Vehicle-mounted refrigerator compressor and vehicle having the same

Abstract

This utility model provides a vehicle-mounted refrigerator compressor and a vehicle having the same, comprising: a housing; a pump body disposed within the housing, the pump body including a cylinder; a drive motor disposed within the housing, the drive motor including a stator and a rotor, the stator being disposed outside the rotor; and a crankshaft, one end of which is drivenly connected to the rotor, and the other end of which is drivenly connected to the cylinder; wherein the ratio of the outer diameter of the stator to the diameter of the cylinder is between 3 and 4, and the ratio of the eccentricity of the crankshaft to the diameter of the cylinder is between 0.2 and 0.45. The technical solution provided by this utility model addresses the problem in the prior art of balancing compressor size reduction and improved cooling-to-weight ratio.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and more specifically, to a vehicle-mounted refrigerator compressor and a vehicle having the same. Background Technology

[0002] The sales share of miniaturized car refrigerators is constantly increasing, especially with the continuous rise in sales and improved driving range of new energy vehicles, making built-in car refrigerators a potential standard feature. In the field of car refrigerators, the reciprocating compressor, as a core refrigeration component, remains a key focus of technological breakthroughs, particularly in miniaturization and performance optimization.

[0003] Existing vehicle-mounted compressors suffer from problems such as large size, heavy weight, and low cooling weight, making it difficult to meet the stringent space utilization requirements of vehicle refrigerators while also addressing energy efficiency issues. Therefore, how to further reduce compressor size, decrease overall weight, and increase cooling weight while ensuring effective cooling performance has become an urgent problem to be solved. Utility Model Content

[0004] This invention provides a vehicle-mounted refrigerator compressor and a vehicle having the same, in order to solve the problem in the prior art of how to balance compressor size reduction and cooling-to-weight ratio improvement.

[0005] According to one aspect of the present invention, a vehicle refrigerator compressor is provided, comprising: a housing; a pump body disposed within the housing, the pump body including a cylinder; a drive motor disposed within the housing, the drive motor including a stator and a rotor, the stator being disposed outside the rotor; and a crankshaft, the rotor being drivenly connected to one end of the crankshaft, and the other end of the crankshaft being drivenly connected to the cylinder; wherein the ratio of the outer diameter of the stator to the diameter of the cylinder is between 3 and 4, and the ratio of the eccentricity of the crankshaft to the diameter of the cylinder is between 0.2 and 0.45.

[0006] Furthermore, the outer diameter of the stator ranges from 50mm to 57mm.

[0007] Furthermore, the volume of the stator ranges from 30 cm³. 3 Up to 65cm 3 .

[0008] Furthermore, the radius of the crankshaft ranges from 10mm to 14mm.

[0009] Furthermore, the pump body also includes a piston, which is movably disposed within the cylinder. The crankshaft is driven to connect with the piston, and the ratio of the piston length to the cylinder length is between 0.5 and 0.6.

[0010] Furthermore, the cylinder has an exhaust port with an area of ​​5.8 mm². 2 Up to 6.5mm2 between.

[0011] Furthermore, the cylinder has an exhaust port, the wall thickness of which is between 1.2 mm and 1.6 mm.

[0012] Furthermore, the pump body also includes a cylinder seat, which is fixed inside the housing, and the cylinder is fixed inside the cylinder seat.

[0013] Furthermore, the vehicle refrigerator compressor also includes a connecting rod, which is located between the crankshaft and the piston. One end of the connecting rod is connected to the crankshaft, and the other end is connected to the piston. The crankshaft drives the piston to move through the connecting rod.

[0014] According to another aspect of the present invention, a vehicle is provided, including the above-described vehicle refrigerator compressor.

[0015] By applying the technical solution of this utility model, in the design of a vehicle refrigerator compressor, innovations in compressor performance and size are achieved by setting the ratio of the stator's outer diameter to the cylinder diameter between 3 and 4, and adjusting the ratio of the crankshaft eccentricity to the cylinder diameter to the range of 0.2 to 0.45. The specific ratio of the stator's outer diameter to the cylinder diameter aims to reduce the volume and weight of the motor assembly, while ensuring that the motor can efficiently drive the piston movement, thereby reducing the overall size of the compressor without sacrificing cooling capacity. The selection of the crankshaft eccentricity to the cylinder diameter ratio optimizes the compression ratio and piston operating efficiency. By adjusting this ratio, the piston's stroke within the cylinder and the cylinder's volume are limited. This not only promotes efficient refrigerant compression but also reduces unnecessary mechanical losses, thereby improving the compressor's energy efficiency ratio. Through the optimization of the above two ratio ranges, the compressor can maintain or even improve its cooling efficiency while maintaining a compact structure, ultimately achieving the goal of producing more cooling capacity with the same weight, or significantly reducing the overall weight of the compressor while achieving the same cooling effect. Attached Figure Description

[0016] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0017] Figure 1 A schematic diagram of the structure of the vehicle refrigerator compressor provided by this utility model is shown;

[0018] Figure 2 A schematic diagram of the shell structure in this application is shown;

[0019] Figure 3 A schematic diagram of the cylinder in this application is shown;

[0020] Figure 4 A schematic diagram of the stator in this application is shown;

[0021] Figure 5 This shows another structural schematic diagram of the vehicle-mounted refrigerator compressor in this application.

[0022] The above figures include the following reference numerals:

[0023] 10. Shell;

[0024] 20. Pump body;

[0025] 21. Cylinder;

[0026] 22. Piston;

[0027] 23. Cylinder seat;

[0028] 30. Drive motor;

[0029] 31. Stator;

[0030] 32. Rotor;

[0031] 40. Crankshaft;

[0032] 50. Exhaust port;

[0033] 60. Connecting rod. Detailed Implementation

[0034] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.

[0035] like Figure 1 and Figure 2As shown, this embodiment of the utility model provides a vehicle refrigerator compressor, which includes a housing 10, a pump body 20, a drive motor 30, and a crankshaft 40. The pump body 20 is disposed within the housing 10 and includes a cylinder 21. The drive motor 30 is disposed within the housing 10 and includes a stator 31 and a rotor 32, with the stator 31 positioned outside the rotor 32. The rotor 32 is drivenly connected to one end of the crankshaft 40, and the other end of the crankshaft 40 is drivenly connected to the cylinder 21. The ratio of the outer diameter of the stator 31 to the diameter of the cylinder 21 is between 3 and 4, specifically 3, 3.5, 3.7, and 4. The ratio of the eccentricity of the crankshaft 40 to the diameter of the cylinder 21 is between 0.2 and 0.45, specifically 0.2, 0.3, 0.35, 0.4, and 0.45. Figure 3 As shown, in this embodiment, the cylinder diameter is represented by D1. (As indicated...) Figure 4 As shown, the outer diameter of stator 31 is represented by D2.

[0036] By applying the technical solution of this utility model, in the design of a vehicle refrigerator compressor, innovations in compressor performance and size are achieved by setting the ratio of the outer diameter of the stator 31 to the diameter of the cylinder 21 between 3 and 4, and adjusting the ratio of the eccentricity of the crankshaft 40 to the diameter of the cylinder 21 to the range of 0.25 to 0.45. The specific ratio of the outer diameter of the stator 31 to the diameter of the cylinder 21 aims to reduce the volume and weight of the motor assembly, while ensuring that the motor can efficiently drive the piston 22, thereby reducing the overall size of the compressor without sacrificing cooling capacity. The selection of the ratio of the eccentricity of the crankshaft 40 to the diameter of the cylinder 21 optimizes the compression ratio and the operating efficiency of the piston 22. By adjusting this ratio, the stroke of the piston 22 within the cylinder 21 and the volume of the cylinder 21 are limited. This not only promotes efficient refrigerant compression but also reduces unnecessary mechanical losses, thereby improving the compressor's energy efficiency ratio. By optimizing the two ratio ranges mentioned above, the compressor can maintain or even improve its refrigeration efficiency while maintaining a compact structure. This ultimately achieves the goal of generating more cooling capacity with the same weight, or significantly reducing the overall weight of the compressor while achieving the same refrigeration effect.

[0037] like Figure 4As shown, in this embodiment, the outer diameter of the stator 31 ranges from 50mm to 57mm. Specifically, it can be 50mm, 55mm, or 57mm. If the outer diameter of the stator 31 is less than 50mm, the electromagnetic coupling strength may be insufficient, affecting the torque output of the motor and thus the cooling efficiency of the compressor. If the outer diameter of the stator 31 is greater than 57mm, although the electromagnetic coupling and torque output of the motor are enhanced, the size and weight of the compressor will be significantly increased. This application designs the outer diameter of the stator 31 within this specific size range, enabling the stator 31 to form an efficient electromagnetic coupling with the rotor 32, ensuring the driving performance of the motor. At the same time, because the outer diameter of the stator 31 is small, it helps to significantly reduce the size and total weight of the compressor, thereby improving the volumetric efficiency of the vehicle refrigerator and the cooling-to-weight ratio of the compressor.

[0038] Specifically, the volume of stator 31 ranges from 30 cm³. 3 Up to 65cm 3 Specifically, it could be 30cm. 3 40cm 3 45cm 3 50cm 3 and 65cm 3 This embodiment, by limiting this scope, aims to ensure that the motor has sufficient driving capability while remaining in the most compact size possible. This allows for a significant reduction in the overall size and weight of the compressor without sacrificing refrigeration efficiency, thereby improving the cooling-to-weight ratio of the vehicle refrigerator and achieving the dual effects of energy saving and space optimization.

[0039] Furthermore, if the volume of stator 31 is less than 30m³, the installation space for the electromagnetic components inside the motor (such as coils and iron cores) may be too cramped, affecting the layout and performance of the electromagnetic components. This would reduce the motor's driving capability, making it unable to effectively drive piston 22 to perform the necessary reciprocating compression motion. This would directly lead to a decrease in the compressor's cooling efficiency, affecting the cooling performance of the vehicle refrigerator. At the same time, an excessively small volume would also limit the motor's heat dissipation capacity, causing the motor temperature to be too high, affecting the stability and lifespan of the compressor.

[0040] Furthermore, when the volume of stator 31 exceeds 65cm³, although it can improve the driving capability and heat dissipation space of the motor to a certain extent, such a setting will increase the volume and weight of the compressor, further reducing the utilization rate of the interior space of the car refrigerator, increasing the burden on the vehicle, and reducing the range. At the same time, the large volume of stator 31 will reduce the cooling-to-weight ratio of the compressor, making it impossible to effectively improve the energy efficiency of the refrigeration system.

[0041] In this embodiment, the radius of the crankshaft 40 ranges from 10mm to 14mm. Specifically, it can be 10mm, 12mm, or 14mm. Specifically, if the radius of the crankshaft 40 is less than 10mm, it will affect the mechanical strength and durability of the crankshaft 40, leading to fatigue or damage under long-term operation and high load conditions, thus affecting the stability and service life of the compressor. Conversely, if the radius of the crankshaft 40 exceeds 14mm, although it will increase the strength and stability of the crankshaft 40, it will also increase the overall size and weight of the compressor, further reducing the cooling-to-weight ratio of the vehicle refrigerator.

[0042] Therefore, through the design within the aforementioned range, this embodiment enables the crankshaft 40 to balance strength and durability while reducing the size of the compressor. Furthermore, the appropriate selection of the crankshaft 40 radius optimizes its rotational inertia, reduces energy loss during operation, and improves the compressor's energy efficiency ratio. This effectively enhances the cooling-to-weight ratio of the vehicle refrigerator without sacrificing cooling performance; that is, it provides more cooling capacity at the same weight, or, with the same cooling capacity output, the compressor is lighter and smaller, offering greater flexibility for automotive interior design.

[0043] Furthermore, the pump body 20 also includes a piston 22, which is movably disposed within the cylinder 21. The crankshaft 40 is drivenly connected to the piston 22, and the ratio of the length of the piston 22 to the length of the cylinder 21 is between 0.5 and 0.6. Specifically, it can be 0.5, 0.52, 0.55, or 0.6. Figure 5 As shown, in this embodiment, the length of cylinder 21 is L1 and the length of piston 22 is L2.

[0044] By setting the ratio of the length of piston 22 to the length of cylinder 21 between 0.5 and 0.6, specifically, if this ratio is less than 0.5, it means that piston 22 is too short relative to cylinder 21. This results in a limited stroke of piston 22 within cylinder 21, preventing sufficient gas compression or exhaust, thus failing to achieve the ideal compression ratio and increasing the overall size and weight of the compressor. If this ratio is greater than 0.6, piston 22 becomes relatively too long, approaching or even exceeding the effective working length of cylinder 21. This causes piston 22 to make hard contact with the head or bottom of cylinder 21 at the end of its stroke, leading to mechanical collision, increased structural wear, and noise.

[0045] Therefore, in this embodiment, by limiting the aforementioned ratio, it is ensured that the piston 22 can complete a sufficient and effective stroke within the cylinder 21, ensuring that the refrigerant is compressed to the ideal pressure level to achieve a highly efficient cooling effect. Simultaneously, this helps to reduce the overall size and weight of the compressor, improving space utilization and portability.

[0046] like Figure 5As shown, in this embodiment, the cylinder 21 has an exhaust port 50, the area of ​​which is 5.8 mm². 2 Up to 6.5mm 2 Between. Specifically, it could be 5.8mm. 2 5.9mm 2 6mm 2 and 6.5mm 2 The area of ​​the exhaust port 50 of cylinder 21 in the vehicle refrigerator compressor is set between 5.8 mm² and 6.5 mm² to optimize the refrigerant flow performance and the compressor's energy efficiency ratio. Within this specific area range, the exhaust port 50 ensures back pressure during compression, effectively preventing refrigerant leakage when compressed to a high pressure state. It also promotes the smooth and rapid discharge of compressed refrigerant, avoiding increased energy consumption due to excessive exhaust resistance. This design helps maintain an ideal pressure gradient inside the compressor, improving refrigerant circulation efficiency and thus enhancing the compressor's cooling effect and energy efficiency ratio.

[0047] Specifically, if the exhaust port 50 area is less than 5.8 mm², firstly, the exhaust resistance will increase, directly affecting the compressor's exhaust efficiency, increasing energy consumption during compression, and thus reducing its energy efficiency ratio. Secondly, an excessively small exhaust port 50 area may also cause abnormally high internal pressure in the compressor, increasing the compressor's mechanical load and potentially leading to wear on the piston 22 and cylinder 21 components over long-term operation, shortening the compressor's lifespan. Furthermore, increased exhaust resistance may also cause noise and vibration problems during compressor operation, further affecting the passenger experience and compressor stability. Conversely, if the exhaust port 50 area exceeds 6.5 mm², although it can reduce exhaust resistance, the excessively large exhaust port 50 area will result in insufficient back pressure when the refrigerant is compressed to a high pressure state, affecting the efficiency of the compression process. This causes the refrigerant to be discharged before being fully compressed, thus reducing the compressor's cooling capacity and energy efficiency ratio. In addition, an excessively large exhaust port 50 area increases the risk of refrigerant leakage, not only affecting the cooling effect but also increasing the compressor's maintenance costs.

[0048] like Figure 5As shown, the wall thickness around the exhaust port 50 is between 1.2mm and 1.6mm. Specifically, in this embodiment, the wall thickness around the exhaust port 50 is A, and the value of A can be 1.2mm, 1.3mm, 1.5mm, and 1.6mm. Setting these values ​​effectively reduces the impact of clearance volume. Clearance volume refers to the volume of uncompressed refrigerant remaining in the cylinder 21 when the piston 22 reaches its top position. This volume plays a buffering and balancing role in the compression cycle, but it also affects the compressor's energy efficiency and cooling capacity. In this embodiment, by controlling the wall thickness around the exhaust port 50 within the above range, the clearance volume can be effectively managed, ensuring that the compressor reaches the preset compression ratio in each compression cycle. This prevents insufficient refrigerant compression due to an excessively large clearance volume, which would affect the cooling effect and energy efficiency ratio, and also prevents excessively high internal pressure in the compressor due to an excessively small clearance volume, which would increase energy consumption and potentially lead to excessive wear of the compressor components.

[0049] Specifically, if the wall thickness around the exhaust port 50 is less than 1.2 mm, the reduced wall thickness of the cylinder 21 material may lead to a decrease in structural strength. This is especially true when high-pressure gas passes through the exhaust port 50, making it prone to deformation or damage, thus increasing the risk of refrigerant leakage and reducing the reliability of the compressor and the overall efficiency of the refrigeration system. Conversely, if the wall thickness around the exhaust port 50 exceeds 1.6 mm, while it enhances the structural stability and sealing performance of the cylinder 21, it also increases the weight of the cylinder 21, which is detrimental to the miniaturization and lightweight design of the compressor.

[0050] In this embodiment, the pump body 20 also includes a cylinder seat 23, which is fixed inside the housing 10, and the cylinder 21 is fixed inside the cylinder seat 23. By providing the cylinder seat 23, a stable support can be provided for the cylinder 21, which promotes the overall stability of the machine body.

[0051] Furthermore, in this embodiment, the vehicle refrigerator compressor also includes a connecting rod 60, which is disposed between the crankshaft 40 and the piston 22. One end of the connecting rod 60 is connected to the crankshaft 40, and the other end is connected to the piston 22. The crankshaft 40 drives the piston 22 to move via the connecting rod 60. The connecting rod 60 converts the rotational motion of the crankshaft 40 into the linear reciprocating motion of the piston 22, thereby driving the refrigerant to circulate through compression and expansion within the cylinder 21.

[0052] The following table shows the specific embodiments and comparative data of this application:

[0053]

[0054] As can be seen from the above comparative data, the weight of the piston 22 compressor provided in the experimental group is only 86.4% of that in the control group, and the COP (Coefficient of Performance) of the compressor in the experimental group is 5% higher than that of the compressor in the control group, thus exhibiting higher cooling capacity. In other words, by using the value range and ratio range provided in this application, the size of the compressor can be further reduced, the total weight can be reduced, and the cooling-to-weight ratio of the compressor can be effectively improved.

[0055] In other embodiments, a vehicle is also provided, which includes the aforementioned vehicle-mounted refrigerator compressor.

[0056] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

[0057] The technical features of the above embodiments can be combined arbitrarily. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as the combination of these technical features does not contradict each other, it should be considered within the scope of this specification.

[0058] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0059] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0060] In the description of this utility model, it should be understood that the directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this utility model. The directional terms "inner" and "outer" refer to the inner and outer contours of each component itself.

[0061] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation besides the orientation of the device as described in the figures. For example, if the device in the figures is inverted, a device described as "above" or "on top of" other devices or structures will subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly. Furthermore, it should be noted that the use of terms such as "first," "second," etc., to define components is merely for the purpose of distinguishing the corresponding components; unless otherwise stated, these terms have no special meaning and therefore should not be construed as limiting the scope of protection of this utility model.

Claims

1. A vehicle-mounted refrigerator compressor, characterized in that, The vehicle-mounted refrigerator compressor includes: Shell (10); A pump body (20) is disposed within the housing (10), and the pump body (20) includes a cylinder (21). A drive motor (30) is disposed inside the housing (10). The drive motor (30) includes a stator (31) and a rotor (32). The stator (31) is disposed outside the rotor (32). A crankshaft (40) is driven to one end of the rotor (32), and the other end of the crankshaft (40) is driven to the cylinder (21); The ratio of the outer diameter of the stator (31) to the diameter of the cylinder (21) is between 3 and 4, and the ratio of the eccentricity of the crankshaft (40) to the diameter of the cylinder (21) is between 0.2 and 0.

45.

2. The vehicle-mounted refrigerator compressor according to claim 1, characterized in that, The outer diameter of the stator (31) ranges from 50 mm to 57 mm.

3. The vehicle-mounted refrigerator compressor according to claim 1, characterized in that, The volume of the stator (31) is in the range of 30 cm. 3 Up to 65cm 3 .

4. The vehicle-mounted refrigerator compressor according to claim 1, characterized in that, The radius of the crankshaft (40) ranges from 10 mm to 14 mm.

5. The vehicle-mounted refrigerator compressor according to claim 1, characterized in that, The pump body (20) also includes a piston (22), which is movably disposed in the cylinder (21). The crankshaft (40) is driven to connect with the piston (22), and the ratio of the length of the piston (22) to the length of the cylinder (21) is between 0.5 and 0.

6.

6. The vehicle-mounted refrigerator compressor according to claim 1, characterized in that, The cylinder (21) has an exhaust port (50) with an area of ​​5.8 mm². 2 Up to 6.5mm 2 between.

7. The vehicle-mounted refrigerator compressor according to claim 1, characterized in that, The cylinder (21) has an exhaust port (50) with a wall thickness of 1.2 mm to 1.6 mm around the exhaust port (50).

8. The vehicle-mounted refrigerator compressor according to claim 1, characterized in that, The pump body (20) also includes a cylinder seat (23), which is fixed inside the housing (10), and the cylinder (21) is fixed inside the cylinder seat (23).

9. The vehicle-mounted refrigerator compressor according to claim 5, characterized in that, The vehicle refrigerator compressor also includes a connecting rod (60), which is disposed between the crankshaft (40) and the piston (22). One end of the connecting rod (60) is connected to the crankshaft (40), and the other end of the connecting rod (60) is connected to the piston (22). The crankshaft (40) drives the piston (22) to move through the connecting rod (60).

10. A vehicle, characterized in that, The vehicle includes a vehicle-mounted refrigerator compressor as described in any one of claims 1 to 9.

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