Elevator air conditioner with secondary condensation function

Abstract

This utility model discloses an elevator air conditioner with secondary condensation function, including a compressor, a condenser, and an evaporator. The output end of the compressor is connected to the input end of the condenser through a first pipe; the output end of the condenser is connected to the input end of the evaporator through a second pipe; and the output end of the evaporator is connected to the input end of the compressor through a third pipe. The second pipe has a heat exchange section, and the heat exchange section and the third pipe have a covering portion, forming a pipe-in-pipe structure. This utility model, by setting up a pipe-in-pipe structure between the second and third pipes, utilizes the heat absorption effect of the low-temperature, low-pressure gaseous refrigerant in the third pipe to perform secondary condensation on the incompletely condensed gas-liquid mixture refrigerant in the second pipe. This effectively solves the problem of insufficient primary condensation under high-temperature environments, ensuring that the refrigerant entering the evaporator is mainly liquid, significantly improving the cooling effect.

Description

Technical Field

[0001] This utility model relates to the technical field of elevator air conditioning, and in particular to an elevator air conditioner with a secondary condensation function. Background Technology

[0002] When the elevator air conditioner starts, the refrigerant is compressed into a high-temperature, high-pressure gas by the compressor and then flows to the condenser. The condenser dissipates heat and condenses the refrigerant into a high-pressure, room-temperature liquid. However, if the air conditioner is in a high-temperature environment, it will not be able to completely condense the refrigerant into a high-pressure pure liquid. The refrigerant that has not been completely cooled is in a gas-liquid mixed state in the pipes of the condenser. The high-temperature, high-pressure gas-liquid mixed refrigerant enters the evaporator through the capillary tube, which will directly affect the cooling effect of the elevator air conditioner. Utility Model Content

[0003] In order to overcome the above-mentioned technical defects, this utility model provides an elevator air conditioner with secondary condensation function, which aims to solve the problems in the background art.

[0004] This utility model is implemented according to the following technical solution:

[0005] This utility model discloses an elevator air conditioner with secondary condensation function, comprising:

[0006] Compressor, condenser, and evaporator;

[0007] The output end of the compressor is connected to the input end of the condenser through a first pipe;

[0008] The output end of the condenser is connected to the input end of the evaporator through a second pipe;

[0009] The output end of the evaporator is connected to the input end of the compressor via a third pipe;

[0010] The second pipe has a heat exchange section, and the heat exchange section and the third pipe have an encasing portion, forming a pipe-in-pipe structure.

[0011] Compared with the prior art, this utility model, by setting up a pipe-in-pipe structure of the second and third pipes, utilizes the heat absorption effect of the low-temperature and low-pressure gaseous refrigerant in the third pipe to perform secondary condensation on the incompletely condensed gas-liquid mixture refrigerant in the second pipe. This effectively solves the problem of insufficient primary condensation under high-temperature conditions, ensuring that the refrigerant entering the evaporator is mainly in liquid state, and significantly improving the cooling effect.

[0012] In a preferred embodiment, the heat exchange section covers a portion of the third pipe.

[0013] In a preferred embodiment, the heat exchange pipe section is a U-shaped pipe.

[0014] In a preferred embodiment, the second pipe has a first capillary section, and the heat exchange section is connected to the output end of the condenser through the first capillary section.

[0015] In a preferred embodiment, the second pipe has a second capillary section, and the heat exchange pipe section is connected to the input end of the evaporator through the second capillary section.

[0016] In a preferred embodiment, the second capillary segment has a helical segment.

[0017] In a preferred embodiment, a filter is provided at the second capillary segment.

[0018] In a preferred embodiment, the evaporator is located above the condenser.

[0019] In a preferred embodiment, the input end of the condenser is located at the upper part of the condenser; the output end of the condenser is located at the bottom of the condenser.

[0020] In a preferred embodiment, the input end of the evaporator is located at the bottom of the evaporator; the output end of the evaporator is located at the top of the evaporator. Attached Figure Description

[0021] The specific embodiments of this utility model will be further described in detail below with reference to the accompanying drawings, wherein:

[0022] Figure 1 This is a perspective view of the elevator air conditioner with secondary condensation function according to this utility model.

[0023] Explanation of reference numerals in the attached figures:

[0024] 100 - Compressor, 200 - Condenser, 300 - Evaporator, 400 - First pipe, 500 - Second pipe, 510 - Heat exchange pipe section, 520 - First capillary section, 530 - Second capillary section, 531 - Spiral pipe section, 600 - Third pipe. Detailed Implementation

[0025] The preferred embodiments of the present invention will be described below with reference to the accompanying drawings. It should be understood that the preferred embodiments described herein are for illustration and explanation only and are not intended to limit the present invention.

[0026] To better illustrate this utility model, a further detailed description of this utility model is provided below with reference to the accompanying drawings.

[0027] The terminology used in the embodiments of this application is for the purpose of describing particular embodiments only and is not intended to limit the embodiments of this application. The singular forms “a,” “the,” and “the” used in the embodiments of this application and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise. It should also be understood that the term “and / or” as used herein refers to and includes any or all possible combinations of one or more of the associated listed items.

[0028] In the following description, when referring to the accompanying drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims. In the description of this application, it should be understood that the terms "first," "second," etc., are used only to distinguish similar objects and are not necessarily used to describe a specific order or sequence, nor should they be construed as indicating or implying relative importance. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0029] Combination Figure 1 As shown, this utility model discloses an elevator air conditioner with secondary condensation function, comprising:

[0030] Compressor 100, condenser 200, and evaporator 300;

[0031] The output end of the compressor 100 is connected to the input end of the condenser through the first pipe 400;

[0032] The output end of the condenser is connected to the input end of the evaporator through a second pipe 500;

[0033] The output end of the evaporator is connected to the input end of the compressor 100 through a third pipe 600;

[0034] The second pipe 500 has a heat exchange pipe section 510, and the heat exchange pipe section 510 and the third pipe 600 have a covering portion to form a pipe-in-pipe structure.

[0035] Compared with the prior art, this utility model, by setting up a pipe-in-pipe structure of the second pipe 500 and the third pipe 600, utilizes the heat absorption effect of the low-temperature and low-pressure gaseous refrigerant in the third pipe 600 to perform secondary condensation on the incompletely condensed gas-liquid mixture refrigerant in the second pipe 500, so that the gas-liquid mixture refrigerant becomes a high-pressure room-temperature liquid before entering the evaporator 300. This effectively solves the problem of insufficient primary condensation under high-temperature conditions, ensures that the refrigerant entering the evaporator 300 is mainly in liquid state, and significantly improves the cooling effect.

[0036] In this invention, the low-temperature, low-pressure gaseous refrigerant has a pressure of 8 to 10 kg and a temperature of 25 to 35°C; the high-pressure, room-temperature liquid has a pressure of 35 to 40 kg and a temperature of 50 to 60°C; the high-temperature, high-pressure gas has a pressure of 35 to 40 kg and a temperature of 90 to 100°C; and the high-temperature, high-pressure gas-liquid mixture has a pressure of 35 to 40 kg and a temperature of approximately 55°C.

[0037] The refrigerant circulation process of this elevator air conditioner is as follows:

[0038] The compressor 100 compresses the low-temperature, low-pressure gaseous refrigerant into a high-temperature, high-pressure gas. Under the influence of the high-temperature working environment, the high-temperature, high-pressure gas enters the condenser 200 through the first pipe 400 and is condensed into a high-temperature, high-pressure gas-liquid mixture. When the high-temperature, high-pressure gas-liquid mixture flows through the second pipe 500, it is condensed into a high-pressure, room-temperature liquid due to the low temperature of the third pipe 600. The high-pressure, room-temperature liquid enters the evaporator 300 and becomes a low-temperature, low-pressure gas. The low-temperature, low-pressure gas enters the compressor 100 through the third pipe 600, forming a cycle.

[0039] Furthermore, the heat exchange section 510 is partially covered by the third pipe 600. This partial coverage design allows for adjustment of the coverage ratio according to actual operating conditions (such as ambient temperature and cooling capacity requirements), flexibly adapting to high-temperature or normal-temperature environments, ensuring that the refrigerant reaches optimal subcooling before entering the evaporator 300, and improving cooling efficiency.

[0040] Furthermore, the heat exchange pipe section 510 is a U-shaped pipe. The U-shaped pipe avoids the long-distance laying required by the traditional straight pipe layout through its curved structure, increases the flow path length of the refrigerant in the heat exchange section 510, effectively increases the heat exchange area between the heat exchange pipe section 510 and the third pipe 600, and allows the high-temperature and high-pressure gas-liquid mixture to be fully converted into a high-pressure room-temperature liquid.

[0041] Furthermore, the second pipe 500 has a first capillary section 520, and the heat exchange pipe section 510 is connected to the output end of the condenser through the first capillary section 520. The capillary section acts as a throttling element, initially reducing the pressure of the high-temperature, high-pressure gas-liquid mixture refrigerant output from the condenser 200, lowering its pressure when entering the heat exchange pipe section 510, making it easier for the gas-liquid mixture refrigerant to be cooled into a liquid state within the heat exchange section 510.

[0042] Furthermore, the second pipe 500 has a second capillary section 530, and the heat exchange pipe section 510 is connected to the input end of the evaporator through the second capillary section 530. The capillary section acts as a throttling element, throttling the refrigerant after secondary condensation, reducing the pressure of the high-pressure room-temperature liquid refrigerant, and preventing incomplete evaporation of the refrigerant after entering the evaporator 300 due to excessive pressure.

[0043] Furthermore, the second capillary section 530 has a spiral section 531. The spiral structure increases the flow path length of the refrigerant within the capillary through its coiled design, providing sufficient length to allow the refrigerant pressure to gradually decrease as it flows toward the evaporator 300.

[0044] Furthermore, a filter is installed at the second capillary section 530. Elevator air conditioners operate in a high-temperature, enclosed car environment for extended periods, and dust, metal shavings, or moisture may mix into the refrigerant. The filter effectively removes solid impurities and liquid moisture from the second capillary section 530 through physical interception, preventing throttling failure or uneven flow due to blockage.

[0045] In one embodiment, the evaporator 300 is located above the condenser 200. The evaporator 300 and condenser 200 are arranged vertically to fully utilize the vertical space at the top of the elevator car and reduce lateral footprint, making it suitable for the limited space of small elevator shafts. The condensate produced by the evaporator 300 during operation can naturally drip onto the condenser 200 by gravity, helping the condenser 200 dissipate heat.

[0046] Furthermore, the input end of the condenser is located at the upper part of the condenser 200; the output end of the condenser is located at the bottom of the condenser 200. After the high-temperature, high-pressure gaseous refrigerant enters from the top, it flows downwards under gravity. Inside the condenser 200, the condensed liquid refrigerant naturally converges to the bottom and is discharged due to gravity, preventing the liquid refrigerant from accumulating at the top and causing localized overheating or uneven heat exchange, thus ensuring a highly efficient and stable condensation process.

[0047] Furthermore, the input end of the evaporator is located at the bottom of the evaporator 300; the output end of the evaporator is located at the top of the evaporator 300. With the input end at the bottom of the evaporator 300, the liquid refrigerant enters from the lowest point and spreads naturally under gravity, making full contact with the fins of the evaporator 300, resulting in a more uniform heat absorption and evaporation process. With the output end at the top, the gaseous refrigerant after evaporation from the liquid refrigerant is preferentially discharged, while the liquid refrigerant remains at the bottom due to gravity, preventing incompletely evaporated droplets from entering the compressor 100 with the gaseous refrigerant, thus extending the lifespan of the compressor 100.

[0048] Based on the disclosure and teachings of the above specification, those skilled in the art can make changes and modifications to the above embodiments. Therefore, this utility model is not limited to the specific embodiments disclosed and described above, and some modifications and changes to this utility model should also fall within the protection scope of the claims of this utility model. Furthermore, although some specific terms are used in this specification, these terms are only for convenience of explanation and do not constitute any limitation on this utility model.

Claims

1. An elevator air conditioner with secondary condensation function, characterized in that, include: Compressor, condenser, and evaporator; The output end of the compressor is connected to the input end of the condenser through a first pipe; The output end of the condenser is connected to the input end of the evaporator through a second pipe; The output end of the evaporator is connected to the input end of the compressor via a third pipe; The second pipe has a heat exchange section, and the heat exchange section and the third pipe have an encasing portion, forming a pipe-in-pipe structure.

2. The elevator air conditioner with secondary condensation function according to claim 1, characterized in that: The heat exchange section is covered by a portion of the third pipe.

3. The elevator air conditioner with secondary condensation function according to claim 2, characterized in that: The heat exchange pipe section is a U-shaped pipe.

4. The elevator air conditioner with secondary condensation function according to claim 2, characterized in that: The second conduit has a first capillary section. The heat exchange tube section is connected to the output end of the condenser via the first capillary tube section.

5. The elevator air conditioner with secondary condensation function according to claim 2, characterized in that: The second conduit has a second capillary section. The heat exchange tube section is connected to the input end of the evaporator via the second capillary tube section.

6. The elevator air conditioner with secondary condensation function according to claim 5, characterized in that: The second capillary segment has a helical tube section.

7. The elevator air conditioner with secondary condensation function according to claim 5, characterized in that: A filter is provided at the second capillary section.

8. The elevator air conditioner with secondary condensation function according to claim 1, characterized in that: The evaporator is located above the condenser.

9. The elevator air conditioner with secondary condensation function according to claim 1, characterized in that: The input end of the condenser is located at the top of the condenser; The output end of the condenser is located at the bottom of the condenser.

10. The elevator air conditioner with secondary condensation function according to claim 1, characterized in that: The input end of the evaporator is located at the bottom of the evaporator; The output end of the evaporator is located at the top of the evaporator.

Images