Pumping structure, compressor assembly and vehicle-mounted refrigerator

Abstract

The utility model provides a kind of oil pumping structure, compressor assembly and vehicle-mounted refrigerator, oil pumping structure includes oil suction pipe, oil suction pipe includes sequentially connected connecting section, transition section and oil suction section, the inner diameter of connecting section is greater than the inner diameter of oil suction section, connecting section is used to be connected with crankshaft, the end portion of oil suction section away from connecting section is provided with oil suction port, the length size of oil suction pipe is between 10mm to 15mm, the inner diameter of connecting section and the inner diameter of oil suction section ratio is between 1.2 to 1.5, the utility model is set to solve the problem that oil pumping structure in prior art is difficult to maintain its oil supply efficiency while reducing volume by above structure setting.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and more specifically, to an oil pump structure, a compressor assembly, and a vehicle refrigerator. Background Technology

[0002] Within the space of a car refrigerator, the reciprocating compressor assembly is a crucial refrigeration structure, and its miniaturization and performance optimization are core issues that the industry continues to explore. Currently, car compressor assemblies on the market generally suffer from excessive size and weight, which not only limits the effective space inside the refrigerator but also negatively impacts vehicle energy efficiency and handling, failing to meet the stringent requirements of car refrigerators for compact design and efficient space utilization. Therefore, the design goal of miniaturizing the compressor assembly requires that each component must be scaled down, and the design optimization of the oil pump structure, a key component ensuring the lubrication performance of the compressor assembly, is particularly important.

[0003] As the overall size of existing compressor components is reduced, the oil pump structure must also be reduced. However, the overall reduction in the size of the oil pump structure leads to a decrease in oil supply efficiency when the compressor components are in the low-frequency operating range, which in turn makes it impossible to effectively lubricate components such as the crankshaft. Utility Model Content

[0004] This invention provides an oil pump structure, a compressor assembly, and a vehicle refrigerator to solve the problem that existing oil pump structures cannot maintain their oil supply efficiency while reducing their size.

[0005] According to one aspect of the present invention, an oil pump structure is provided, including an oil suction pipe, which includes a connecting section, a transition section and an oil suction section connected in sequence. The inner diameter of the connecting section is larger than the inner diameter of the oil suction section. The connecting section is used to connect to a crankshaft. An oil suction port is provided at the end of the oil suction section away from the connecting section. The length of the oil suction pipe is between 10 mm and 15 mm. The ratio of the inner diameter of the connecting section to the inner diameter of the oil suction section is between 1.2 and 1.5.

[0006] Furthermore, the connecting section has a straight hole structure, and the ratio of the inner diameter of the connecting section to the diameter of the oil suction port is between 3.5 and 3.8.

[0007] Furthermore, the ratio of the length of the connecting section to the length of the transition section is between 3 and 3.5, and the ratio of the length of the connecting section to the length of the oil-absorbing section is between 1 and 1.5.

[0008] Furthermore, the pump structure also includes an oil guide plate, which is fixed inside the suction pipe and symmetrically arranged along the axis of the suction pipe.

[0009] Furthermore, the ratio of the length of the oil suction pipe to the length of the oil guide plate along the axis is between 1.5 and 1.8.

[0010] Furthermore, the shape of the two sides of the oil guide plate is adapted to the shape of the inner wall of the oil suction pipe. The oil guide plate has a first end and a second end that are arranged opposite to each other along the axial direction. The first end is located in the connecting section, and the second end is located in the oil suction section. The two sides of the first end are interference-fitted with the inner wall of the connecting section.

[0011] Furthermore, the side of the transition section is an inclined plane, and the angle between the inclined plane and the axis of the oil suction pipe is between 30° and 60°.

[0012] Furthermore, the length of the connecting segment is greater than or equal to 5 mm.

[0013] According to one aspect of the present invention, a compressor assembly is provided, including the above-described oil pump structure.

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

[0015] Applying the technical solution of this utility model, the oil suction pipe consists of a connecting section, a transition section, and an oil suction section. The connecting section has a larger inner diameter, designed to form a stable connection with the crankshaft. This not only ensures the overall stability of the pump structure but also guarantees sufficient lubricating oil flow during high-speed rotation, laying the foundation for the efficient operation of the compressor components. The oil suction section uses a smaller inner diameter and has an oil suction port at the end furthest from the connecting section. This design effectively enhances the lubricating oil suction speed through the centrifugal effect of fluid. Meanwhile, the overall length of the oil suction pipe is optimized to 10mm to 15mm. This simplification saves space without sacrificing pump efficiency, meeting the compact size requirements of automotive refrigerator compressors. The ratio of the inner diameter of the connecting section to the oil suction section is set between 1.2 and 1.5. This ratio ensures both the stability of the connecting section and the oil suction efficiency of the oil suction section, guaranteeing that lubricating oil can be smoothly and quickly transferred from the oil suction port to the crankshaft under both low-frequency and high-frequency operating conditions. This overcomes the problem of insufficient oil supply under low-frequency conditions caused by the small size of traditional structures. This significantly improves the overall performance of the pump structure and resolves the contradiction between compressor miniaturization and oil supply capacity. 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 pump structure provided by this utility model is shown;

[0018] Figure 2This invention provides a schematic diagram of the pump structure from another angle.

[0019] Figure 3 This application shows a schematic diagram illustrating the dimensions and structure of the connecting section, transition section, and oil-absorbing section.

[0020] Figure 4 A cross-sectional view of the pump structure in this application is shown;

[0021] Figure 5 This shows a cross-sectional view of the pump structure in this application from another angle;

[0022] Figure 6 This application shows Figure 5 A magnified view of a section at point B in the middle;

[0023] Figure 7 A schematic diagram of the oil guide plate is shown.

[0024] The above figures include the following reference numerals:

[0025] 10. Oil suction pipe;

[0026] 11. Connecting section;

[0027] 12. Transition section;

[0028] 13. Oil suction section;

[0029] 20. Oil suction port;

[0030] 30. Oil guide plate;

[0031] 31. First end;

[0032] 32. The second end. Detailed Implementation

[0033] 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.

[0034] like Figure 1 and Figure 2As shown, this embodiment of the utility model provides an oil pump structure, which includes an oil suction pipe 10. The oil suction pipe 10 includes a connecting section 11, a transition section 12, and an oil suction section 13 connected in sequence. The inner diameter of the connecting section 11 is larger than the inner diameter of the oil suction section 13. The connecting section 11 is used to connect to the crankshaft. An oil suction port 20 is provided at the end of the oil suction section 13 away from the connecting section 11. The length of the oil suction pipe 10 is between 10mm and 15mm, and the ratio of the inner diameter of the connecting section 11 to the inner diameter of the oil suction section 13 is between 1.2 and 1.5. Specifically, the length of the oil suction pipe 10 can be 10mm, 12mm, 13mm, 14mm, and 15mm. The ratio of the inner diameter of the connecting section 11 to the inner diameter of the oil suction section 13 can be 1.2, 1.3, 1.4, and 1.5. Figure 3 and Figure 4 As shown, in this embodiment, the inner diameter of the connecting section 11 is D1, the inner diameter of the oil suction section 13 is D2, and the length of the oil suction pipe 10 is H.

[0035] Applying the technical solution of this utility model, the oil suction pipe 10 consists of a connecting section 11, a transition section 12, and an oil suction section 13. The connecting section 11 has a larger inner diameter, designed to form a stable connection with the crankshaft. This not only ensures the overall stability of the pump structure but also guarantees sufficient lubricating oil flow during high-speed rotation, laying the foundation for the efficient operation of the compressor components. The oil suction section 13 uses a smaller inner diameter and has an oil suction port 20 at the end furthest from the connecting section 11. This design effectively enhances the lubricating oil suction speed through the centrifugal effect of the fluid. Meanwhile, the overall length of the oil suction pipe 10 is optimized to 10mm to 15mm. This simplification of dimensions saves significant space without sacrificing pump efficiency, meeting the compact size requirements of the vehicle refrigerator compressor. The ratio of the inner diameter of the connecting section 11 to the oil suction section 13 is set between 1.2 and 1.5. This ratio ensures both the stability of the connecting section 11 and the oil suction efficiency of the oil suction section 13, guaranteeing that lubricating oil can be smoothly and quickly transferred from the oil suction port 20 to the crankshaft under both low-frequency and high-frequency operating conditions. This overcomes the problem of insufficient oil supply under low-frequency conditions caused by the small size of traditional structures. This significantly improves the overall performance of the pump structure and resolves the contradiction between compressor miniaturization and oil supply capacity.

[0036] In this application, the ratio of the inner diameter of the connecting section 11 to the inner diameter of the oil suction section 13 is set between 1.2 and 1.5. This ratio is chosen to balance connection stability and oil suction efficiency, ensuring that lubricating oil can be smoothly and quickly transferred from the oil suction port 20 to the crankshaft under both low-frequency and high-frequency operating conditions. This significantly improves the overall performance of the pump structure and resolves the contradiction between compressor miniaturization and oil supply capacity. If the ratio of the connecting section 11 to the oil suction section 13 is less than 1.2, that is, the diameter of the connecting section 11 is too close to or smaller than the diameter of the oil suction section 13, the narrow connecting section 11 will increase the flow resistance of lubricating oil, especially under low-frequency operating conditions, which may lead to insufficient lubricating oil supply and further affect the stable operation of the compressor and the life of its components. If the ratio of connecting section 11 to oil suction section 13 is higher than 1.5, that is, the length of connecting section 11 is significantly greater than that of oil suction section 13, the centrifugal force on the lubricating oil is significantly reduced under low-frequency operating conditions, making it difficult to form effective power accumulation. This leads to difficulty in the upward movement of lubricating oil and may even affect the starting and continuous operation capability of the compressor components. Ultimately, the compressor components may fall into a vicious cycle of low lubrication efficiency and reduced efficiency.

[0037] Specifically, the connecting section 11 has a straight hole structure, and the ratio of the inner diameter of the connecting section 11 to the diameter of the oil suction port 20 is between 3.5 and 3.8. In some specific embodiments of this application, the ratio of the inner diameter of the connecting section 11 to the diameter of the oil suction port 20 can be 3.5, 3.6, 3.7, and 3.8. Figure 4 As shown, in this embodiment, the diameter of the oil suction port 20 is limited to D3.

[0038] By setting the connecting section 11 as a straight hole structure, compared with the curved structure, a smoother transmission path for lubricating oil is provided, reducing flow resistance and ensuring efficient transmission of lubricating oil from the oil suction port 20 to the crankshaft. Furthermore, the straight hole structure provides an excellent installation space for the connection between the connecting section 11 and the crankshaft, making the connection between the connecting section 11 and the crankshaft more convenient.

[0039] If the ratio of the inner diameter of the connecting section 11 to the diameter of the oil suction port 20 is set to less than 3.5, the effective diameter of the connecting section 11 becomes too small relative to the oil suction port 20. This increases the resistance of the lubricating oil during transmission, especially at low frequencies, making it more difficult for the lubricating oil to rise, potentially failing to provide sufficient lubrication and further affecting the performance and lifespan of the compressor. Conversely, when this ratio is set to more than 3.8, the inner diameter of the connecting section 11 becomes too large relative to the diameter of the oil suction port 20. Under low-frequency operation, an excessively large diameter of the connecting section 11 results in insufficient upward force for the lubricating oil, making it difficult to overcome the effects of gravity and viscosity, thus reducing the lubrication effect. Under high-frequency or high-load conditions, due to centrifugal force, excessive lubricating oil may flow into the connecting section, wasting resources and potentially generating additional resistance due to excessive lubricating oil accumulation, even affecting the normal operation of the crankshaft.

[0040] Therefore, in this application, the ratio of the inner diameter of the connecting section 11 to the diameter of the oil suction port 20 is between 3.5 and 3.8. This allows the lubricating oil to meet lubrication requirements while avoiding unnecessary waste and turbulence, thereby improving the stability and efficiency of the pump oil. Especially under low-frequency operating conditions, this ratio effectively balances the intake and discharge of lubricating oil, preventing excessive oil volume from increasing the burden on the pump structure, or insufficient oil volume from causing wear and efficiency reduction. This improves the reliability and stability of the compressor components, further extending their service life.

[0041] The ratio of the length of connecting section 11 to the length of transition section 12 is between 3 and 3.5, and the ratio of the length of connecting section 11 to the length of oil-absorbing section 13 is between 1 and 1.5. Specifically, the ratio of the length of connecting section 11 to the length of transition section 12 can be 3, 3.2, or 3.5. The ratio of the length of connecting section 11 to the length of oil-absorbing section 13 can be 1, 1.1, 1.3, or 1.5. Figure 3 As shown, in this embodiment, the length of the connecting section 11 is limited to h1, the length of the transition section 12 is limited to h2, and the length of the oil-absorbing section 13 is limited to h3.

[0042] If the ratio of the length of connecting section 11 to the length of transition section 12 is less than 3, the length of connecting section 11 is too short, which will directly weaken its stability in contact with the crankshaft and reduce the effect of the interference fit. This may cause relative sliding or vibration between the connecting section and the crankshaft during compressor operation, especially at high speeds. This not only affects the mechanical strength and durability of the pump oil structure but may also lead to leakage of lubricating oil during transmission, seriously affecting the lubrication effect and the performance of the compressor component. If this ratio is higher than 3.5, the length of connecting section 11 will be excessively long, with a large difference compared to transition section 12. An excessively long connecting section 11 will significantly increase the resistance when the lubricating oil rises, reducing the upward ability of the lubricating oil at low frequencies. Even under centrifugal force, the lubricating oil will have difficulty quickly passing through the long connecting section 11 to reach the lubrication point of the crankshaft, which may lead to insufficient lubrication and affect the start-up and stable operation of the compressor component.

[0043] Therefore, in this embodiment, by limiting the ratio of the length of the connecting section 11 to the length of the transition section 12, and by limiting the ratio of the length of the connecting section 11 to the length of the oil suction section 13, it is ensured that the connecting section 11 has sufficient length to connect with the crankshaft, thus ensuring the stability of the connection between the connecting section 11 and the crankshaft. The appropriate length limitation of the transition section 12 ensures that the lubricating oil can smoothly transition in the transition section 12, avoiding the phenomenon of turbulence caused by the sudden change in diameter when the lubricating oil enters the larger diameter connecting section 11 through the smaller diameter oil suction section 13, reducing energy loss and improving pumping efficiency.

[0044] The length ratio of connecting section 11 to oil suction section 13 is set between 1 and 1.5. Specifically, if the length ratio of connecting section 11 to oil suction section 13 is less than 1, it means that the length of oil suction section 13 exceeds that of connecting section 11. An excessively long oil suction section 13 will significantly increase the transmission distance of lubricating oil from the oil suction port 20 to connecting section 11. This will not only directly increase the resistance to lubricating oil flow, but also make it difficult for lubricating oil to quickly and fully enter the connecting section under low-frequency operating conditions, thus affecting the starting and operating efficiency of the compressor. On the other hand, if the length ratio of connecting section 11 to oil suction section 13 exceeds 1.5, the length of connecting section 11 is significantly longer than that of oil suction section 13. The excessive extension of connecting section 11 may lead to an excessively deep connection with the crankshaft. This not only increases the complexity of the pump structure, but may also affect the continuous transmission of lubricating oil due to interference from crankshaft movement. Especially during high-speed operation, the residence time of lubricating oil in the connecting section increases, affecting the timely supply of lubricating oil and the optimization of fluid dynamics.

[0045] Therefore, the length ratio of connecting section 22 to suction section 13 affects the amount and speed of lubricating oil drawn in at suction port 20. By controlling the length ratio of connecting section 11 to suction section 13 within the aforementioned range, sufficient lubricating oil volume can be ensured while avoiding the possibility of a bulky pump structure and reduced oil suction efficiency due to an excessively long suction section 13. This design ensures that even under low-frequency operating conditions, lubricating oil can quickly and fully enter from suction port 20. Subsequently, with the help of centrifugal force, through the fluid dynamics optimization of transition section 12, it flows to connecting section 11 and finally reaches the crankshaft, ensuring that the compressor receives ideal lubrication at all operating stages and avoiding wear and efficiency reduction caused by poor lubrication.

[0046] like Figure 4 and Figure 5 As shown, the oil pump structure also includes an oil guide plate 30, which is fixed inside the oil suction pipe 10 and is symmetrically arranged along the axis of the oil suction pipe 10.

[0047] In this embodiment, in the operating environment of the compressor assembly's rotation, the oil guide plate 30, positioned within the oil suction pipe 10, effectively agitates the lubricating oil, ensuring that the lubricating oil rises stably and evenly even during low-frequency operation, thus improving the stability and reliability of the compressor assembly at low frequencies. Furthermore, in this embodiment, the oil guide plate 30 is symmetrically arranged along the axis of the oil suction pipe 10, ensuring that the lubricating oil experiences uniform force on both sides during its transmission from the oil suction port 20 to the crankshaft. This avoids flow deviation or turbulence caused by asymmetry, further enabling the oil guide plate 30 to balance the centrifugal force distribution of the lubricating oil, promoting uniform distribution of the lubricating oil across the cross-section of the oil suction pipe 10, thereby improving the uniformity and smoothness of lubricating oil transmission.

[0048] The ratio of the length of the oil suction pipe 10 to the length of the oil guide plate 30 along its axis is between 1.5 and 1.8. Specifically, the ratio can be 1.5, 1.6, 1.7, or 1.8. If the ratio is less than 1.5, it indicates that the oil guide plate 30 is too long relative to the oil suction pipe 10. Excessive elongation of the oil guide plate 30 leads to increased internal fluid friction, increased energy loss, and makes pumping the lubricating oil more difficult. If the ratio is greater than 1.8, it indicates that the oil suction pipe 10 is too large relative to the oil guide plate 30, suggesting that the oil guide plate 30 may not be able to adequately agitate the lubricating oil.

[0049] Therefore, the selection of the above ratio range firstly ensures that the guide plate 30 has sufficient length to cover and influence the main flow area of ​​the lubricating oil, especially during the low-frequency oiling stage of the suction pipe 10. The guide plate 30 can fully agitate the lubricating oil, enhance its kinetic energy, and promote the lubricating oil to overcome gravity and viscous resistance, smoothly rising to key lubrication parts such as the crankshaft. At the same time, it also provides space for the connection between the connecting section 11 and the crankshaft, avoiding interference between the guide plate 30 and the crankshaft after it is installed in the suction pipe 10, which could cause the guide plate 30 to bend.

[0050] like Figures 5 to 7 As shown, the shapes of the two sides of the oil guide plate 30 are adapted to the inner wall shape of the oil suction pipe 10. The oil guide plate 30 has a first end 31 and a second end 32 arranged opposite to each other along the axial direction. The first end 31 is located inside the connecting section 11, and the second end 32 is located inside the oil suction section 13. The two sides of the first end 31 are interference-fitted with the inner wall of the connecting section 11. Specifically, in this embodiment, the difference in the interference fit between the two sides of the first end of the oil guide plate 30 and the inner wall of the connecting section 11 is in the range of 0.2mm-0.3mm, and the interference fit section is not less than 1mm, specifically 1.1mm, 1.2mm, etc. The width of the second end of the oil guide plate 30 is equal to the inner diameter of the oil suction section 13. In other embodiments, the width of the lower end of the oil guide plate 30 may also be greater than the inner diameter of the oil suction section 13, so that the second end of the oil guide plate 30 is interference-fitted with the oil suction section 13.

[0051] In this embodiment, the shapes of both sides of the oil guide plate 30 are designed to match the shape of the inner wall of the oil suction pipe 10, facilitating the connection between the oil guide plate 30 and the inner wall of the oil suction pipe 10. By setting the difference in the interference fit between the oil guide plate 30 and the inner wall of the oil suction pipe 10 between 0.2mm and 0.3mm, and ensuring that the length of the interference fit section is not less than 1mm, not only is the fixing effect of the oil guide plate 30 enhanced, preventing loosening of the oil guide plate 30, but it also ensures that when the lubricating oil passes through this area, it will not leak or reduce the flow efficiency due to excessive gaps. On the contrary, the tight fit improves the pumping efficiency of the lubricating oil and reduces unnecessary turbulence and energy loss. Furthermore, in this embodiment, by setting the width of the second end of the oil guide plate 30 to be equal to the inner diameter of the oil suction pipe 10, the stable connection between the oil guide plate 30 and the oil suction pipe 10 is ensured while reducing the length of the interference fit between the oil guide plate 30 and the oil suction pipe 10, reducing the difficulty of the operator's work when assembling the oil guide plate 30 and the oil suction pipe 10.

[0052] Specifically, the side of the transition section 12 is an inclined plane, and the angle between the inclined plane and the axis of the oil suction pipe 10 is between 30° and 60°. More specifically, the angle between the inclined plane and the axis of the oil suction pipe 10 can be 30°, 40°, 45°, 50°, and 60°. For example... Figure 3 As shown, in this embodiment, the angle between the inclined plane and the oil suction pipe 10 is limited to α.

[0053] like Figure 3As shown, by designing the side of the transition section 12 as a slope, and adjusting the angle between this slope and the axis of the oil suction pipe 10 to between 30° and 60°, this angle is denoted as α in this embodiment. Specifically, if the angle between the slope of the transition section and the axis of the oil suction pipe is greater than 60°, the fluid dynamics change will be too slow when the lubricating oil transitions from the small-diameter oil suction section 13 to the large-diameter connecting section 11, which is insufficient to form effective kinetic energy accumulation. Conversely, when this angle is less than 30°, the slope of the transition section becomes too steep, and the lubricating oil will encounter strong fluid dynamic impacts when passing through the diameter change area, generating significant turbulence. Turbulence not only increases the energy consumption of the lubricating oil and reduces the pumping efficiency, but also leads to unstable lubricating oil flow, affecting the continuous supply of lubricating oil.

[0054] Therefore, in this embodiment, the above-mentioned numerical design achieves a smooth transition and kinetic energy optimization of the lubricating oil from the small-diameter suction section 13 to the large-diameter connecting section 11. Furthermore, it ensures that the lubricating oil maintains good fluidity in areas with abrupt diameter changes, avoids severe turbulence that may result from right-angle turns, reduces fluid resistance, and improves the continuity and efficiency of lubricating oil pumping.

[0055] In this application, the length of the connecting section 11 is greater than or equal to 5mm. Specifically, it can be 5mm, 5.5mm, 6mm, etc. By setting the length of the connecting section 11, sufficient installation space is provided for the connecting section 11 to connect with the crankshaft, ensuring the stability of the connection between the connecting section 11 and the crankshaft. Furthermore, sufficient space is provided for the installation of the connecting section 11 and the oil suction plate, making the overall structure of the device more stable.

[0056] In this embodiment, the area of ​​the oil suction port 20 is 6.5 mm. 2 Specifically, to ensure effective oil suction, the device extends into the oil sump to a depth of at least 5mm-10mm, specifically 5mm, 6mm, 7mm, 9mm, 10mm, etc., to ensure that the oil suction port 20 is below the lubricating oil surface in the oil sump, thereby ensuring that the oil suction port 20 can stably and continuously perform oil suction operations. It should be noted that in this embodiment, the insertion point into the oil sump can be the connecting section 11, the transition section 12, the oil suction section 13, or the crankshaft.

[0057] In other embodiments, a compressor assembly is provided, including the aforementioned oil pump structure.

[0058] In another embodiment, a vehicle refrigerator is provided, including the oil pump structure described above.

[0059] 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.

[0060] The technical features of the above embodiments can be combined in any way. 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 to be within the scope of this specification.

[0061] 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.

[0062] 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.

[0063] 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.

[0064] 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 beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would 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.

[0065] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this utility model.

Claims

1. A pump structure, characterized in that, The oil pump structure includes an oil suction pipe (10), which includes a connecting section (11), a transition section (12), and an oil suction section (13) connected in sequence. The inner diameter of the connecting section (11) is larger than the inner diameter of the oil suction section (13). The connecting section (11) is used to connect to the crankshaft. An oil suction port (20) is provided at the end of the oil suction section (13) away from the connecting section (11). The length of the oil suction pipe (10) is between 10 mm and 15 mm. The ratio of the inner diameter of the connecting section (11) to the inner diameter of the oil suction section (13) is between 1.2 and 1.

5.

2. The pump structure according to claim 1, characterized in that, The connecting section (11) has a straight hole structure, and the ratio of the inner diameter of the connecting section (11) to the diameter of the oil suction port (20) is between 3.5 and 3.

8.

3. The pump structure according to claim 1, characterized in that, The ratio of the length of the connecting section (11) to the length of the transition section (12) is between 3 and 3.5, and the ratio of the length of the connecting section (11) to the length of the oil-absorbing section (13) is between 1 and 1.

5.

4. The pump structure according to claim 1, characterized in that, The oil pump structure also includes an oil guide plate (30), which is fixed inside the oil suction pipe (10) and is symmetrically arranged along the axis of the oil suction pipe (10).

5. The pump structure according to claim 4, characterized in that, The ratio of the length of the oil suction pipe (10) to the length of the oil guide plate (30) along the axis is between 1.5 and 1.

8.

6. The pump structure according to claim 4, characterized in that, The shape of the two sides of the oil guide plate (30) is adapted to the shape of the inner wall of the oil suction pipe (10). The oil guide plate (30) has a first end (31) and a second end (32) arranged opposite to each other along the axial direction. The first end (31) is located in the connecting section (11), and the second end (32) is located in the oil suction section (13). The two sides of the first end (31) are interference-fitted with the inner wall of the connecting section (11).

7. The pump structure according to claim 1, characterized in that, The side of the transition section (12) is an inclined surface, and the angle between the inclined surface and the axis of the oil suction pipe (10) is between 30° and 60°.

8. The pump structure according to claim 5, characterized in that, The length of the connecting segment (11) is greater than or equal to 5 mm.

9. A compressor assembly, characterized in that, The pump structure includes any one of claims 1 to 8.

10. A vehicle-mounted refrigerator, characterized in that, The pump structure includes any one of claims 1 to 8.

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