Evaporator and Refrigeration Device

The present application claims the benefit of Chinese Patent Application Nos. 2024205503858 filed on Mar. 20, 2024, 2024103216853 filed on Mar. 20, 2024, 202410554314X filed on May 6, 2024, 2024216537538 filed on Jul. 12, 2024 and 2024109380194 filed on Jul. 12, 2024. All the above are hereby incorporated by reference in their entirety.

The present disclosure relates to the technical field of refrigeration, and in particular to an evaporator and a refrigeration device.

As a heat exchanger, the evaporator is an important component in the refrigeration device. A condensed fluid at a low temperature exchanges heat with outside air through the evaporator, and is vaporized to absorb heat, thereby realizing a refrigeration effect. The evaporator in most existing refrigeration devices (such as a smoothie maker) includes a main body and a coil. The main body includes an inner housing and an outer housing. The coil is sleeved on the inner housing and comes in contact with a wall of the outer housing. The condensed fluid is charged to the coil. The condensed fluid exchanges heat with the outside through a wall of the coil and the wall of the outer housing of the main body, thereby realizing the refrigeration effect. However, according to the above structure, the heat is transferred through the wall of the coil and the wall of the outer housing of the main body. Due to various heat transfer media, the heat transfer efficiency is low, the whole structure is complex, and the cost is high.

A technical problem to be solved by the present disclosure is to provide an evaporator and a refrigeration device. The present disclosure can improve heat transfer efficiency and cold conduction performance of the evaporator, and has a simple overall structure and a low production cost.

To solve the above-mentioned technical problem, the present disclosure provides an evaporator, including an evaporator housing, a condensate input tube, a gas-guide tube, and a refrigerant region, where the refrigerant region is provided around an inner wall of the evaporator housing; the refrigerant region and the evaporator housing enclose at least one refrigerant passage; and the refrigerant passage includes an input end connected to a condenser through the condensate input tube, and an output end connected to a compressor through the gas-guide tube.

As an improvement to the above solution, the refrigerant region includes a refrigerant housing and at least one spiral turbulator sheet; the refrigerant housing is hermetically connected to the evaporator housing; the spiral turbulator sheet is located between the refrigerant housing and the evaporator housing; and the spiral turbulator sheet, the refrigerant housing, and the evaporator housing enclose the at least one refrigerant passage.

As an improvement to the above solution, a heat-exchange member is provided between the evaporator housing and the refrigerant housing; the heat-exchange member includes a heat insulating body and the spiral turbulator sheet; the heat insulating body is sleeved on or embedded into the refrigerant housing; and the spiral turbulator sheet is protruded from a sidewall of the heat insulating body.

As an improvement to the above solution, when a side of the heat-exchange member away from the spiral turbulator sheet is located on the refrigerant housing, the spiral turbulator sheet extends toward the evaporator housing to form the refrigerant passage where a condensed fluid exchanges heat with outside air through the evaporator housing.

As an improvement to the above solution, when a side of the heat-exchange member away from the spiral turbulator sheet is located on the evaporator housing, the spiral turbulator sheet extends toward the refrigerant housing to form the refrigerant passage where a condensed fluid exchanges heat with outside air through the refrigerant housing.

As an improvement to the above solution, a plurality of spiral turbulator sheets are provided between the refrigerant housing and the evaporator housing; the refrigerant housing, the evaporator housing, and the plurality of spiral turbulator sheets enclose a plurality of refrigerant passages; the plurality of refrigerant passages are arranged in parallel; and the plurality of refrigerant passages are spaced apart by the spiral turbulator sheets.

As an improvement to the above solution, the spiral turbulator sheet is made of metal, plastic or silica gel.

As an improvement to the above solution, the heat-exchange member is made of plastic or silica gel; and the heat insulating body and the spiral turbulator sheet are an integrated structure or a split structure.

As an improvement to the above solution, an input tube opening and an output tube opening communicating with the refrigerant passage in one-to-one correspondence are respectively provided at two ends of the refrigerant housing; the condensate input tube communicates with the refrigerant passage through the input tube opening; and the gas-guide tube communicates with the refrigerant passage through the output tube opening.

As an improvement to the above solution, the refrigerant housing is provided with a plurality of middle input tube openings at intervals along a flow direction of the refrigerant passage; the middle input tube openings communicate with the refrigerant passage; the middle input tube openings are located between the input tube opening and the output tube opening; and the middle input tube openings each are connected to the condenser through a corresponding condensate input tube.

As an improvement to the above solution, an input tube opening and an output tube opening communicating with the refrigerant passage in one-to-one correspondence are respectively provided at two ends of the evaporator housing; the condensate input tube communicates with the refrigerant passage through the input tube opening; and the gas-guide tube communicates with the refrigerant passage through the output tube opening.

As an improvement to the above solution, the evaporator housing is provided with a plurality of middle input tube openings at intervals along a flow direction of the refrigerant passage; the middle input tube openings communicate with the refrigerant passage; the middle input tube openings are located between the input tube opening and the output tube opening; and the middle input tube openings each are connected to the condenser through a corresponding condensate input tube.

As an improvement to the above solution, one end of the refrigerant housing is provided with an outward extending limit ring; the limit ring is hermetically connected to one end of the evaporator housing; the other end of the evaporator housing away from the limit ring is provided with an inward extending support ring; and the support ring is hermetically connected to the other end of the refrigerant housing.

As an improvement to the above solution, the evaporator housing or the refrigerant housing has a diameter of A, and a thickness of B, the A being 60-100 mm, and the B being 0.5-1.2 mm; a width of the refrigerant passage is the same as a pitch of the spiral turbulator sheet; the spiral turbulator sheet has the pitch of C, a width of E, and a thickness of F, the C being 5-20 mm, the E being 2-10 mm, and the F being 0.4-2 mm; and a ratio of the thickness of the evaporator housing or the refrigerant housing to the pitch of the spiral turbulator sheet is G, the G satisfying 0.06≤G≤0.1.

As an improvement to the above solution, the A is 80-90 mm, the B is 0.8-1.0 mm, the C is 8-16 mm, the E is 5-8 mm, the F is 0.9-1.5 mm, and the G satisfies 0.0625≤G≤0.1.

As an improvement to the above solution, the refrigerant region includes at least one spiral raised member; the raised member is hermetically connected to the inner wall of the evaporator housing; and an inner chamber of the raised member and the evaporator housing enclose the at least one refrigerant passage.

As an improvement to the above solution, the refrigerant region includes a plurality of spiral raised members; inner chambers of the raised members and the evaporator housing enclose a plurality of refrigerant passages; the plurality of refrigerant passages are arranged in parallel; and the plurality of refrigerant passages are spaced apart by the raised members.

As an improvement to the above solution, the raised member and the inner wall of the evaporator housing are an integrally punch-formed structure; an input port and an output port communicating with the refrigerant passage in one-to-one correspondence are respectively provided at two ends of the raised member at intervals; the condensate input tube communicates with the refrigerant passage through the input port; and the gas-guide tube communicates with the refrigerant passage through the output port.

As an improvement to the above solution, the raised member is provided with a plurality of middle input ports at intervals along a flow direction of the refrigerant passage; the middle input ports communicate with the refrigerant passage; the middle input ports are located between the input port and the output port; and the middle input ports each are connected to the condenser through a corresponding condensate input tube.

As an improvement to the above solution, the evaporator housing has a diameter of A, and a thickness of B, the A being 60-100 mm, and the B being 0.5-1.2 mm; a width of the refrigerant passage is the same as a diameter of the raised member; the raised member has the diameter of D, and a thickness of H, the D being 5-10 mm, and the H being 0.4-0.8 mm; and a ratio of the thickness of the evaporator housing to the diameter of the raised member is I, the I satisfying 0.1≤I≤0.12.

As an improvement to the above solution, the A is 80-90 mm, the B is 0.8-1.0 mm, the D is 6-8 mm, the H is 0.5-0.6 mm, and the I satisfies 0.1≤I≤0.11.

The present disclosure further provides a refrigeration device, including a machine body, where the evaporator is provided in the machine body; and the refrigeration device includes any one of an ice cream maker, a smoothie maker, a cold beverage maker, and an ice maker.

The present disclosure has the following beneficial effects:

By guiding the condensed fluid through the refrigerant passage, the condensed fluid is vaporized fully to improve a heat exchange effect. The condensed fluid can exchange heat with the outside directly through the single heat transfer medium. By reducing the heat transfer medium, the present disclosure can effectively improve heat transfer efficiency of the evaporator, thereby improving cold conduction performance of the evaporator. Moreover, the present disclosure can simplify an overall structure, save an assembly space, and lower a production cost.

In order to make the objectives, technical solutions, and advantages of the present disclosure clearer, the present disclosure will be further described in detail below with reference to the accompanying drawings.

toillustrate a schematic structural view of an evaporator according to a first embodiment of the present disclosure. As shown into, the evaporator includes an evaporator housing, a condensate input tube, a gas-guide tube, and a refrigerant region. The refrigerant regionis provided around an inner wall of the evaporator housing. The refrigerant regionand the evaporator housingenclose a refrigerant passage. A condensed fluid in the refrigerant passageacts on the inner wall of the evaporator housing, to realize an external refrigeration function of the evaporator. The refrigerant passageincludes an input end connected to a condenser through the condensate input tube, and an output end connected to a compressor through the gas-guide tube. When the evaporator works, the condenser conveys the condensed fluid to the refrigerant passagethrough the condensate input tube. The condensed fluid flowing to the refrigerant passagecan absorb heat from the outside directly through the evaporator housing, thereby realizing heat exchange with outside air. A vaporized gas from the condensed fluid is exhausted back to the compressor through the gas-guide tube. By guiding the condensed fluid through the refrigerant passage, the condensed fluid is vaporized fully to improve a heat exchange effect. The refrigerant regionaround the inner wall of the evaporator housingcan increase a heat transfer area. The condensed fluid can exchange heat with the outside only through the evaporator housing(namely a single heat transfer medium). By reducing the heat transfer medium, the present disclosure can effectively improve heat transfer efficiency, thereby improving cold conduction performance of the evaporator. Moreover, the present disclosure can simplify an overall structure, save an assembly space, and lower a production cost.

The refrigerant regionincludes a refrigerant housingand a spiral turbulator sheet. The refrigerant housingis hermetically connected to the evaporator housing, such that an airtight space is formed between the refrigerant housingand the evaporator housing. The spiral turbulator sheetis located between the refrigerant housingand the evaporator housing. The spiral turbulator sheet, the refrigerant housingand the evaporator housing I enclose the refrigerant passage. The refrigerant passageof a spiral structure can guide the condensed fluid therein to improve a flow velocity, such that the condensed fluid is vaporized fully, thereby improving the heat transfer efficiency, and further improving the cold conduction performance of the evaporator.

Preferably, a wall of the evaporator housingis preferably made of metal. The metal has a good heat transfer effect, and can improve the cold conduction performance. However, the material of the wall of the evaporator housingis not limited thereto, and may further be other heat conductive materials with the good heat transfer effect.

Preferably, the spiral turbulator sheetis preferably made of metal or plastic, but is not limited thereto.

Further, an input tube openingand an output tube openingcommunicating with the refrigerant passageare respectively provided at two ends of the refrigerant housing. The condensate input tubecommunicates with the refrigerant passagethrough the input tube opening. The condenser allows the condensed fluid to flow in the refrigerant passagethrough the condensate input tubeand the input tube opening. The condensed fluid is vaporized gradually in the refrigerant passageto realize heat exchange. The gas-guide tubecommunicates with the refrigerant passagethrough the output tube opening. After the condensed fluid in the refrigerant passageis vaporized, the vaporized gas from the condensed fluid is exhausted back to the compressor through the output tube openingand the gas-guide tubeto realize cold conduction circulation.

Both the gas-guide tubeand the condensate input tubeare provided inside the refrigerant housing. This makes the structure compact, reduces the overall footprint of the evaporator, improves the space utilization rate of the evaporator, and ensures that one side of the evaporator housingcomes in contact with a heat exchange surface maximally for refrigeration to achieve the better refrigeration effect.

Further, as shown into, one end of the refrigerant housingis provided with an outward extending limit ring. The limit ringis hermetically connected to one end of the evaporator housing. The other end of the evaporator housingaway from the limit ringis provided with an inward extending support ring. The support ringis hermetically connected to the other end of the refrigerant housing. Through the limit ringand the support ring, the refrigerant housingis fixed, supported and limited, the airtight space for storing the condensed fluid is formed between the refrigerant housingand the evaporator housing, and the condensed fluid does not flow out to affect the cold conduction performance of the evaporator.

Preferably, as shown inand, an inward extending input tubeis provided on the input tube opening, such that the condensate input tubeis stably inserted into the input tubeand welded to improve connection stability and airtightness. Correspondingly, an inward extending output tubeis provided on the output tube opening, such that the gas-guide tubeis stably inserted into the output tubeand welded to improve connection stability and airtightness.

Further, the evaporator housinghas a diameter of A. The A is 60-100 mm. Further, the A is preferably 80-90 mm. The evaporator housinghas a thickness of B. The B is 0.5-1.2 mm. Further, the B is preferably 0.8-1.0 mm.

A width of the refrigerant passageis the same as a pitch of the spiral turbulator sheet. The spiral turbulator sheethas the pitch of C. The spiral turbulator sheethas a width of E. The spiral turbulator sheethas a thickness of F. The C is 5-20 mm, the E is 2-10 mm, and the F is 0.4-2 mm. Further, the C is 8-16 mm, the E is 5-8 mm, and the F is 0.9-1.5 mm.

A ratio of the thickness of the evaporator housingto the pitch of the spiral turbulator sheetis G. The G satisfies 0.06≤G=(B/C)≤0.1. Further, the G satisfies 0.0625≤G≤0.1.

The width of the refrigerant passageand the thickness of the evaporator housingjointly determine the heat exchange efficiency and the heat exchange effect of the evaporator. When the ratio G of the thickness of the evaporator housingto the pitch of the spiral turbulator sheetsatisfies 0.6≤G≤0.1, the heat exchange effect is desirable, and the evaporator has the desirable cold conduction performance. In principle, the larger the width of the refrigerant passage(namely a larger contact width between the refrigerant passageand the inner wall of the evaporator housing), the larger the heat exchange area, the higher the heat exchange efficiency and the better the heat exchange effect. The smaller the thickness of the evaporator housing, namely the thinner the heat transfer medium, the higher the heat transfer efficiency and the better the heat transfer effect. However, in case of the excessively large width of the refrigerant passage, the flow velocity of the condensed fluid is slowed down to cause the poor heat exchange effect of the condensed fluid. Meanwhile, the evaporator housing, the refrigerant housingand the spiral turbulator sheetare required to be thicker to cause a high cost, or event affect a service life. In addition, if the evaporator housingis too thin, and the refrigerant passagehas an overlarge fluid flow rate or an overlarge pressure, the evaporator housingdeforms to even affect the airtightness, thereby affecting normal operation. If the evaporator housingis too thick, the heat transfer efficiency and the heat transfer effect are also affected. In view of this, if the ratio G of the thickness of the evaporator housingto the pitch of the spiral turbulator sheetexceeds an appropriate range, namely G<0.06 and G>0.1, the heat exchange effect is affected, the cost is increased, and the stability in use is reduced.

Correspondingly, on the basis of the satisfied ratio G of the thickness of the evaporator housingto the pitch of the spiral turbulator sheet, other parameters of the evaporator housingand the spiral turbulator sheetalso fall within corresponding ranges, such that the overall structure is compact and firm, the stability is high, and the cost is optimal.

Preferably, a width of a section of the refrigerant passagebecomes increasingly large along a flow direction of the refrigerant passage, so as to improve an influx of the condensed fluid to enhance the heat exchange effect. Alternatively, the width of the section of the refrigerant passagebecomes increasingly small along the flow direction of the refrigerant passage, so as to improve a heat exchange velocity of the condensed fluid to enhance the heat exchange effect, thereby improving the cold conduction effect of the evaporator.

Preferably, in other embodiments, the width of the section of the refrigerant passagemay also be unchanged along the flow direction of the refrigerant passage according to an actual need of the user, so as to lower a difficulty of a manufacturing process and achieve the better heat exchange effect.

illustrates a schematic structural view of an evaporator according to a second embodiment of the present disclosure. As shown in, different from the first embodiment shown by, the refrigerant housingmay further be provided with a plurality of middle input tube openingsat intervals along a flow direction of the refrigerant passage.

The middle input tube openingscommunicate with the refrigerant passage. The middle input tube openingsare located between the input tube openingand the output tube opening. The middle input tube openingseach are connected to the condenser through a corresponding condensate input tube. When the evaporator works, the condensed fluid of the condenser flows to different positions of the refrigerant passagesynchronously through the input tube openingand the plurality of middle input tube openings, and acts on the evaporator housing. As a result, the condensed fluid at the low temperature performs heat exchange more quickly at different positions of the evaporator, thereby accelerating a circulation rate and a heat transfer rate of the whole condensed fluid, and improving the cold conduction efficiency of the evaporator.

illustrates a schematic structural view of an evaporator according to a third embodiment of the present disclosure. As shown in, different from the first embodiment shown by, three spiral turbulator sheetsare provided between the refrigerant housingand the evaporator housing.

The refrigerant housing, the evaporator housing and the spiral turbulator sheetsenclose three refrigerant passages. The three refrigerant passagesare arranged in parallel. The three refrigerant passagesare spaced apart by the spiral turbulator sheets. Through the three independent refrigerant passages, the condensed fluid can flow to the evaporator synchronously for heat exchange. This can effectively improve the heat exchange efficiency and the heat exchange effect of the condensed fluid, thereby improving the cold conduction efficiency of the evaporator.

toillustrate a schematic structural view of an evaporator according to a fourth embodiment of the present disclosure. As shown byto, different from the first embodiment shown byto, a heat-exchange memberis provided between the evaporator housingand the refrigerant housing. The heat-exchange memberincludes a heat insulating bodyand the spiral turbulator sheet. The heat insulating bodyis sleeved on or embedded into the refrigerant housing. The spiral turbulator sheetis protruded from a sidewall of the heat insulating body. That is, the spiral turbulator sheetis a spiral convex rib on the sidewall of the heat insulating body. When a side (namely the heat insulating body) of the heat-exchange memberaway from the spiral turbulator sheetis located on the refrigerant housing, the spiral turbulator sheetextends toward the evaporator housingto form the refrigerant passagewhere a condensed fluid exchanges heat with outside air through the evaporator housing, to realize the external refrigeration function of the evaporator.

Meanwhile, a width of a cross section of the refrigerant passagebecomes increasingly large in a direction from the refrigerant housingto the evaporator housing. This increases a contact area between the condensed fluid and the sidewall of the evaporator housing, thereby improving the heat exchange efficiency and the refrigeration effect.