

2. A first ventilation opening is provided at the first end of the duct, and a second intake opening is provided in the housing that communicates with the cooling chamber, and the first ventilation opening communicates with the second intake opening, The first fan includes a case and an impeller, the impeller being housed within the case which has a first air intake, and the second end of the duct having a second ventilation opening that communicates with the first air intake. The vehicle refrigerator according to claim 1, characterized in that the case is provided with the first air outlet, the housing is provided with a second air outlet that communicates with the cooling chamber, and the second air outlet communicates with the first air outlet.

3. The in-vehicle refrigerator according to claim 2, characterized in that the second air intake and the second air outlet are provided facing each other in the horizontal direction.

4. The in-vehicle refrigerator according to claim 2, characterized in that the case is provided with a first groove, the second end of the duct is fitted into the first groove, and the first air intake is provided in the first groove.

5. The in-vehicle refrigerator according to claim 2, characterized in that a first wall surface is provided on the side of the impeller that is close to the case, a second wall surface is provided on the side of the case that is close to the impeller, and there is a gap between the first wall surface and the second wall surface, the gap being in the range of 0.5 mm to 3.5 mm.

6. The in-vehicle refrigerator according to claim 5, characterized in that a third air intake is provided on the first wall surface, the first air intake is provided on the second wall surface and communicates with the third air intake, and a plurality of third air outlets are provided on the circumferential side of the impeller, uniformly arranged in the circumferential direction of the impeller, and the third air outlets communicate with the first air outlets.

7. The vehicle refrigerator according to claim 2, characterized in that the case is provided with a baffle, and the orthogonal projection of the baffle onto a vertical plane partially covers the orthogonal projection of the impeller onto a vertical plane.

8. The in-vehicle refrigerator according to claim 2, characterized in that a plurality of first air outlets are provided, a plurality of second air outlets are provided, and the plurality of second air outlets and the plurality of first air outlets are provided in a one-to-one correspondence.

9. The in-vehicle refrigerator according to claim 2, characterized in that the air duct assembly further includes a first ventilation grille provided at the first ventilation opening, and / or a second ventilation grille is provided at the first air outlet of the case.

10. The in-vehicle refrigerator according to claim 1, wherein the air duct assembly further includes a second evaporator, the second evaporator being provided in the duct so that heat exchange occurs between the airflow in the duct and the second evaporator when the first fan is operating.

11. The vehicle refrigerator according to any one of claims 1 to 10, characterized in that a heat-insulating layer is provided in the first storage chamber, arranged around the cooling chamber.

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