Compressor and refrigeration apparatus

Abstract

A compressor and a refrigeration apparatus. The compressor comprises a housing, a crankshaft (1), and two bearings (2) sleeved on two shaft sections (12) of the crankshaft (1); a mating surface of each bearing (2) and the corresponding shaft section (12) is provided with a plurality of communication grooves (12a), a plurality of first oil grooves (2a), and a plurality of second oil grooves (2b) extending in the axial direction of the bearing (2); one of each shaft section (12) and the corresponding bearing (2) is provided with a plurality of communication grooves (12a), and the other one is provided with a plurality of first oil grooves (2a) and a plurality of second oil grooves (2b); the plurality of communication grooves (12a), the plurality of first oil grooves (2a), and the plurality of second oil grooves (2b) are all arranged at uniform intervals along the circumferential direction of the crankshaft (1). By means of an intermittent oil supply method, appropriate lubrication is maintained, and oil splashing is reduced.

Description

Compressors and refrigeration equipment

[0001] Related applications

[0002] This application claims priority to Chinese patent application No. 202510134488.5, filed on February 6, 2025, the entire contents of which are incorporated herein by reference. Technical Field

[0003] This application relates to the field of compressor technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0004] In air conditioning systems, crankshafts and bearings are key components, and their operating principles inevitably generate noise during operation. This noise typically has complex characteristics. Therefore, reducing crankshaft and bearing noise is crucial for improving the overall quietness of the air conditioning system and is a key consideration in product development.

[0005] Especially in bearing designs that separate high-pressure and low-pressure chambers, the pump body is one of the main sources of noise. The interconnected oil sump in traditional designs allows lubricating oil to flow from the high-pressure area to the low-pressure area under pressure differential; this flow sometimes occurs in the form of jets. Furthermore, such an oil sump design can generate additional excitation on the crankshaft and bearings, leading to greater noise and vibration problems during crankshaft operation. Summary of the Invention

[0006] The main objective of this application is to provide a compressor and refrigeration equipment that addresses the problem that when lubricating oil flows from the high-pressure zone to the low-pressure zone within the compressor, it can easily cause additional excitation to the compressor pump.

[0007] To achieve the above objectives, the compressor proposed in this application includes:

[0008] case;

[0009] A crankshaft, disposed within the housing and rotatable about its axis, the crankshaft including an eccentric portion and two shaft segments disposed on either side of the eccentric portion; and,

[0010] Two bearings are respectively sleeved on the periphery of the two shaft segments. The inner side of the two bearings, which are arranged opposite each other, is set as a high-pressure area, and the outer side of the two bearings, which are opposite to each other, is set as a low-pressure area.

[0011] Each bearing and the corresponding shaft segment have a plurality of oil grooves extending along the axial direction of the bearing on their mating surfaces. The plurality of oil grooves include a plurality of connecting grooves, a plurality of first oil grooves, and a plurality of second oil grooves. One of each shaft segment and the corresponding bearing is provided with the plurality of connecting grooves, and the other is provided with the plurality of first oil grooves and the plurality of second oil grooves spaced apart along the axial direction of the bearing. One end of each first oil groove is connected to the high-pressure area, and one end of each second oil groove is connected to the low-pressure area. During the crankshaft's rotational stroke, each connecting groove has a first position connected to the corresponding first oil groove and a second position connected to the second oil groove.

[0012] The plurality of connecting grooves are evenly spaced along the circumference of the crankshaft, the plurality of first oil grooves are evenly spaced along the circumference of the crankshaft, and the plurality of second oil grooves are evenly spaced along the circumference of the crankshaft.

[0013] In one embodiment, the plurality of connecting grooves are disposed on the shaft segment, and the plurality of first oil grooves and the plurality of second oil grooves are disposed on the bearing.

[0014] In one embodiment, the oil trough is arranged in a spiral shape; or,

[0015] The oil groove is inclined relative to the axial direction of the crankshaft.

[0016] In one embodiment, the crankshaft is rotatably disposed about a first clockwise direction, and the crankshaft has a first end and a second end disposed opposite to each other;

[0017] From the first end to the second end of the crankshaft, the first oil groove, the second oil groove, and the connecting groove all extend along the first clockwise direction.

[0018] In one embodiment, the length of the connecting groove in the axial direction of the crankshaft is L, and the distance between the ends of the first oil groove and the second oil groove that are close to each other in the circumferential direction of the bearing is D, wherein D / 10≤L≤4D.

[0019] In one embodiment, the number of the connecting slots is N1, where 2 ≤ N1 ≤ 4;

[0020] The number of the first oil tanks is N2, where 2≤N2≤4;

[0021] The number of the second oil tanks is N3, where 2 ≤ N3 ≤ 4.

[0022] In one embodiment, the ends of the first oil groove and the second oil groove that are close to each other are staggered in the circumferential direction of the bearing.

[0023] In one embodiment, the compressor is a rotary compressor.

[0024] This application provides a refrigeration device, the refrigeration device including a compressor, the compressor comprising:

[0025] case;

[0026] A crankshaft, disposed within the housing and rotatable about its axis, the crankshaft including an eccentric portion and two shaft segments disposed on either side of the eccentric portion; and,

[0027] Two bearings are respectively sleeved on the periphery of the two shaft segments. The inner side of the two bearings, which are arranged opposite each other, is set as a high-pressure area, and the outer side of the two bearings, which are opposite to each other, is set as a low-pressure area.

[0028] Each bearing and the corresponding shaft segment have a plurality of oil grooves extending along the axial direction of the bearing on their mating surfaces. The plurality of oil grooves include a plurality of connecting grooves, a plurality of first oil grooves, and a plurality of second oil grooves. One of the crankshaft and the two bearings is provided with the plurality of connecting grooves, and the other is provided with the plurality of first oil grooves and the plurality of second oil grooves spaced apart along the axial direction of the bearing. One end of each first oil groove is connected to the high-pressure area, and one end of each second oil groove is connected to the low-pressure area. During the crankshaft's rotational stroke, each connecting groove has a first position connected to the corresponding first oil groove and a second position connected to the second oil groove.

[0029] The plurality of connecting grooves, the plurality of first oil grooves, and the plurality of second oil grooves are evenly spaced along the circumferential direction of the crankshaft.

[0030] In one embodiment, the refrigeration equipment includes an air conditioner.

[0031] In the technical solution of this application, the lubricating oil in the high-pressure zone enters the multiple connecting grooves through the multiple first oil grooves. When the crankshaft rotates relative to the bearing, the multiple connecting grooves move to the first position and connect with the multiple first oil grooves respectively. Then, as the crankshaft continues to rotate, the multiple connecting grooves move to the second position and connect with the multiple second oil grooves respectively. The lubricating oil temporarily staying in the multiple connecting grooves flows into the multiple second oil grooves after an appropriate time interval and finally reaches the low-pressure zone. While maintaining proper lubrication through intermittent oil supply, it can also reduce oil spraying. By evenly arranging the multiple connecting grooves, the multiple first oil grooves, and the multiple second oil grooves along the circumference of the crankshaft, the lubricating oil can smoothly enter the multiple first oil grooves, the multiple connecting grooves, and the multiple second oil grooves simultaneously, regardless of the position of the crankshaft, avoiding instantaneous pressure imbalance, thereby reducing the excitation on the bearing and the crankshaft and reducing the problem of additional excitation of the compression pump by the lubricating oil. Attached Figure Description

[0032] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0033] Figure 1 is a cross-sectional schematic diagram of a partial structure of a compressor embodiment provided in this application;

[0034] Figure 2 is a schematic diagram of the crankshaft in the first position in Figure 1;

[0035] Figure 3 is a schematic diagram of the crankshaft in the second position in Figure 1;

[0036] Figure 4 is a schematic diagram of the crankshaft in Figure 2;

[0037] Figure 5 is a structural schematic diagram of the crankshaft in Figure 2 from another perspective;

[0038] Figure 6 is a structural schematic diagram of one embodiment of the bearing in Figure 2;

[0039] Figure 7 is a side view of the bearing in Figure 6;

[0040] Figure 8 is a cross-sectional view of the bearing in Figure 7;

[0041] Figure 9 is a structural schematic diagram of another embodiment of the bearing in Figure 2;

[0042] Figure 10 is a side view of the bearing in Figure 9;

[0043] Figure 11 is a cross-sectional view of the bearing in Figure 10.

[0044] Explanation of icon numbers:

[0045] 1. Crankshaft; 11. Eccentric part; 12. Shaft section; 12a. Connecting groove; 2. Bearing; 2a. First oil groove; 2b. Second oil groove.

[0046] The realization of the purpose, functional features and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Embodiments of the present invention

[0047] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0048] It should be noted that if the embodiments of this application involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0049] Furthermore, if the embodiments of this application involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution that simultaneously satisfies A and B. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed in this application.

[0050] Traditional oil sump designs allow lubricating oil to flow from high-pressure areas to low-pressure areas under pressure differentials; this flow can sometimes occur in the form of jets. Furthermore, such an oil sump design can exert additional stress on the crankshaft and bearings, leading to greater noise and vibration problems during crankshaft operation.

[0051] This application proposes a compressor designed to address the problem that when lubricating oil flows from the high-pressure zone to the low-pressure zone within the compressor, it can easily cause additional excitation to the compression pump.

[0052] Please refer to Figures 1 and 2. In one embodiment of this application, the compressor includes a housing, a crankshaft 1, and two bearings 2. The crankshaft 1 is disposed within the housing and is rotatable about its axis. The crankshaft 1 includes an eccentric portion 11 and two shaft segments 12 disposed on both sides of the eccentric portion 11. The two bearings 2 are respectively sleeved on the periphery of the two shaft segments 12. The inner sides of the two bearings 2, which are arranged opposite each other, are designated as high-pressure zones, and the outer sides of the two bearings 2, which are separated from each other, are designated as low-pressure zones. Multiple oil grooves extending axially along the bearing 2 are provided on the mating surfaces of each bearing 2 and the corresponding shaft segment 12. The multiple oil grooves include multiple connecting grooves 12a, multiple first oil grooves 2a, and multiple second oil grooves 2b. One of the shaft segment 12 and the corresponding bearing 2 is provided with the plurality of connecting grooves 12a, and the other is provided with the plurality of first oil grooves 2a and the plurality of second oil grooves 2b. One end of each first oil groove 2a is connected to the high-pressure area, and one end of each second oil groove 2b is connected to the low-pressure area. During its rotational stroke, each connecting groove 12a has a first position connected to the corresponding first oil groove 2a and a second position connected to the second oil groove 2b. The plurality of connecting grooves 12a are evenly spaced along the circumference of the crankshaft 1, the plurality of first oil grooves 2a are evenly spaced along the circumference of the crankshaft 1, and the plurality of second oil grooves 2b are evenly spaced along the circumference of the crankshaft 1.

[0053] It is understood that the crankshaft 1 is rotatably arranged around its axis, and each of the shaft segments 12 has multiple oil grooves on its surface. When the surface of the crankshaft 1 is provided with multiple connecting grooves 12a, then the bearing 2 is provided with multiple first oil grooves 2a and multiple second oil grooves 2b. When the surface of the crankshaft 1 is provided with multiple first oil grooves 2a and multiple second oil grooves 2b, the surface of the crankshaft 1 is provided with multiple connecting grooves 12a. The multiple connecting grooves 12a are used to guide the lubricating oil flowing into the multiple first oil grooves 2a to the multiple second oil grooves 2b. It is understood that when the crankshaft 1 rotates relative to the bearing 2, the lubricating oil flowing through the first oil grooves 2a, the connecting grooves 12a and the second oil grooves 2b can penetrate and cover all areas of the mating surface, thereby achieving lubrication between the crankshaft 1 and the bearing 2.

[0054] The first oil tank 2a, the connecting groove 12a, and the second oil tank 2b can have the same shape, or they can have different shapes. However, the connecting grooves 12a are all the same to form a rotationally symmetrical figure; the first oil tanks 2a are all the same to form a rotationally symmetrical figure; and the second oil tanks 2b are all the same to form a rotationally symmetrical figure.

[0055] In this way, the crankshaft 1 and the bearing 2 are in a balanced state in terms of mass distribution. When the lubricating oil flows, whether it reaches the multiple first oil grooves 2a, the multiple connecting grooves 12a, or the multiple second oil grooves 2b at the same time, it can maintain balance, thereby reducing the excitation of the bearing 2 and crankshaft 1 caused by the asymmetrical flow of oil, that is, reducing the additional force acting on the bearing 2 and crankshaft 1, thereby reducing noise and vibration.

[0056] In the technical solution of this application, lubricating oil in the high-pressure zone enters the multiple connecting grooves 12a through the multiple first oil grooves 2a. When the crankshaft 1 rotates relative to the bearing 2, the multiple connecting grooves 12a move to the first position, respectively connecting with the multiple first oil grooves 2a. Then, as the crankshaft 1 continues to rotate, the multiple connecting grooves 12a move to the second position, respectively connecting with the multiple second oil grooves 2b. The lubricating oil temporarily remaining in the multiple connecting grooves 12a flows into the multiple second oil grooves 2b after an appropriate time interval and eventually reaches the low-pressure zone. This intermittent oil supply maintains... While maintaining proper lubrication, oil spraying can also be reduced. By evenly arranging the multiple connecting grooves 12a, the multiple first oil grooves 2a, and the multiple second oil grooves 2b along the circumference of the crankshaft 1, the lubricating oil can smoothly enter the multiple first oil grooves 2a, the multiple connecting grooves 12a, and the multiple second oil grooves 2b simultaneously, regardless of the position of the crankshaft 1. The force acting on the bearing 2 and the shaft segment 12 is the same in the circumferential direction, avoiding instantaneous pressure imbalance, thereby reducing the excitation on the bearing 2 and the crankshaft 1, and reducing the problem of additional excitation of the compression pump by the lubricating oil.

[0057] Furthermore, in this embodiment, the plurality of connecting grooves 12a are disposed on the shaft segment 12, and the plurality of first oil grooves 2a and the plurality of second oil grooves 2b are disposed on the bearing 2.

[0058] Since the crankshaft 1 needs to mate with two bearings 2, if each shaft segment 12 is provided with the plurality of first oil grooves 2a and the plurality of second oil grooves 2b, and the crankshaft 1 includes two shaft segments 12, then the crankshaft 1 has too many oil grooves. Each additional oil groove creates a local weak point on the crankshaft 1. The accumulation of multiple oil grooves weakens the overall structural integrity of the crankshaft 1, leading to a decrease in its bending and torsional resistance. Furthermore, creating oil grooves removes a certain amount of material from the crankshaft 1, reducing the effective cross-sectional area available for load bearing and lowering the maximum load-bearing capacity of the crankshaft 1.

[0059] Thus, by setting the plurality of first oil grooves 2a and the plurality of second oil grooves 2b on the bearing 2, and distributing the two sets of first oil grooves 2a and second oil grooves 2b evenly on the two bearings 2, rather than setting them all on the crankshaft 1, excessive oil grooves are avoided from weakening the strength and rigidity of the crankshaft 1.

[0060] In some embodiments, the oil groove extends linearly along the axial direction of the bearing 2. This also achieves the purpose of intermittently delivering lubricating oil.

[0061] Specifically, the oil groove is inclined relative to the axial direction of the bearing 2. It can be understood that the inclination direction of the oil groove is consistent with the rotation direction of the crankshaft 1, which means that the flow direction of the lubricating oil can follow the inclination direction of the oil groove. The centrifugal force generated by the rotation of the crankshaft 1 causes the lubricating oil to naturally move along the path of the oil groove, which can reduce the resistance to the flow of lubricating oil.

[0062] In other embodiments, the oil trough is arranged in a spiral shape.

[0063] The oil grooves are arranged in a spiral shape along the circumference of the bearing 2, ensuring that the lubricating oil moves along the spiral path under pressure, rather than spreading randomly. The spiral shape of the oil grooves matches the flow direction of the lubricating oil with the rotation direction of the crankshaft 1. When the crankshaft 1 rotates, compared to straight or annular oil grooves which may cause some lubricating oil to flow backward or stagnate, the centrifugal force generated by the rotation of the crankshaft 1 assists the flow of the lubricating oil. The lubricating oil will naturally move along the path of the spiral grooves, reducing the resistance to the flow of the lubricating oil and making the flow smoother.

[0064] Furthermore, in this embodiment, the crankshaft 1 is rotatably arranged around a first clockwise direction, and the crankshaft 1 has a first end and a second end arranged opposite to each other; from the first end to the second end of the crankshaft 1, the first oil groove 2a, the second oil groove 2b and the connecting groove 12a all extend along the first clockwise direction.

[0065] It should be noted that the first clockwise direction can refer to either a clockwise or counterclockwise direction. In this design, the crankshaft 1 is arranged to rotate around the first clockwise direction. The first oil groove 2a, the second oil groove 2b, and the connecting groove 12a all extend along the first clockwise direction, indicating that the first oil groove 2a, the second oil groove 2b, and the connecting groove 12a are arranged in the same direction as the rotation of the crankshaft 1, rather than limiting the rotation direction of the crankshaft 1.

[0066] It is understood that if the extension direction of the oil groove is consistent with the rotation direction of the crankshaft 1 (i.e. both are clockwise), then during the rotation of the crankshaft 1, the forward-oriented oil groove will naturally push the lubricating oil along with the rotation of the crankshaft 1, rather than resisting the rotation direction of the crankshaft 1, so as to reduce the impact force of the liquid on the solid surface and thus reduce the excitation.

[0067] Conversely, if the oil groove extends counterclockwise while the crankshaft 1 rotates clockwise, the flow direction of the lubricating oil will be opposite to the rotation direction of the crankshaft 1. In this case, the oil groove must "flow upstream" to deliver the lubricating oil, resulting in higher fluid resistance and increased excitation or vibration caused by the oil flow impacting the surface of the crankshaft 1.

[0068] Furthermore, in this embodiment, the pitch of the oil groove is S, where 20mm ≤ S ≤ 600mm.

[0069] A smaller pitch (e.g., close to 20mm) allows the lubricant to contact different working surfaces more frequently, providing a denser lubrication coverage, but may also increase manufacturing difficulty and cost. A larger pitch (e.g., close to 600mm) simplifies the structure and reduces material usage, but may reduce the frequency of lubricant distribution, affecting lubrication performance. Setting the pitch between 20mm and 600mm strikes a balance between lubricant flow efficiency and system complexity.

[0070] In some other embodiments, referring to Figure 4, the angle between the length direction of the first oil groove 2a and the axial direction of the bearing 2 is set to A1, 5°≤A1≤90°, and the angle between the length direction of the second oil groove 2b and the axial direction of the bearing 2 is set to A2, 5°≤A2≤90°.

[0071] It should be noted that the length direction of the first oil groove 2a is the direction of the line connecting the two longest ends of the first oil groove 2a; the length direction of the second oil groove 2b is the direction of the line connecting the two longest ends of the second oil groove 2b. A straight line parallel to the axial direction of the bearing 2 is drawn from one end of the length direction of the first oil groove 2a, and the angle between this straight line and the length direction of the first oil groove 2a is A1. Similarly, a straight line parallel to the axial direction of the bearing 2 is drawn from one end of the length direction of the second oil groove 2b, and the angle between this straight line and the length direction of the second oil groove 2b is A2.

[0072] The first oil groove 2a and the second oil groove 2b are inclined and the included angle between them and the axial direction of the bearing 2 is set between 5° and 90°. The centrifugal force generated by the rotation of the crankshaft 1 can assist the flow of lubricating oil. The lubricating oil will naturally move along the path of the oil groove, reducing the resistance to the flow of lubricating oil and making the flow smoother.

[0073] In some other embodiments, please refer to Figure 4, the angle between the length direction of the connecting groove a and the axial direction of the crankshaft 1 is set to B, where 5°≤B≤90°.

[0074] It should be noted that the length direction of the connecting groove a is the direction of the line connecting the two ends of the connecting groove a with the longest distance. A straight line parallel to the axial direction of the crankshaft 1 is drawn from one end of the length direction of the connecting groove a, and the angle between this straight line and the length direction of the connecting groove a is B.

[0075] The connecting groove a is inclined and the angle between it and the axial direction of the crankshaft 1 is set between 5° and 90°. The centrifugal force generated by the rotation of the crankshaft 1 can assist the flow of lubricating oil. The lubricating oil will naturally move along the path of the connecting groove a, reducing the resistance to the flow of lubricating oil and making the flow smoother.

[0076] Furthermore, in some embodiments, the number of the connecting grooves 12a is N1, 2≤N1≤4; the number of the first oil grooves 2a is N2, 2≤N2≤4; and the number of the second oil grooves 2b is N3, 2≤N3≤4.

[0077] If too many oil tanks 2a, 12a and 2b are provided (more than 4), the lubricating oil will flow too frequently, causing unnecessary oil spraying, resulting in internal pressure fluctuations in the system, and thus increasing noise and vibration.

[0078] Furthermore, if too many oil grooves 2a, 12a and 2b are provided, the manufacturing process of the bearing 2 becomes more complicated, production costs increase, and the mechanical strength and lifespan of the bearing 2 are weakened.

[0079] Thus, by setting the number of the first oil tank 2a, the connecting groove 12a, and the second oil tank 2b to between 2 and 4, the lubricating oil can be effectively distributed and circulated, while maintaining the stability of the system and reducing noise and vibration.

[0080] It is understandable that the first oil tank 2a, the connecting groove 12a and the second oil tank 2b are set in the same number to effectively ensure the stability of lubricating oil transmission.

[0081] Furthermore, in this embodiment, the ends of the first oil groove 2a and the second oil groove 2b that are close to each other are staggered in the circumferential direction of the bearing 2.

[0082] It is understood that the first oil groove 2a and the second oil groove 2b are not directly aligned in the circumferential direction of the bearing 2, but are offset at a certain angle. The offset oil grooves can maintain the continuity of the inner wall material of the bearing 2 to a certain extent, and avoid structural weakening caused by excessive material reduction.

[0083] Furthermore, in this embodiment, the length of the connecting groove 12a in the axial direction of the crankshaft 1 is L, and the distance between the ends of the first oil groove 2a and the second oil groove 2b that are close to each other in the circumferential direction of the bearing 2 is D, wherein D / 10≤L≤4D.

[0084] This configuration, which places the first oil groove 2a and the second oil groove 2b at a considerable distance in the circumferential direction of the bearing 2, ensures that the connecting groove 12a requires a certain interval of time to connect with either the first oil groove 2a or the second oil groove 2b during rotation, thus better achieving the purpose of intermittent oil transfer.

[0085] Specifically, please refer to Figures 5 and 8. In this embodiment, the height of the bearing is H, the length of the first oil groove 2a in the axial direction of the bearing 2 is h1, the length of the second oil groove 2b in the axial direction of the bearing 2 is h2, and 0.8H≤h1+h2≤1.5H.

[0086] It should be noted that if the sum of h1 + h2 is too small, the contact area between the connecting groove 12a and the first or second oil groove 2b will be reduced. During the rotation of the crankshaft 1, the lubricating oil cannot be smoothly transferred from the first oil groove 2a to the connecting groove 12a, nor can it be smoothly transferred from the connecting groove 12a to the second oil groove 2b, thus affecting the lubricating oil transfer efficiency. As a result, the lubrication effect decreases, increasing the risk of friction and wear, and may also generate additional noise and vibration.

[0087] If the sum of h1 and h2 is too large, causing the length of the first or second oil groove 2b to exceed the end wall position of the connecting groove 12a, the lubricating oil may deviate from the preset direction during flow. An excessively long oil groove will change the path of the lubricating oil flow, causing some lubricating oil to fail to be effectively guided to the low-pressure area as designed, resulting in poor lubricating oil flow.

[0088] Therefore, setting h1+h2 between 0.8H and 1.5H ensures that the lengths of the first oil groove 2a and the second oil groove 2b provide sufficient contact area for smooth lubricant transfer, while preventing excessive length from affecting the flow direction and efficiency of the lubricant. This method achieves effective intermittent oil supply while maintaining system stability and quiet operation.

[0089] Furthermore, in this embodiment, the width of the oil groove is w, the depth of the oil groove is d1, and the inner diameter of the bearing 2 is d2, wherein d1≤w≤d2 / 4.

[0090] The width w of the oil groove must be greater than or equal to the depth d1 of the oil groove. The oil groove cannot be too narrow, otherwise it will affect the flow rate and fluidity of the lubricating oil. An appropriate width can ensure that enough lubricating oil can smoothly enter the oil groove and be effectively distributed to various parts that need lubrication when the crankshaft 1 rotates.

[0091] The width w of the oil groove is set to be less than or equal to d² / 4 to ensure that the oil groove is not too large, thereby avoiding weakening the structural strength of bearing 2. An excessively wide oil groove may cause the bearing 2 wall to become thinner, reducing its mechanical strength and thus affecting the life and reliability of bearing 2. At the same time, a smaller oil groove width also helps to maintain the concentration and directionality of the lubricating oil flow, preventing excessive diffusion or leakage of lubricating oil.

[0092] Furthermore, in this embodiment, the end walls of the first oil tank 2a and the second oil tank 2b at their closest points are configured as arc surfaces.

[0093] This design creates a smooth transition path, resulting in less resistance for the lubricating oil as it flows from one oil tank to another. Compared to right-angled edges or flat end walls, curved end walls reduce sudden changes in liquid flow, avoiding turbulence or vortices caused by abrupt angle changes.

[0094] Because of the reduced flow resistance, the lubricating oil can pass through the connection area between the oil grooves more smoothly, preventing the lubricating oil from stagnating or accumulating at the junction of the oil grooves, and ensuring that the lubricating oil is always in a dynamic flow state.

[0095] Specifically, in this embodiment, the compressor is a rotary compressor.

[0096] It should be noted that a rotary compressor is a device that compresses gas through rotational motion, primarily used in air conditioning and refrigeration systems. The rotary compressor utilizes one or more rotating components (such as a rotor) moving within a confined space to reduce the volume of gas and increase its pressure. Specifically, the rotary compressor contains an eccentrically mounted rotor. As the rotor rotates, a series of changing spaces are formed between it and the cylinder wall. These spaces gradually decrease, thereby achieving the intake, compression, and discharge of gas.

[0097] The symmetrically arranged oil grooves ensure that the torque generated by the lubricating oil flow is balanced at any rotational position, reducing the unbalanced force caused by the asymmetrical oil grooves, thereby reducing the vibration of the bearing 2 and the rotor compressor.

[0098] This application also proposes a refrigeration device, which includes a heat exchanger and a compressor. The specific structure of the compressor is as described in the above embodiments. Since this compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0099] The refrigeration equipment refers to a device or system used to lower the temperature and remove heat. The refrigeration equipment may be a refrigerator, freezer, or air conditioner, etc.

[0100] Specifically, in this embodiment, the refrigeration equipment includes an air conditioner. For the air conditioner, by arranging the plurality of first oil grooves 2a and the plurality of second oil grooves 2b on the bearing 2 as symmetrical about the axis of the bearing 2, and arranging the plurality of connecting grooves 12a on the crankshaft 1 as symmetrical about the axis of the bearing 2, the vibration and noise of the air conditioner can be reduced, providing a comfortable environment for the user.

[0101] The above description is merely an exemplary embodiment of this application and does not limit the patent scope of this application. Any equivalent structural transformations made based on the technical concept of this application and the contents of the specification and drawings of this application, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this application.

Claims

1. A compressor, wherein, The compressor includes: case; A crankshaft, disposed within the housing and rotatable about its axis, the crankshaft including an eccentric portion and two shaft segments disposed on either side of the eccentric portion; and, Two bearings are respectively sleeved on the periphery of the two shaft segments. The inner side of the two bearings, which are arranged opposite each other, is set as a high-pressure area, and the outer side of the two bearings, which are opposite to each other, is set as a low-pressure area. Each bearing and the corresponding shaft segment have multiple oil grooves on their mating surfaces. The multiple oil grooves include multiple connecting grooves, multiple first oil grooves, and multiple second oil grooves. One of each shaft segment and the corresponding bearing is provided with the multiple connecting grooves, and the other is provided with the multiple first oil grooves and the multiple second oil grooves. One end of each first oil groove is connected to the high-pressure area, and one end of each second oil groove is connected to the low-pressure area. During the crankshaft's rotational stroke, each connecting groove has a first position connected to the corresponding first oil groove and a second position connected to the second oil groove. The plurality of connecting grooves are evenly spaced along the circumference of the crankshaft, the plurality of first oil grooves are evenly spaced along the circumference of the crankshaft, and the plurality of second oil grooves are evenly spaced along the circumference of the crankshaft.

2. The compressor of claim 1, wherein, The plurality of connecting grooves are provided on the shaft segment, and the plurality of first oil grooves and the plurality of second oil grooves are provided on the bearing.

3. The compressor of claim 1 or 2, wherein, The oil trough is arranged in a spiral shape; or... The oil groove is inclined relative to the axial direction of the crankshaft.

4. The compressor of any one of claims 1 to 3, wherein, The crankshaft is rotatable about a first clockwise direction, and the crankshaft has a first end and a second end that are disposed opposite to each other; The first oil groove, the second oil groove, and the connecting groove all extend along the first clockwise direction from the first end to the second end of the crankshaft.

5. The compressor of any one of claims 1 to 4, wherein, The length of the connecting groove in the axial direction of the crankshaft is L, and the distance between the ends of the first oil groove and the second oil groove that are close to each other in the circumferential direction of the bearing is D, where D / 10≤L≤4D.

6. The compressor of any one of claims 1 to 5, wherein, The number of the connecting slots is N1, where 2≤N1≤4; The number of the first oil tanks is N2, where 2≤N2≤4; The number of the second oil tanks is N3, where 2 ≤ N3 ≤ 4.

7. The compressor of any one of claims 1 to 6, wherein, The ends of the first oil groove and the second oil groove that are close to each other are staggered in the circumferential direction of the bearing.

8. The compressor of any one of claims 1 to 7, wherein, The compressor is a rotary compressor.

9. A refrigeration appliance, wherein, The refrigeration equipment includes a compressor as described in any one of claims 1 to 8.

10. The refrigeration appliance of claim 9, wherein, The refrigeration equipment includes an air conditioner.

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