Compressor and refrigeration system
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-02-14
- Publication Date
- 2026-08-14
AI Technical Summary
[0004]本发明的主要目的在于提供一种压缩机及制冷系统，至少解决现有技术中转子压缩机在小直径曲轴、低润滑油注油量以及压缩机低频运转条件下供油能力不足的问题
[0029]在本发明中，发明人通过在压缩机的排气孔处设置延长结构，便可以增强压缩机供油能力，如此便可以解决现有技术中转子压缩机在小直径曲轴、低润滑油注油量以及压缩机低频运转条件下供油能力不足的问题。实际工作时，需要先往压缩机的内部注入少许的润滑油，接着启动压缩机，曲轴便可以在安装腔内旋转。在曲轴转动的过程中，由于离心力的作用，供油通道内的冷媒(即制冷剂)便可以从排气孔处甩出至供油通道的外部，如此便可以在供油通道内产生沿压缩机的高度方向流动的气流。由于本申请的压缩机在排气孔处设置有凸出于曲轴的外周侧预定长度的延长结构，因此，在曲轴转动的过程中，延长结构上远离曲轴的一端具有更大的离心力，又由于延长结构与供油通道连通，故而更大的离心力可以在供油通道内产生更强的气流。在气流的作用下，可以抬升供油通道内的润滑油在压缩机的高度方向上的油面高度，使得润滑油油面高于第一导流通道和第二导流通道，最终从第一导流通道和第二导流通道流出分别对副轴承和主轴承进行润滑。
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Figure CN122565708A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of refrigeration technology, and more specifically, to a compressor and a refrigeration system. Background Technology
[0002] Rotary compressors are a common and crucial component in air conditioning systems, compressing gases through rotational motion. In a rotary compressor, the oil supply system is essential for reliable operation, as it provides necessary lubrication to moving parts and sometimes also functions as a cooling and sealing agent. During operation, to enhance the rotational efficiency of internal components, pistons, bearings, and other moving parts require lubrication to reduce wear and maintain efficient operation.
[0003] Furthermore, rotary compressor crankshafts can be classified into two types based on the type of central oil hole: blind-hole crankshafts and through-hole crankshafts. Several radial oil holes are formed in the radial direction of the crankshaft, and these radial holes communicate with the central oil hole, thus supplying lubrication to the internal components of the compressor during crankshaft rotation. However, existing rotary compressors suffer from insufficient oil supply. On one hand, to reduce compressor energy consumption, the crankshaft diameter is reduced to make the rotary compressor smaller. While this reduces energy consumption, it also reduces the diameter of the central bore, resulting in insufficient oil supply within the rotary compressor. On the other hand, reducing the amount of oil injected into the compressor makes it more energy-efficient and environmentally friendly. While this reduces costs, the reduced oil volume directly leads to insufficient oil supply. Finally, controlling the rotary compressor to operate at low frequencies reduces energy consumption. While this reduces costs, low-frequency operation weakens the centrifugal oil supply capacity of the rotary compressor, resulting in insufficient oil supply within the compressor. Summary of the Invention
[0004] The main objective of this invention is to provide a compressor and refrigeration system that at least solves the problems of insufficient oil supply capacity of existing rotary compressors under conditions of small-diameter crankshaft, low lubricating oil injection volume, and low-frequency operation of the compressor.
[0005] According to one aspect of the present invention, a compressor is provided, comprising:
[0006] A housing having a mounting cavity;
[0007] A pump body assembly, which is disposed within the mounting cavity, includes a crankshaft, a main bearing, a compression cylinder, and a secondary bearing.
[0008] The crankshaft is rotatably disposed in the mounting cavity and extends along the height direction of the compressor. The main bearing, the compression cylinder, and the auxiliary bearing are all sleeved on the crankshaft. The main bearing and the auxiliary bearing are respectively located on opposite sides of the compression cylinder and fix the compression cylinder to the crankshaft.
[0009] The crankshaft is provided with an oil supply channel extending along the axis of the crankshaft. Along the direction from the bottom end to the top end of the compressor, the crankshaft is provided with a first guide channel, a second guide channel and an exhaust port at intervals. The first guide channel, the second guide channel and the exhaust port all extend from the oil supply channel to the outer periphery of the crankshaft and pass through the outer surface of the crankshaft. The exhaust port is provided with an extension structure protruding a predetermined length from the outer periphery of the crankshaft. The first guide channel is used to supply lubricating oil to the auxiliary bearing at least, and the second guide channel is used to supply lubricating oil to the main bearing at least.
[0010] Furthermore, the extended structure is perpendicular to the axial direction of the crankshaft; or,
[0011] The extended structure is inclined toward the bottom end of the compressor.
[0012] Furthermore, along the radial direction of the crankshaft, the length of the extension structure protruding from the outer surface of the crankshaft is greater than or equal to 2 mm.
[0013] Furthermore, the cross-sectional shape of the internal channel of the extended structure includes at least one of a circle, an ellipse, and a rectangle;
[0014] The extension structure is formed by a pipe fitting, one side of which extends into the vent hole;
[0015] The oil supply channel includes through holes or blind holes.
[0016] Furthermore, the compressor has a minimum operating frequency of less than 15 Hz, and the amount of lubricating oil inside the compressor is 200 ml to 350 ml.
[0017] Furthermore, the compressor also includes a rotor core and a balance block. The rotor core is sleeved on the crankshaft, and the balance block is disposed on the rotor core. A conveying hole extending radially along the crankshaft is provided through the rotor core, and the conveying hole communicates with the exhaust hole.
[0018] A conveying channel extending radially along the crankshaft is provided through the balance block, the conveying channel communicating with the exhaust port, and the extension structure is formed by the balance block or the rotor core; or,
[0019] The tubular component extends to the rotor core or the counterweight.
[0020] Furthermore, the compressor also includes a rotor core and a balance block. The rotor core is sleeved on the crankshaft, the balance block is disposed on the rotor core, and a conveying hole extending radially along the crankshaft is provided through the rotor core.
[0021] The balance block is provided with a conveying channel extending radially along the crankshaft.
[0022] Furthermore, a conveying hole extending radially along the crankshaft is provided through the rotor core, and the conveying hole communicates with the pipe fitting; or,
[0023] A conveying channel extending radially along the crankshaft is provided through the balance block. The pipe is connected to the conveying channel. The extension structure is formed by the pipe and the rotor core or by the pipe and the balance block.
[0024] Furthermore, the fitting is fixedly connected to the crankshaft by at least one of the following methods: interference fit, threaded connection, welding, and bonding.
[0025] Furthermore, the diameter of the outlet of the extended structure is larger than the diameter of the exhaust port.
[0026] Furthermore, the crankshaft includes a long shaft section, an eccentric section, and a short shaft section connected in sequence. The rotor core and the main bearing are sleeved on the long shaft section, the piston of the compression cylinder is sleeved on the eccentric section, and the auxiliary bearing is sleeved on the short shaft section. The diameter of the long shaft section is less than or equal to 16 mm, and the diameter of the short shaft section is less than or equal to 14 mm.
[0027] Furthermore, both the first flow channel and the second flow channel include at least one. When the first flow channel or the second flow channel includes multiple channels, the multiple first flow channels are spaced apart along the outer periphery of the crankshaft, and the multiple second flow channels are spaced apart along the outer periphery of the crankshaft.
[0028] On the other hand, this application also mentions a refrigeration system, which includes the compressor described above.
[0029] In this invention, the inventors enhance the compressor's oil supply capacity by providing an extended structure at the compressor's exhaust port. This solves the problem of insufficient oil supply capacity in existing rotary compressors under conditions of small-diameter crankshafts, low lubricating oil volume, and low-frequency compressor operation. In actual operation, a small amount of lubricating oil is first injected into the compressor, then the compressor is started, allowing the crankshaft to rotate within the mounting cavity. During crankshaft rotation, due to centrifugal force, the refrigerant in the oil supply channel is thrown out from the exhaust port to the outside of the oil supply channel, thus generating an airflow along the compressor's height within the oil supply channel. Because the compressor of this application has an extended structure protruding a predetermined length from the outer periphery of the crankshaft at the exhaust port, the end of the extended structure furthest from the crankshaft has a greater centrifugal force during crankshaft rotation. Furthermore, since the extended structure is connected to the oil supply channel, this greater centrifugal force generates a stronger airflow within the oil supply channel. Under the action of airflow, the oil level of the lubricating oil in the oil supply channel can be raised in the height direction of the compressor, so that the oil level of the lubricating oil is higher than that of the first guide channel and the second guide channel, and finally flows out from the first guide channel and the second guide channel to lubricate the auxiliary bearing and the main bearing respectively.
[0030] In other words, compared to existing compressors, the compressor of this application, by incorporating an extended structure at the exhaust port, can generate a stronger airflow at the exhaust port without increasing the crankshaft diameter. Under the influence of this stronger airflow, the pressure in the oil supply channel decreases, resulting in better suction of the lubricating oil and raising the oil level in the supply channel. This allows the lubricating oil to flow more effectively from the first and second guide channels, respectively, to lubricate the auxiliary and main bearings. Therefore, due to its ingenious structural design, the compressor of this application can use a smaller diameter crankshaft. Furthermore, the extended structure generates a stronger centrifugal force at the end of the extended structure away from the crankshaft during rotation, enabling the compressor of this application to maintain a strong oil supply capacity even under conditions of low lubricating oil volume and low-frequency operation. Attached Figure Description
[0031] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings:
[0032] Figure 1 A cross-sectional view of the compressor disclosed in the first embodiment of the present invention from a first perspective;
[0033] Figure 2 This is a structural diagram of the pump body assembly and rotor core disclosed in an embodiment of the present invention from a second perspective;
[0034] Figure 3 A cross-sectional view of the pump body assembly and rotor core disclosed in the first embodiment of the present invention from a first perspective;
[0035] Figure 4 A cross-sectional view of the compressor disclosed in the second embodiment of the present invention from a first perspective;
[0036] Figure 5 for Figure 4 Enlarged view of section A;
[0037] Figure 6 A first-view cross-sectional view of the compressor disclosed in the third embodiment of the present invention;
[0038] Figure 7 This is a cross-sectional view of the compressor disclosed in the fourth embodiment of the present invention from a first perspective.
[0039] The above figures include the following reference numerals:
[0040] 10. Housing; 11. Mounting cavity; 20. Pump body assembly; 21. Crankshaft; 211. Oil supply passage; 2111. Through hole; 2112. Blind hole; 212. First guide channel; 213. Second guide channel; 214. Exhaust port; 215. Long shaft section; d1. Diameter of long shaft section; 216. Eccentric section; 217. Short shaft section; d2. Diameter of short shaft section; 22. Main bearing; 23. Compression cylinder; 231. Piston; 24. Secondary bearing; L. Predetermined length; 25. Extension structure; 251. Internal passage; 30. Rotor core; 40. Balance block; 401. Conveying channel; 4011. Connecting section; 4012. Expansion section. Detailed Implementation
[0041] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.
[0042] 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 scope of exemplary embodiments according to the invention. 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.
[0043] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values of the components and steps set forth in these embodiments do not limit the scope of the 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 figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.
[0044] As mentioned in the background section, to make compressors smaller and more energy-efficient, methods such as reducing crankshaft diameter, decreasing oil supply, and controlling low-frequency operation of rotary compressors have been employed. However, these methods can lead to insufficient oil supply within the rotary compressor. Insufficient oil supply can cause wear between moving parts (such as crankshafts and bearings) and, in severe cases, damage to the internal structure of the compressor. Therefore, the inventors of this application have designed a novel rotary compressor that solves the problems of insufficient oil supply in existing rotary compressors under conditions of small-diameter crankshafts, low lubricating oil supply, and low-frequency operation.
[0045] See Figures 1 to 7 As shown, according to an embodiment of this application, a compressor is provided, which includes a housing 10, a pump body assembly 20, a rotor core 30, and a balance block 40.
[0046] Specifically, the housing 10 has a mounting cavity 11. The pump body assembly 20 is disposed within the mounting cavity 11, and the pump body assembly 20 includes a crankshaft 21, a main bearing 22, a compression cylinder 23, and a secondary bearing 24. The crankshaft 21 is rotatably disposed in the mounting cavity 11 and along the height direction of the compressor (i.e.,...). Figure 1 Extending in the direction indicated by y, the main bearing 22, the compression cylinder 23, and the auxiliary bearing 24 are all sleeved on the crankshaft 21, with the main bearing 22 and the auxiliary bearing 24 located on opposite sides of the compression cylinder 23, fixing the compression cylinder 23 to the crankshaft 21. A bearing 24 is provided inside the crankshaft 21 along the axial direction of the crankshaft 21 (i.e.,...). Figure 1 The oil supply passage 211 extends along the direction indicated by y in the middle, from the bottom to the top of the compressor (i.e., Figure 1(in the direction indicated by y), a first guide channel 212, a second guide channel 213 and an exhaust port 214 are sequentially and spaced apart on the crankshaft 21. The first guide channel 212, the second guide channel 213 and the exhaust port 214 all extend from the oil supply channel 211 to the outer periphery of the crankshaft 21 and pass through the outer surface of the crankshaft 21. An extension structure 25 protruding a predetermined length L from the outer periphery of the crankshaft 21 is provided at the exhaust port 214. The first guide channel 212 is used at least to deliver lubricating oil to the auxiliary bearing 24, and the second guide channel 213 is used at least to deliver lubricating oil to the main bearing 22.
[0047] In this application, the inventors enhance the oil supply capacity of the compressor by providing an extension structure 25 at the compressor's exhaust port 214. This solves the problem of insufficient oil supply capacity in existing rotary compressors under conditions of small-diameter crankshafts, low lubricating oil volume, and low-frequency compressor operation. In actual operation, a small amount of lubricating oil (200 ml to 350 ml as mentioned below) needs to be injected into the compressor first. Then, the compressor is started, and the crankshaft 21 rotates within the mounting cavity 11. During the rotation of the crankshaft 21, due to centrifugal force, the refrigerant in the oil supply channel 211 is thrown out from the exhaust port 214 to the outside of the oil supply channel 211, thus generating an airflow along the height direction of the compressor within the oil supply channel 211. Because the compressor of this application has an extension structure 25 protruding a predetermined length L from the outer periphery of the crankshaft 21 at the exhaust port 214, the end of the extension structure 25 away from the crankshaft 21 has a greater centrifugal force during the rotation of the crankshaft 21. Since the extension structure 25 is connected to the oil supply channel 211, the greater centrifugal force can generate a stronger airflow within the oil supply channel 211. Under the action of the airflow, the oil level of the lubricating oil in the oil supply channel 211 can be raised in the height direction of the compressor, making the lubricating oil level higher than the first guide channel 212 and the second guide channel 213. Finally, the lubricating oil flows out from the first guide channel 212 and the second guide channel 213 to lubricate the auxiliary bearing 24 and the main bearing 22, respectively.
[0048] In other words, compared to existing compressors, the compressor of this application, by providing an extension structure 25 at the exhaust port 214, allows the compressor to generate a stronger airflow at the exhaust port 214 without increasing the diameter of the crankshaft 21. Under the action of the stronger airflow, the pressure in the oil supply channel 211 decreases, which can better draw in the lubricating oil, raising the lubricating oil level in the oil supply channel 211. This allows the lubricating oil to flow out from the first guide channel 212 and the second guide channel 213 to better lubricate the auxiliary bearing 24 and the main bearing 22, respectively. Therefore, due to the ingenious structural design of the compressor of this application, a smaller diameter crankshaft 21 can be used. Furthermore, due to the effect of the extension structure 25, a stronger centrifugal force is generated at the end of the extension structure 25 away from the crankshaft 21 during rotation, thus enabling the compressor of this application to still have a strong oil supply capacity even under low lubricating oil volume and low frequency operation conditions.
[0049] Furthermore, the extension structure 25 is perpendicular to the axial direction of the crankshaft 21, or the extension structure 25 is inclined towards the bottom end of the compressor.
[0050] For example, the axial direction of crankshaft 21 is... Figure 1 The direction indicated by 'y'. In this application, when the extension structure 25 is perpendicular to the axis of the crankshaft 21, the extension structure 25 can extend along the radial direction of the crankshaft 21, or it can be offset from the radial direction of the crankshaft 21 within the plane containing the radial direction of the crankshaft 21. When the extension structure 25 is inclined towards the bottom end of the compressor, the extension structure 25 can be inclined towards the bottom end of the compressor within the plane containing the axis of the crankshaft 21, or it can be set at an acute angle to the plane containing the axis of the crankshaft 21. In order to make the compressor of this application have a better oil supply effect, in actual manufacturing, the extension structure 25 of this application is generally set to extend along the radial direction of the crankshaft 21. This setting not only has a better suction effect on lubricating oil, but also the stress on the extension structure 25 is more reasonable and less prone to damage. It should be noted that the reason why the extension structure 25 of this application does not tilt toward the top of the compressor is that if the extension structure 25 tilts toward the top of the compressor during the rotation of the crankshaft 21, the lubricating oil will be very easy to be thrown out from the compressor's exhaust port 214, resulting in an increased oil discharge rate, which in turn leads to an increase in the amount of lubricating oil required by the compressor. Therefore, the extension structure 25 does not tilt toward the top of the compressor.
[0051] Further, see Figure 4 and Figure 5As shown, the extension structure 25 protrudes from the outer surface of the crankshaft 21 by a length greater than or equal to 2 mm along the radial direction of the crankshaft 21. Specifically, when the extension structure 25 extends along the radial direction of the crankshaft 21, its predetermined length L needs to be greater than or equal to 2 mm. When the extension structure 25 is arranged in a way that is inclined towards the bottom of the compressor, its predetermined length L needs to have a projected length in the radial direction of the crankshaft 21 greater than or equal to 2 mm, that is, the effective length of the extension structure 25 in the radial direction of the crankshaft 21 is greater than or equal to 2 mm. If the effective length of the extension structure 25 in the radial direction of the crankshaft 21 is less than 2 mm, the oil supply effect of the compressor will be relatively poor, which may cause the compressor to fail to operate normally under conditions of small-diameter crankshaft, low lubricating oil injection, and low-frequency compressor operation.
[0052] Specifically, without considering the increase in compressor size, the longer the effective length of the extension structure 25 in the radial direction of the crankshaft 21, the greater the centrifugal force generated. This can be expressed by the formula F = mω. 2 The value of 'r' is reflected in the formula, where F is the centrifugal force, m is the mass, ω is the angular velocity of crankshaft 21, and r is the effective length of the extension structure 25 in the radial direction of crankshaft 21. The formula shows that a larger 'r' results in a larger centrifugal force, thus improving the compressor's oil supply performance. Existing compressors also use methods to increase centrifugal force to enhance oil supply, but these methods increase the diameter of crankshaft 21. While this increases centrifugal force, it also increases the size and weight of crankshaft 21, leading to increased costs and hindering cost savings.
[0053] Further, see Figure 1 , Figure 3 , Figure 4 , Figure 6 as well as Figure 7 As shown, the cross-sectional shape of the internal channel 251 of the extension structure 25 includes at least one of circular, elliptical, and rectangular shapes. The extension structure 25 is formed by a pipe fitting, one side of which extends into the vent port 214. The oil supply channel 211 includes a through hole 2111 or a blind hole 2112.
[0054] Specifically, the cross-sectional shape of the internal channel 251 of the extension structure 25 is the shape of the cross-section obtained by cutting the extension structure 25 along a direction perpendicular to the axis of the extension structure 25, and the axis of the extension structure 25 is... Figure 1The direction indicated by x. In this application, the cross-sectional shape of the internal channel 251 of the extension structure 25 can be circular, elliptical, or rectangular. The embodiments of this application show the case where the cross-sectional shape of the internal channel 251 of the extension structure 25 is circular. In actual manufacturing, in order to facilitate the installation of the extension structure 25 to the exhaust port 214 of the crankshaft 21, and to better connect the internal channel 251 of the extension structure 25 with the exhaust port 214, the compressor of this application generally sets the cross-sectional shape of the internal channel 251 of the extension structure 25 to be circular in actual manufacturing. In addition, the extension structure 25 is formed by a pipe, which can be a pipe that is installed separately at the exhaust port 214 and fixedly connected to the crankshaft 21, or a pipe formed by directly drilling holes in the rotor core 30 or the balance block 40 and communicating with the exhaust port 214. Moreover, the oil supply channel 211 of this application can be provided with a blind hole 2112 (i.e. Figure 1 , Figure 3 , Figure 4 as well as Figure 6 As shown), the oil supply passage 211 is along the axial direction of the crankshaft 21 (i.e., Figure 1 The direction indicated by 'y' extends but does not penetrate the crankshaft 21. The oil supply passage 211 can also be provided with a through-hole 2111 (i.e.,...). Figure 7 As shown), the oil supply passage 211 is along the axial direction of the crankshaft 21 (i.e., Figure 1 The direction indicated by y in the middle extends to completely penetrate the crankshaft 21.
[0055] Further, see Figure 1 , Figure 3 , Figure 4 , Figure 6 as well as Figure 7 As shown, the compressor operates at a frequency below 15 Hz, and the amount of lubricating oil inside the compressor is 200 ml to 350 ml.
[0056] Specifically, the amount of lubricating oil inside the compressor is set to 200 ml to 350 ml. This amount is relatively small compared to existing compressors. In other words, compared to existing compressors, the compressor of this application can still operate stably with a low lubricating oil level, requiring less lubricating oil, which can save costs to some extent. The reason for setting the lubricating oil amount to 200 ml to 350 ml is that when the lubricating oil amount is within this range, the lubricating oil can provide good lubrication for the compressor without causing waste or malfunction due to excessive lubricating oil. If the lubricating oil amount is less than 200 ml, it will not only fail to meet the lubrication requirements of the compressor, but also require a higher crankshaft speed, making it impossible for the compressor to meet the oil supply requirements under low-frequency operation conditions. If the lubricating oil amount is greater than 350 ml, it will not only increase costs to some extent, but also cause the lubricating oil to easily be thrown out of the extension structure 25 and into the oil supply channel 211 during crankshaft rotation.
[0057] Furthermore, in this application, the compressor can still meet the oil supply requirements when the operating frequency is below 15 Hz. Although existing compressors can still meet the oil supply requirements when the operating frequency is below 15 Hz, it is necessary to increase the diameter of the crankshaft 21 or increase the amount of lubricating oil inside the compressor to meet the oil supply requirements. This will not only increase the overall size of the compressor, but also increase the cost, making it inconvenient to use and save costs. Unlike existing compressors, the compressor in this application increases the centrifugal force at the end of the extension structure 25 away from the crankshaft 21 by adding an extension structure 25 at the exhaust port 214. The increase in centrifugal force will directly lead to a faster airflow velocity in the internal channel 251 of the extension structure 25. Since the pressure is lower at the faster flow velocity, the airflow in the oil supply channel 211 can be discharged from the extension structure 25 to the outside of the oil supply channel 211 due to the pressure difference. In this process, the oil supply channel 211 can play a good role in suction of lubricating oil, thereby delivering the lubricating oil to the first guide channel 212 and the second guide channel 213, and finally supplying the auxiliary bearing 24 and the main bearing 22 for lubrication, respectively.
[0058] Further, see Figure 1 , Figure 3 , Figure 4 , Figure 6 as well as Figure 7As shown, the compressor also includes a rotor core 30 and a balance block 40. The rotor core 30 is sleeved on the crankshaft 21, and the balance block 40 is disposed on the rotor core 30. A conveying hole (not shown in the drawings of this application) extending radially along the crankshaft 21 is provided through the rotor core 30, and the conveying hole communicates with the exhaust port 214. A conveying channel 401 extending radially along the crankshaft 21 is provided through the balance block 40, and the conveying channel 401 communicates with the exhaust port 214. The extension structure 25 is formed by the balance block 40 or the rotor core 30. Alternatively, a pipe can extend to the rotor core 30 or the balance block 40.
[0059] Specifically, the rotor core 30 is fitted onto the crankshaft 21, meaning that the rotor core 30 is directly mounted on the crankshaft 21, allowing the rotor core 30 and the components mounted on it to move synchronously with the rotation of the crankshaft 21. This design helps improve power transmission efficiency, reduce energy loss, and ensure a tight mechanical fit between the rotor core 30 and the crankshaft 21. A balance block 40 is placed on the rotor core 30. The function of the balance block 40 is to reduce vibration by increasing or adjusting the mass distribution, thereby improving the stability and smoothness of the system. Placing the balance block 40 on the rotor core 30 effectively counteracts the unbalanced forces caused by high-speed rotation, reducing noise and wear, and extending the compressor's service life. Furthermore, in some other embodiments of this application, the extension structure 25 can be formed by a rotor core 30 through which a conveying hole is provided, and the conveying hole is connected to the exhaust hole 214. Therefore, as the crankshaft 21 rotates continuously, the conveying hole enhances the centrifugal effect, thereby enhancing the gas flow in the oil supply channel 211, thus raising the lubricating oil level in the oil supply channel 211 and improving the lubrication effect of the compressor. Moreover, in this application, the extension structure 25 can also be formed by a balance block 40 through which a conveying channel 401 is provided, and the conveying channel 401 is connected to the exhaust hole 214. Similar to the conveying hole described above, the conveying channel 401 can also enhance the centrifugal effect as the crankshaft 21 rotates continuously, thereby raising the lubricating oil level in the oil supply channel 211 and improving the lubrication effect of the compressor.
[0060] Further, see Figure 1 , Figure 3 , Figure 4 , Figure 6 as well as Figure 7 As shown, a conveying hole (not shown in the accompanying drawings) extending radially along the crankshaft 21 is provided through the rotor core 30. The conveying hole is directly connected to the exhaust hole or the conveying hole is connected to the pipe. Alternatively, a conveying channel 401 extending radially along the crankshaft 21 is provided through the balance block 40. The pipe is connected to the conveying channel 401. The extension structure 25 is formed by the pipe and the rotor core 30 or by the pipe and the balance block 40.
[0061] Exemplarily, in this application, a conveying hole can be provided on the rotor core 30 and the conveying hole can be directly connected to the exhaust hole or the conveying hole can be connected to a pipe. Alternatively, a conveying channel 401 can be provided on the balance block 40 and the conveying channel 401 can be directly connected to the exhaust hole or to a pipe. Furthermore, a pipe can be directly connected to the exhaust hole 214 at a position on the crankshaft 21 that is offset from the rotor core 30 and the balance block 40. The first embodiment of this application (i.e....) Figure 1 and Figure 3 (as shown) and the fourth embodiment (i.e. Figure 7 The diagrams show a case where a pipe is directly connected to the exhaust port 214 at a position offset from the rotor core 30 and the balance weight 40 on the crankshaft 21. The second embodiment of this application (i.e....) Figure 4 The diagram shows a case where a conveying channel 401 is provided on the balance block 40 and the conveying channel 401 is connected to the pipe fitting. The third embodiment (i.e.) Figure 6 The diagram shows a configuration where a delivery channel 401 is provided on the balance block 40 and communicates with the exhaust port. In general, the purpose of the above-described extension structure configuration is to allow the compressor to use centrifugal force to expel air from the delivery channel 401 through the extension structure 25 when the crankshaft 21 rotates, thereby allowing lubricating oil to flow along the axial direction of the crankshaft 21 in the oil supply channel 211 (i.e.,...). Figure 1 (The direction indicated by y) flows.
[0062] Further, see Figure 1 , Figure 3 , Figure 4 , Figure 6 as well as Figure 7 As shown, the pipe fitting is fixedly connected to the crankshaft 21 by at least one of the following methods: interference fit, threaded connection, welding, and bonding. Specifically, the pipe fitting and the vent hole 214 can be connected by an interference fit (i.e., the pipe fitting is fixedly connected to the crankshaft 21 by interference fit), or they can be connected by threads that can mate with each other (i.e., the pipe fitting is fixedly connected to the crankshaft 21 by threaded connection), or the pipe fitting can be directly welded to the vent hole 214 of the crankshaft 21, or it can be bonded to the vent hole 214 of the crankshaft 21. The embodiment of this application shows the case where the pipe fitting is welded to the vent hole 214 of the crankshaft 21.
[0063] Further, see Figure 4 As shown, the orifice diameter at the outlet of the extended structure 25 is larger than that of the exhaust orifice. The gradually increasing orifice diameter within the extended structure along the fluid flow direction helps reduce flow resistance and enhances the suction effect. (See also...) Figure 4As shown, the outer diameter of the pipe is equal to the diameter of the vent hole 214. The conveying channel 401 includes a connecting section 4011 and an expansion section 4012. The connecting section 4011 is closer to the crankshaft 21 than the expansion section 4012. The pipe is connected to the conveying channel 401 through the connecting section 4011. The diameter of the connecting section 4011 is greater than or equal to the outer diameter of the pipe, and the diameter of the expansion section 4012 is greater than the diameter of the connecting section 4011.
[0064] Specifically, the arrangement of the pipe fitting's outer diameter being equal to the diameter of the exhaust port 214 ensures a good connection between the exhaust port 214 and the internal channel 251 of the pipe fitting when the pipe fitting is fixed at the exhaust port 214. This provides excellent sealing between the oil supply channel 211 and the pipe fitting, thereby enhancing the compressor's oil supply performance. Furthermore, in this application, the diameter of the connecting section 4011 is equal to the outer diameter of the extension structure 25, ensuring a tight seal between the connecting section 4011 and the extension structure 25. The diameter of the expansion section 4012 is larger than that of the connecting section 4011; that is, the internal diameters of the pipe fitting, the connecting section 4011, and the expansion section 4012 gradually increase. This arrangement not only facilitates the assembly of the pipe fitting and the connecting section 4011 but also reduces air resistance from the oil supply channel 211 to the delivery channel 401. This allows air in the oil supply channel 211 to be more easily discharged from the delivery channel 401 when the crankshaft 21 rotates, further enhancing the compressor's oil supply performance.
[0065] Further, see Figure 1 and Figure 3 As shown, the crankshaft 21 includes a long shaft section 215, an eccentric section 216, and a short shaft section 217 connected in sequence. The rotor core 30 and the main bearing 22 are sleeved on the long shaft section 215. The piston 231 of the compression cylinder 23 is sleeved on the eccentric section 216. The auxiliary bearing 24 is sleeved on the short shaft section 217. The diameter d1 of the long shaft section is less than or equal to 16 mm, and the diameter d2 of the short shaft section is less than or equal to 14 mm.
[0066] Specifically, the crankshaft 21 consists of a long shaft section 215, an eccentric section 216, and a short shaft section 217. This design allows the rotor core 30 and the main bearing 22 to be mounted on the long shaft section 215, ensuring an effective connection between the motor (not shown in the figure) containing the rotor core 30 and the pump body assembly 20, which is more conducive to the motor driving the compression cylinder 23 to work. Furthermore, the piston 231 is fitted onto the eccentric section 216, which is a key component for achieving reciprocating motion, enabling the piston 231 to perform linear reciprocating motion to complete the gas intake and compression process. The auxiliary bearing 24 is mounted on the short shaft section 217, which supports the end of the crankshaft 21, making the forces on the crankshaft 21 more balanced, helping to stabilize the operation of the crankshaft 21 and reduce vibration during rotation. The smaller diameters d1 (d1≤16 mm) of the long shaft section 215 and d2 (d2≤14 mm) of the short shaft section 217 not only reduce weight and material costs but also help reduce the rotational inertia of the crankshaft 21 and its components (such as the rotor core 30), thus improving the compressor's response speed. Because the crankshaft 21 uses smaller diameter long shaft section 215 and short shaft section 217, the internal structure of the compressor is more compact. This design facilitates compressor miniaturization, which is highly advantageous for household or portable devices.
[0067] Further, see Figure 1 and Figure 3 As shown, each of the first flow channel 212 and the second flow channel 213 includes at least one. When there are multiple first flow channels 212 or multiple second flow channels 213, the multiple first flow channels 212 are spaced apart along the outer periphery of the crankshaft 21, and the multiple second flow channels 213 are spaced apart along the outer periphery of the crankshaft 21.
[0068] Specifically, when the first guide channel 212 and the second guide channel 213 are spaced apart along the outer circumference of the crankshaft 21, the lubricating oil can be more evenly distributed across the entire circumference of the crankshaft. This helps improve lubrication and reduce wear between critical moving parts (such as the main bearing 22 and the auxiliary bearing 24). When there are multiple first guide channels 212 or second guide channels 213, the lubricating oil can contact the crankshaft 21, the main bearing 22, and the auxiliary bearing 24 over a larger area, thus increasing the surface area for heat exchange and improving cooling efficiency. This helps maintain the operating temperature of the crankshaft 21 and surrounding components within a safe range, preventing overheating that could lead to performance degradation or damage to the compressor. Furthermore, the guide channels spaced apart along the outer circumference of the crankshaft 21 (i.e., the first guide channel 212 and the second guide channel 213) can establish an oil film more quickly during compressor startup, reducing frictional losses between moving parts inside the compressor (such as the crankshaft 21, the main bearing 22, and the auxiliary bearing 24) during startup. This is especially important for the frequent start-stop of the compressor, as it can significantly reduce the risk of wear and improve the compressor's energy efficiency. A well-designed flow channel arrangement can also help improve the dynamic balance of the crankshaft 21 during rotation. The presence and flow of lubricating oil can dampen the internal components of the compressor, thereby reducing vibration and noise caused by motion imbalance.
[0069] On the other hand, this application also mentions a refrigeration system, such as an air conditioner, a refrigerator, and a freeze dryer, which includes the aforementioned compressor. Therefore, this refrigeration system includes all the technical effects of the aforementioned compressor. Since the technical effects of the compressor have already been described in detail above, they will not be repeated here.
[0070] As can be seen from the above description, this application, by setting up a compressor composed of a housing 10, a pump body assembly 20, a rotor core 30, and a balance block 40, can at least solve the problem of insufficient oil supply capacity of existing rotary compressors under conditions of small-diameter crankshafts, low lubricating oil injection, and low-frequency compressor operation. In this application, the main bearing 22 and the auxiliary bearing 24 respectively cooperate with and support the long shaft section 215 and the short shaft section 217 of the crankshaft 21. The crankshaft 21 has an axially extending oil supply channel 211 inside, and a first guide channel 212, a second guide channel 213, and an exhaust port 214 communicating with the central oil hole in the radial direction of the crankshaft 21. An extension structure 25 is provided at the exhaust port 214 at the top of the compressor. The extension structure 25 can increase the centrifugal force of the small-diameter crankshaft 21 during rotation, thereby increasing the airflow and velocity at the exhaust port 214, reducing the pressure in the oil supply channel 211 and the extension structure 25, which in turn causes the lubricating oil level in the oil supply channel 211 to rise. The rise in the lubricating oil level increases the oil supply of the compressor, which can reduce abnormal wear inside the compressor and ensure the normal operation of the compressor.
[0071] It is evident that the compressor of this application, through a simple structural design, can have good oil supply capacity under conditions of small-diameter crankshaft, low lubricating oil volume, and low-frequency operation. Compared with existing compressors, the compressor of this application can be applied to more complex conditions and can also save costs to a certain extent.
[0072] 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.
[0073] 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 should not be construed as limiting the scope of protection of this invention.
[0074] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.
Claims
1. A compressor, characterized in that, include: A housing (10) having a mounting cavity (11); Pump body assembly (20), the pump body assembly (20) is disposed in the mounting cavity (11), the pump body assembly (20) includes a crankshaft (21), a main bearing (22), a compression cylinder (23) and a secondary bearing (24); The crankshaft (21) is rotatably disposed in the mounting cavity (11) and extends along the height direction of the compressor. The main bearing (22), the compression cylinder (23) and the auxiliary bearing (24) are all sleeved on the crankshaft (21). The main bearing (22) and the auxiliary bearing (24) are respectively located on opposite sides of the compression cylinder (23) and fix the compression cylinder (23) on the crankshaft (21). The crankshaft (21) is provided with an oil supply channel (211) extending along the axial direction of the crankshaft (21). Along the direction from the bottom end to the top end of the compressor, the crankshaft (21) is provided with a first guide channel (212), a second guide channel (213), and an exhaust port (214) at intervals. The first guide channel (212), the second guide channel (213), and the exhaust port (214) all extend from the oil supply channel (211) to the outer periphery of the crankshaft (21) and pass through the outer surface of the crankshaft (21). The exhaust port (214) is provided with an extension structure (25) protruding from the outer periphery of the crankshaft (21) by a predetermined length (L). The first guide channel (212) is used to supply lubricating oil to the auxiliary bearing (24), and the second guide channel (213) is used to supply lubricating oil to the main bearing (22).
2. The compressor according to claim 1, characterized in that, The extension structure (25) is perpendicular to the axial direction of the crankshaft (21); or, The extension structure (25) is inclined toward the bottom end of the compressor.
3. The compressor according to claim 2, characterized in that, Along the radial direction of the crankshaft (21), the length of the extension structure (25) protruding from the outer surface of the crankshaft (21) is greater than or equal to 2 mm.
4. The compressor according to claim 1, characterized in that, The cross-sectional shape of the internal channel (251) of the extended structure (25) includes at least one of a circle, an ellipse, and a rectangle; The extension structure (25) is formed of a pipe, one side of which extends into the vent (214); The oil supply channel (211) includes a through hole (2111) or a blind hole (2112).
5. The compressor according to claim 1, characterized in that, The compressor has a minimum operating frequency of less than 15 Hz, and the amount of lubricating oil inside the compressor is 200 ml to 350 ml.
6. The compressor according to claim 1, characterized in that, The compressor also includes a rotor core (30) and a balance block (40). The rotor core (30) is sleeved on the crankshaft (21), and the balance block (40) is disposed on the rotor core (30). A conveying hole extending radially along the crankshaft (21) is provided through the rotor core (30), and the conveying hole communicates with the exhaust hole (214). A conveying channel (401) extending radially along the crankshaft (21) is provided through the balance block (40), the conveying channel (401) communicating with the exhaust port (214), and the extension structure (25) is formed by the balance block (40) or the rotor core (30); or, The extension structure (25) is formed by a tube that extends to the rotor core (30) or the counterweight (40).
7. The compressor according to claim 4, characterized in that, The compressor also includes a rotor core (30) and a balance block (40). The rotor core (30) is sleeved on the crankshaft (21), and the balance block (40) is disposed on the rotor core (30). A conveying hole extending in the radial direction of the crankshaft (21) is provided through the rotor core (30). The balance block (40) has a conveying channel (401) extending radially along the crankshaft (21).
8. The compressor according to claim 7, characterized in that, A conveying hole extending radially along the crankshaft (21) is provided through the rotor core (30), and the conveying hole communicates with the pipe fitting; or, The balance block (40) is provided with a conveying channel (401) extending radially along the crankshaft (21). The pipe is connected to the conveying channel (401). The extension structure (25) is formed by the pipe and the rotor core (30) or by the pipe and the balance block (40).
9. The compressor according to claim 4, 7, or 8, characterized in that, The fitting is fixedly connected to the crankshaft (21) by at least one of interference fit, threaded connection, welding and bonding.
10. The compressor according to claim 1, characterized in that, The diameter of the outlet of the extended structure (25) is larger than the diameter of the exhaust port (214).
11. The compressor according to any one of claims 1 to 8, characterized in that, The crankshaft (21) includes a long shaft section (215), an eccentric section (216), and a short shaft section (217) connected in sequence. The rotor core (30) of the compressor and the main bearing (22) are sleeved on the long shaft section (215). The piston (231) of the compression cylinder (23) is sleeved on the eccentric section (216). The auxiliary bearing (24) is sleeved on the short shaft section (217). The diameter (d1) of the long shaft section is less than or equal to 16 mm, and the diameter (d2) of the short shaft section is less than or equal to 14 mm.
12. The compressor according to any one of claims 1 to 8, characterized in that, The first flow channel (212) and the second flow channel (213) each include at least one. When the first flow channel (212) or the second flow channel (213) includes multiple, the multiple first flow channels (212) are spaced apart along the outer periphery of the crankshaft (21), and the multiple second flow channels (213) are spaced apart along the outer periphery of the crankshaft (21).
13. A refrigeration system, characterized in that, The refrigeration system includes the compressor according to any one of claims 1 to 12.