Compressor and refrigerating system

Abstract

The utility model discloses a compressor and a refrigerating system. The compressor comprises a shell and a pump body assembly. An installation cavity is formed in the shell, and the pump body assembly is arranged in the installation cavity and mainly comprises a crankshaft, a main bearing, a compression air cylinder and an auxiliary bearing. The crankshaft extends in the height direction of the compressor and can rotate, and the main bearing and the auxiliary bearing are arranged on the crankshaft in a sleeving mode. An oil supply channel extending along the axis is arranged in the crankshaft and used for conveying lubricating oil. From the bottom end to the top end of the compressor, the crankshaft is sequentially provided with a first flow guide channel, a second flow guide channel and an exhaust hole at intervals, and the channels extend outwards from the oil supply channel to the surface of the crankshaft. The first flow guide channel is responsible for conveying lubricating oil to the auxiliary bearing, and the second flow guide channel is designed for supplying oil to the main bearing. The exhaust hole is provided with an extension structure protruding by a preset length. The problem that in the prior art, a rotor compressor is insufficient in oil supply capacity under the conditions of a small-diameter crankshaft, low lubricating oil injection amount and low-frequency operation of the compressor can be at least solved.

Description

TECHNICAL FIELD

[0001] The utility model relates to refrigeration technical field, specifically, a kind of compressor and refrigeration system. BACKGROUND

[0002] Rotor compressor is the key component about refrigeration in air conditioning system, it compresses gas by rotating movement. In rotor compressor, oil supply structure is an important part to ensure the reliable operation of machine, because it is responsible for providing necessary lubricating oil to moving parts, and sometimes also undertakes the role of cooling and sealing. In order to increase the rotating effect of internal components of compressor, piston, bearing and other moving parts inside rotor compressor need lubricating oil lubrication to reduce wear and maintain efficient operation when rotor compressor works.

[0003] In addition, the crankshaft of rotor compressor can be divided into blind hole crankshaft and through hole crankshaft according to the type of central oil hole on the crankshaft, a plurality of radial oil holes are opened in the radial direction of the crankshaft, and the radial oil holes are communicated with the central oil hole, so as to supply oil lubrication to the internal components of the compressor through the radial oil holes when the crankshaft rotates. However, the existing rotor compressor has the defect of insufficient oil supply. On the one hand, in order to reduce the energy consumption of the compressor, people make the rotor compressor more miniaturized by reducing the diameter of the crankshaft, which can reduce the energy consumption of the compressor, but the hole diameter of the central hole of the crankshaft will also be reduced, and the oil supply inside the rotor compressor cannot be satisfied. On the other hand, people make the rotor compressor more energy-saving and environment-friendly by reducing the oil injection amount of the compressor, which can reduce the cost, but the reduction of oil injection amount will directly lead to the unsatisfied oil supply of the rotor compressor. On the other hand, people make the rotor compressor run at low frequency to reduce its energy consumption, which can reduce the cost, but low frequency operation will weaken the centrifugal oil supply capacity of the rotor compressor, resulting in unsatisfied oil supply inside the rotor compressor. UTILITY MODEL CONTENTS

[0004] The main purpose of the utility model is to provide a kind of compressor and refrigeration system, at least solve the problem of insufficient oil supply of rotor compressor in small diameter crankshaft, low lubricating oil injection amount and low frequency operation of compressor in prior art.

[0005] According to one aspect of the utility model, a kind of compressor is provided, comprising:

[0006] The shell has a mounting cavity;

[0007] The pump body assembly is arranged in the mounting cavity, and the pump body assembly comprises a crankshaft, a main bearing, a compression cylinder and a secondary bearing;

[0008] The crankshaft is rotatably arranged 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, and the main bearing and the auxiliary bearing are respectively located at opposite sides of the compression cylinder and fix the compression cylinder on the crankshaft;

[0009] The crankshaft is provided with an oil supply channel extending along the axial direction of the crankshaft, and along the direction from the bottom end to the top end of the compressor, the crankshaft is sequentially and spacedly provided with a first flow guide channel, a second flow guide channel and an exhaust hole, the first flow guide channel, the second flow guide channel and the exhaust hole all extend from the oil supply channel to the outer circumferential side of the crankshaft and pass through the outer surface of the crankshaft, the exhaust hole is provided with an extension structure protruding from the outer circumferential side of the crankshaft by a predetermined length, the first flow guide channel is at least used for delivering lubricating oil to the auxiliary bearing, and the second flow guide channel is at least used for delivering lubricating oil to the main bearing.

[0010] Further, the extension structure is perpendicular to the axial direction of the crankshaft; or,

[0011] The extension structure is inclined to the bottom end of the compressor.

[0012] Further, 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 2mm.

[0013] Further, the cross-sectional shape of the internal passage of the extension structure includes at least one of a circle, an ellipse and a rectangle;

[0014] The extension structure is formed by a pipe, one side of the pipe extends into the exhaust hole;

[0015] The oil supply channel includes a through hole or a blind hole.

[0016] Further, the lowest operating frequency of the compressor is lower than 15Hz, and the amount of lubricating oil inside the compressor is 200ml to 350ml.

[0017] Further, the compressor further comprises a rotor core and a balance block, the rotor core is sleeved on the crankshaft, the balance block is arranged on the rotor core, a delivery hole extending along the radial direction of the crankshaft is arranged through the rotor core, and the delivery hole is in communication with the exhaust hole;

[0018] A delivery passage extending along the radial direction of the crankshaft is arranged through the balance block, the delivery passage is in communication with the exhaust hole, and the extension structure is formed by the balance block or the rotor core; or,

[0019] The pipe extends to the rotor core or the balance block.

[0020] Further, the compressor further comprises a rotor core sleeved on the crankshaft and a balance block arranged on the rotor core, and a delivery hole extending along a radial direction of the crankshaft is arranged on the rotor core.

[0021] A delivery channel extending along the radial direction of the crankshaft is arranged on the balance block.

[0022] Further, a delivery hole extending along the radial direction of the crankshaft is arranged on the rotor core, and the delivery hole is communicated with the pipe.

[0023] A delivery channel extending along the radial direction of the crankshaft is arranged on the balance block, the pipe is communicated with the delivery channel, and the extension structure is formed by the pipe and the rotor core or by the pipe and the balance block.

[0024] Further, the pipe is fixedly connected with the crankshaft by at least one of interference pressing, threaded connection, welding and bonding.

[0025] Further, a diameter of the hole at the outlet of the extension structure is greater than a diameter of the exhaust hole.

[0026] Further, the crankshaft comprises 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, the auxiliary bearing is sleeved on the short shaft section, and a diameter of the long shaft section is less than or equal to 16 mm and a diameter of the short shaft section is less than or equal to 14 mm.

[0027] Further, the first flow guide channel and the second flow guide channel each comprise at least one, when the first flow guide channel or the second flow guide channel comprises multiple, multiple first flow guide channels are arranged at intervals along an outer periphery of the crankshaft, and multiple second flow guide channels are arranged at intervals along the outer periphery of the crankshaft.

[0028] In another aspect, the application also relates to a refrigeration system comprising the above compressor.

[0029] In the utility model, the inventor sets the extension structure at the exhaust hole of the compressor, which can enhance the oil supply capacity of the compressor, so as to solve the problem of insufficient oil supply capacity of the rotor compressor in the prior art under the conditions of small diameter crankshaft, low lubricating oil injection amount and low frequency operation of the compressor. In actual work, a small amount of lubricating oil needs to be injected into the compressor first, and then the compressor is started, so that the crankshaft can rotate in the installation cavity. In the process of rotation of the crankshaft, the refrigerant (i.e. refrigerant) in the oil supply channel can be thrown out from the exhaust hole to the outside of the oil supply channel due to the centrifugal force, so that the airflow flowing in the height direction of the compressor can be generated in the oil supply channel. Since the compressor of the present application is provided with the extension structure protruding from the outer circumferential side of the crankshaft by a predetermined length at the exhaust hole, in the process of rotation of the crankshaft, the end of the extension structure away from the crankshaft has a greater centrifugal force, and since the extension structure is in communication with the oil supply channel, the greater centrifugal force can generate a stronger airflow in the oil supply channel. Under the action of the airflow, the oil surface height of the lubricating oil in the oil supply channel in the height direction of the compressor can be lifted, so that the lubricating oil surface is higher than the first and second flow guide channels, and finally flows out from the first and second flow guide channels to lubricate the auxiliary bearing and the main bearing respectively.

[0030] That is, compared with the existing compressor, the compressor of the present application sets the extension structure at the exhaust hole, so that the compressor can generate a stronger airflow at the exhaust hole without increasing the diameter of the crankshaft. Under the action of the stronger airflow, the pressure in the oil supply channel decreases, which can better suck the lubricating oil, so that the lubricating oil in the oil supply channel is lifted, and then the lubricating oil can better flow out from the first and second flow guide channels to lubricate the auxiliary bearing and the main bearing respectively. Therefore, due to the ingenious structural design of the compressor of the present application, a smaller diameter crankshaft can be used, and due to the action of the extension structure, a stronger centrifugal force can be generated at the end of the extension structure away from the crankshaft in the process of rotation of the crankshaft, so that the compressor of the present application still has strong oil supply capacity under the conditions of low lubricating oil injection amount and low frequency operation. BRIEF DESCRIPTION OF DRAWINGS

[0031] The drawings described herein are used to provide further understanding of the utility model and constitute a part of the utility model. The schematic embodiments of the utility model and the description thereof are used to explain the utility model and do not constitute improper limitation on the utility model. In the drawings:

[0032] Figure 1 The compressor disclosed in the first embodiment of the utility model is a sectional view at the first viewing angle;

[0033] Figure 2The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view.

[0034] Figure 3 The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view.

[0035] Figure 4 The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view.

[0036] Figure 5 The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view. Figure 4 The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view.

[0037] Figure 6 The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view.

[0038] Figure 7 The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view.

[0039] The utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a pump body assembly and rotor core at first visual angle's sectional view for first embodiment of the utility model discloses a pump body assembly and rotor core at second visual angle's structure diagram for embodiment of the utility model discloses a compressor at first visual angle's sectional view for second embodiment of the utility model discloses a compressor at first visual angle's sectional view for third embodiment of the utility model discloses a compressor at first visual angle's sectional view for fourth embodiment of the utility model discloses a compressor at first visual angle's sectional view.

[0040] 10, shell, 11, installation cavity, 20, pump body assembly, 21, crankshaft, 211, oil supply channel, 2111, through hole, 2112, blind hole, 212, first flow guide channel, 213, second flow guide channel, 214, exhaust hole, 215, long axis section, d1, diameter of long axis section, 216, eccentric section, 217, short axis section, d2, diameter of short axis section, 22, main bearing, 23, compression cylinder, 231, piston, 24, auxiliary bearing, L, predetermined length, 25, extension structure, 251, internal passage, 30, rotor core, 40, balance block, 401, delivery channel, 4011, connecting section, 4012, expansion section. DETAILED DESCRIPTION

[0041] It should be noted that the terms used herein are for the purpose of describing specific embodiments and are not intended to limit exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form unless the context clearly indicates otherwise, and it will be further understood that the terms "comprise" and / or "include" when used herein specify the presence of stated features, steps, operations, devices, components and / or combinations thereof.

[0042] It should be noted that the terms used herein are for the purpose of describing specific embodiments and are not intended to limit exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form unless the context clearly indicates otherwise, and it will be further understood that the terms "comprise" and / or "include" when used herein specify the presence of stated 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 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.

[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 in the middle), 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 from the outer periphery of the crankshaft 21 by a predetermined length L 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 can be 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 cannot be construed as limiting the scope of protection of this utility model.

[0074] 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.

Claims

1. A compressor characterized by, The compressor comprises: a housing (10) having a mounting cavity (11); a pump body assembly (20) arranged in the mounting cavity (11), the pump body assembly (20) comprising a crankshaft (21), a main bearing (22), a compression cylinder (23), and a secondary bearing (24); wherein the crankshaft (21) is rotatably arranged in the mounting cavity (11) and extends along the height direction of the compressor, the main bearing (22), the compression cylinder (23), and the secondary bearing (24) are all sleeved on the crankshaft (21), and the main bearing (22) and the secondary bearing (24) are respectively located on opposite sides of the compression cylinder (23) and fix the compression cylinder (23) on the crankshaft (21); an oil supply channel (211) extending along the axial direction of the crankshaft (21) is arranged in the crankshaft (21), and along the direction from the bottom end to the top end of the compressor, a first flow guide channel (212), a second flow guide channel (213), and an exhaust hole (214) are sequentially and spacedly arranged on the crankshaft (21), the first flow guide channel (212), the second flow guide channel (213), and the exhaust hole (214) all extend from the oil supply channel (211) to the outer circumferential side of the crankshaft (21) and pass through the outer surface of the crankshaft (21), an extension structure (25) protruding from the outer circumferential side of the crankshaft (21) by a predetermined length (L) is arranged at the exhaust hole (214), the first flow guide channel (212) is at least used for delivering lubricating oil to the secondary bearing (24), and the second flow guide channel (213) is at least used for delivering lubricating oil to the main bearing (22).

2. The compressor of claim 1, wherein, The extension structure (25) is perpendicular to the axial direction of the crankshaft (21); or The extension structure (25) is inclined to the bottom end of the compressor.

3. The compressor of claim 2, wherein, 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 of claim 1, wherein, The cross-sectional shape of the inner channel (251) of the extension structure (25) comprises at least one of a circle, an ellipse, and a rectangle; The extension structure (25) is formed by a pipe fitting, one side of the pipe fitting extends into the exhaust hole (214); The oil supply channel (211) comprises a through hole (2111) or a blind hole (2112).

5. The compressor of claim 1, wherein, The lowest operating frequency of the compressor is lower than 15 Hz, and the lubricating oil amount inside the compressor is 200-350 ml.

6. The compressor of claim 1, wherein, The compressor further comprises a rotor core (30) and a balance block (40), the rotor core (30) is sleeved on the crankshaft (21), the balance block (40) is arranged on the rotor core (30), a delivery hole extending along the radial direction of the crankshaft (21) is arranged through the rotor core (30), and the delivery hole communicates with the exhaust hole (214). The balance block (40) is provided with a delivery channel (401) extending in the radial direction of the crankshaft (21) and penetrating through the balance block (40), the delivery channel (401) is in communication with the exhaust hole (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 pipe, and the pipe extends to the rotor core (30) or the balance block (40).

7. The compressor of claim 4, wherein, The compressor further comprises 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 arranged on the rotor core (30), and the rotor core (30) is provided with a delivery hole extending in the radial direction of the crankshaft (21) and penetrating through the rotor core (30). The balance block (40) is provided with a delivery channel (401) extending in the radial direction of the crankshaft (21) and penetrating through the balance block (40).

8. The compressor of claim 7, wherein, The rotor core (30) is provided with a delivery hole extending in the radial direction of the crankshaft (21) and penetrating through the rotor core (30), and the delivery hole is in communication with the pipe; or The balance block (40) is provided with a delivery channel (401) extending in the radial direction of the crankshaft (21) and penetrating through the balance block (40), the pipe is in communication with the delivery channel (401), and the extension structure (25) is formed by the pipe and the rotor core (30) together or by the pipe and the balance block (40) together.

9. The compressor according to claim 4 or 7 or 8, characterized in that, The pipe is fixedly connected with the crankshaft (21) by at least one of interference pressing, threaded connection, welding and bonding.

10. The compressor of claim 1, wherein, The diameter of the hole at the outlet of the extension structure (25) is greater than the diameter of the exhaust hole (214).

11. The compressor of any one of claims 1 to 8, wherein, The crankshaft (21) comprises 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) of the compressor 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), and 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 of any one of claims 1 to 8, wherein, The first flow guide channel (212) and the second flow guide channel (213) each comprise at least one, when the first flow guide channel (212) or the second flow guide channel (213) comprises a plurality, a plurality of the first flow guide channels (212) are arranged at intervals along the outer periphery of the crankshaft (21), and a plurality of the second flow guide channels (213) are arranged at intervals along the outer periphery of the crankshaft (21).

13. A refrigeration system characterized by, The refrigeration system comprises the compressor according to any one of claims 1 to 12. The refrigeration system comprises the compressor according to any one of claims 1 to 12.

Images