Rotary compressor and refrigeration equipment

Abstract

The utility model discloses a rotary compressor and refrigeration equipment, the rotary compressor comprises a pump body assembly, a motor assembly, a crankshaft and a bearing assembly, and the pump body assembly comprises an air cylinder; the motor assembly comprises a stator and a rotor, the stator is arranged around the rotor, and the rotor can rotate relative to the stator; the crankshaft is connected with the rotor and provided with an eccentric part, and the eccentric part is rotationally arranged in the air cylinder; the bearing assembly comprises a bearing body and a first flexible structure, the bearing body is provided with a shaft hole and a through hole, the shaft hole and the through hole are arranged in the axial direction and communicate with each other, the bearing body is installed at the end of the crankshaft through the shaft hole and located at the end, away from the pump body assembly, of the motor assembly, and the first flexible structure is located at the end of the shaft hole and arranged around the crankshaft. The outer wall of the first flexible structure and the inner wall of the through hole are arranged in a spaced mode and define an annular groove. According to the rotary compressor, the lubricity between the crankshaft and the bearing assembly is good, abrasion can be reduced, and the reliability is high.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a rotary compressor and refrigeration equipment. Background Technology

[0002] With the increasing speed and efficiency of rotary compressors, and the use of high-density motors in specific environments, ensuring the coaxiality of the motor stator and rotor during operation, as well as reducing crankshaft end deformation, has become particularly important for guaranteeing the reliability of rotary compressors. To achieve this, some rotary compressors use motor bearings installed at the motor ends. However, when conventional sliding bearings are used as motor bearings, the bearings themselves are prone to wear, resulting in relatively poor reliability and affecting the overall reliability of the rotary compressor. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a rotary compressor with good lubrication between its crankshaft and bearing assembly, which reduces wear and improves reliability.

[0004] This utility model also provides a refrigeration device having the above-mentioned rotary compressor.

[0005] The rotary compressor according to a first aspect of the present invention includes:

[0006] Pump body assembly, including cylinder;

[0007] An electric motor assembly includes a stator and a rotor, the stator being arranged around the rotor and the rotor being rotatable relative to the stator;

[0008] A crankshaft connected to the rotor, the crankshaft having an eccentric portion rotatably disposed within the cylinder;

[0009] A bearing assembly includes a bearing body and a first flexible structure. The bearing body has a shaft hole and a through hole. The shaft hole and the through hole are arranged axially and communicate with each other. The bearing body is mounted on the end of the crankshaft through the shaft hole, and the bearing body is located at the end of the motor assembly opposite to the pump body assembly. The first flexible structure is located at the end of the shaft hole and arranged around the crankshaft. The outer wall of the first flexible structure is spaced apart from the inner wall of the through hole and defines an annular groove.

[0010] The rotary compressor according to the first aspect of this utility model has at least the following beneficial effects: by setting the first flexible structure and the annular groove, the structural stiffness of the first flexible structure is reduced, making it easier for the first flexible structure to deform under external force. During the operation of the rotary compressor, when the crankshaft comes into contact with the inner wall of the bearing assembly, the first flexible structure deforms along with the end of the crankshaft, thereby increasing the contact area between the crankshaft and the inner wall, reducing the surface pressure, increasing the minimum oil film thickness, thereby improving the lubrication between the crankshaft and the bearing assembly, reducing wear, effectively extending the service life of the bearing assembly and improving reliability, and improving the reliability of the rotary compressor.

[0011] According to some embodiments of the present invention, the first flexible structure is located at the end of the shaft hole opposite to the motor assembly.

[0012] According to some embodiments of the present invention, the bearing assembly further includes a bushing, which is disposed in the shaft hole and sleeved on the end of the crankshaft. One end of the bushing, away from the motor assembly, extends out of the shaft hole and forms the first flexible structure.

[0013] According to some embodiments of this utility model, the inner diameter of the bushing is D, and the height of the first flexible structure along the axial direction of the bearing body is h, satisfying: h≤0.5D.

[0014] According to some embodiments of the present invention, along the axial direction of the bearing body, the height of the first flexible structure is h, and the height of the bushing is H, satisfying: h / H≤2 / 3.

[0015] According to some embodiments of the present invention, along the axial direction of the bearing body, the height of the first flexible structure is h, which satisfies: 1.5mm≤h≤20mm.

[0016] According to some embodiments of the present invention, the wall thickness of the bushing along the radial direction of the bearing body is T, satisfying: 1mm≤T≤4mm.

[0017] According to some embodiments of this utility model, the inner diameter of the bushing is D, along the axial direction of the bearing body, the height of the first flexible structure is h, along the radial direction of the bearing body, and the wall thickness of the bushing is T, satisfying: h 3 / (D*T 3 )≤82.4.

[0018] According to some embodiments of the present invention, the side of the first flexible structure facing the annular groove is provided as an inclined surface, and the wall thickness of the first flexible structure increases from the groove opening to the bottom of the annular groove.

[0019] According to some embodiments of the present invention, one end of the bushing facing the motor assembly protrudes from the bearing body and forms a second flexible structure, the second flexible structure being arranged around the crankshaft.

[0020] According to some embodiments of the present invention, the bushing includes a friction-reducing coating, which is attached to the inner peripheral wall of the bushing.

[0021] According to some embodiments of the present invention, the first flexible structure and the bearing body are integrally formed.

[0022] The refrigeration equipment according to a second aspect of the present invention includes the rotary compressor described in the first aspect of the present invention.

[0023] The refrigeration equipment according to the second aspect of this utility model has at least the following beneficial effects: Because the refrigeration equipment uses the aforementioned rotary compressor, the structural stiffness of the first flexible structure is reduced by setting a first flexible structure and an annular groove, making the first flexible structure prone to deformation under external force. During the operation of the rotary compressor, when the crankshaft contacts the inner wall of the shaft hole, the first flexible structure deforms along with the end deformation of the crankshaft, thereby increasing the contact area between the crankshaft and the inner wall of the shaft hole, reducing surface pressure, increasing the minimum oil film thickness, thereby improving the lubrication between the crankshaft and the bearing assembly, reducing wear, effectively extending the service life of the bearing assembly and improving reliability, and improving the reliability of the rotary compressor.

[0024] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0025] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0026] Figure 1 This is a cross-sectional schematic diagram of the internal structure of the rotary compressor in an embodiment of this utility model;

[0027] Figure 2 yes Figure 1 Cross-sectional view of the bearing assembly;

[0028] Figure 3 yes Figure 2 A sectional view of the bearing body;

[0029] Figure 4 This is a cross-sectional view of the bearing assembly in another embodiment of the present invention;

[0030] Figure 5 This is a cross-sectional view of the bearing assembly in another embodiment of the present invention;

[0031] Figure 6 This is a cross-sectional view of the bearing assembly in another embodiment of the present invention;

[0032] Figure 7 This is a graph showing how the deformation ratio of the crankshaft changes with the ratio h / H in this embodiment of the present invention.

[0033] Figure 8 This is a graph showing the minimum oil film thickness as a function of the height h of the first flexible structure in this embodiment of the invention.

[0034] Figure 9 This is a graph showing how the minimum oil film thickness varies with the wall thickness T of the first flexible structure in this embodiment of the invention.

[0035] Figure label:

[0036] Pump body assembly 100; first cylinder 110; first compression chamber 111; first roller 112; second cylinder 120; second compression chamber 121; second roller 122; first bearing 130; second bearing 140; partition plate 150;

[0037] Motor assembly 200; stator 210; rotor 220; counterweight 221;

[0038] Crankshaft 300; Eccentric part 310;

[0039] Bearing assembly 400; bearing body 410; main body 411; mounting part 412; through hole 413; first flexible structure 420; head 421; root 422; shaft hole 430; annular groove 440; bushing 450; second flexible structure 460. Detailed Implementation

[0040] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0041] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0042] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. If "first" or "second" is used in the description, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0043] In the description of this utility model, unless otherwise explicitly defined, terms such as setting, installing, connecting, assembling, and cooperating should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0044] With the increasing speed and efficiency of rotary compressors, and the use of high-density motors in specific environments, ensuring the coaxiality of the motor stator and rotor during operation, as well as reducing crankshaft end deformation, has become particularly important for ensuring the reliability of rotary compressors. To this end, some rotary compressors achieve these goals by installing motor bearings at the motor ends.

[0045] However, when using conventional sliding bearings as motor bearings, two problems arise. First, the motor bearings themselves are prone to wear, resulting in relatively poor reliability. Second, because the crankshaft is connected to the motor rotor, during the operation of the rotary compressor, the motor stator generates a magnetic attraction force on the rotor, causing a slight radial offset. Simultaneously, to balance the centrifugal force of the crankshaft's eccentric portion, balance weights are installed at both ends of the rotor, located at the radial ends. During operation, these balance weights also cause a slight radial offset of the rotor. This leads to bending deformation at the crankshaft end, causing it to tilt relative to the rotor's axis of rotation. At this point, the contact between the crankshaft end and the motor bearing becomes point contact, with the oil film thickness at the minimum required thickness. This small minimum oil film thickness leads to abnormal wear on both the crankshaft and motor bearings, ultimately affecting the overall reliability of the rotary compressor.

[0046] Therefore, referring to Figures 1 to 6 As shown, the first aspect of this utility model provides a rotary compressor, which can be a single-cylinder rotary compressor or a double-cylinder rotary compressor.

[0047] Reference Figure 1The diagram shown is a cross-sectional view of the internal structure of a rotary compressor, omitting the housing. It can be understood that the rotary compressor includes a pump body assembly 100, a motor assembly 200, a crankshaft 300, and a bearing assembly 400. The pump body assembly 100 is a dual-cylinder structure. Specifically, the pump body assembly 100 includes a first cylinder 110 and a second cylinder 120. The pump body assembly 100 also includes a first bearing 130, a second bearing 140, and a partition 150. The first cylinder 110 is positioned above the second cylinder 120, and the partition 150 is sandwiched between the first cylinder 110 and the second cylinder 120. The first bearing 130 is positioned above the first cylinder 110, and the second bearing 140 is positioned below the second cylinder 120. In other words, the first cylinder 110 and the second cylinder 120 are located between the first bearing 130 and the second bearing 140. The first cylinder 110 is provided with a first compression chamber 111 and a first roller 112 installed in the first compression chamber 111. Similarly, the second cylinder 120 is provided with a second compression chamber 121 and a second roller 122 installed in the second compression chamber 121. The lower part of the crankshaft 300 passes sequentially through the first bearing 130, the first cylinder 110, the partition 150, the second cylinder 120, and the second bearing 140. The lower part of the crankshaft 300 is provided with two eccentric portions 310, and the eccentric directions of the two eccentric portions 310 are opposite, that is, the direction from the central axis of the crankshaft 300 toward the center of the eccentric portion 310. The two eccentric portions 310 are respectively provided in the first compression chamber 111 and the second compression chamber 121, thereby realizing the connection between the crankshaft 300 and the first cylinder 110, and the connection between the crankshaft 300 and the second cylinder 120.

[0048] Reference Figure 1 As shown, it can be understood that by setting the first bearing 130 and the second bearing 140, the crankshaft 300 is supported and positioned to bear the reaction force of the compressed gas in the first cylinder 110 and the second cylinder 120 during the operation of the rotary compressor, thereby improving the working stability of the first cylinder 110 and the second cylinder 120.

[0049] Reference Figure 1 As shown, the motor assembly 200 is connected to the crankshaft 300 and located above the pump body assembly 100. Specifically, the motor assembly 200 includes a stator 210 and a rotor 220. Typically, the stator 210 is fixedly connected to the housing of the rotary compressor and is annular. The rotor 220 is disposed within the inner ring of the stator 210, i.e., the stator 210 is arranged around the rotor 220, and the rotor 220 is fixedly connected to the crankshaft 300. The rotor 220 can rotate relative to the stator 210. Under the action of a magnetic field, the rotor 220 can be driven to rotate relative to the stator 210. Thus, the rotor 220 drives the eccentric portion 310 to rotate via the crankshaft 300, thereby compressing the refrigerant in the first compression chamber 111 and the second compression chamber 121.

[0050] Reference Figure 1 As shown, it can be understood that, in order to balance the centrifugal force of the eccentric portion 310 of the crankshaft 300, balance blocks 221 are installed at both the upper and lower ends of the rotor 220, and the two balance blocks 221 at the upper and lower ends are located at both ends of the rotor 220 in the radial direction, that is, the two balance blocks 221 are arranged on opposite sides. Therefore, the balance of the rotor 220 during rotation can be improved, the radial offset of the rotor 220 can be reduced, the coaxiality of the stator 210 and the rotor 220 can be improved, and the dynamic and static balance effect can be improved.

[0051] Reference Figure 1 and Figure 2 As shown, it can be understood that, in order to improve the coaxiality of the stator 210 and rotor 220, prevent the stator 210 and rotor 220 from rubbing against each other, and reduce the deflection deformation at the end of the crankshaft 300, a bearing assembly 400 is also installed at the upper end of the crankshaft 300, that is, the bearing assembly 400 is located on the side of the rotor 220 away from the pump body assembly 100. Specifically, the bearing assembly 400 includes a bearing body 410 and a bushing 450, wherein the bearing body 410 includes a main body portion 411 and a mounting portion 412. The main body portion 411 is cylindrical, and the mounting portion 412 is connected to the upper end of the main body portion 411 and is annular. The mounting portion 412 is arranged around the main body portion 411, and the bearing body 410 can be fixedly installed through the mounting portion 412. The main body portion 411 and the mounting portion 412 are integrally formed structures, which are easy to manufacture.

[0052] Reference Figure 3 As shown, the main body 411 is provided with a shaft hole 430 and a through hole 413. The shaft hole 430 and the through hole 413 are arranged and connected along the axial direction of the crankshaft 300, wherein the through hole 413 is located on the upper side of the shaft hole 430. Generally speaking, the central axis of the through hole 413 coincides with that of the shaft hole 430, and the inner diameter of the through hole 413 is larger than that of the shaft hole 430, thus forming a stepped hole between the through hole 413 and the shaft hole 430.

[0053] Reference Figure 2 and Figure 3 As shown, it can be understood that the bushing 450 is installed at the shaft hole 430, and the upper end of the crankshaft 300 passes through the bushing 450, thereby positioning the upper end of the crankshaft 300 through the bearing body 410 and the bushing 450, so as to improve the coaxiality between the stator 210 and the rotor 220 and reduce the deflection deformation of the end of the crankshaft 300.

[0054] Reference Figure 2As shown, it can be understood that, generally speaking, along the axial direction of the crankshaft 300, the height of the bushing 450 is greater than the height of the shaft hole 430 and less than the height of the main body 411. The lower end of the bushing 450 is flush with the lower end of the main body 411, and the upper end of the bushing 450 extends out of the shaft hole 430 and into the through hole 413. The portion of the bushing 450 extending into the through hole 413 forms a first flexible structure 420. At this time, the first flexible structure 420 is located at the end of the shaft hole 430 away from the motor assembly 200. The first flexible structure 420 is arranged around the crankshaft 300, that is, the first flexible structure 420 is an annular wall. The outer peripheral wall of the first flexible structure 420 is spaced apart from the inner peripheral wall of the through hole 413 and defines an annular groove 440. The inner side is the side facing the central axis of the crankshaft 300, and the opposite side is the outer side. It is easy to understand that the annular groove 440 is arranged around the first flexible structure 420. Thanks to the annular groove 440, the first flexible structure 420 is suspended on both sides of the crankshaft 300 in the radial direction. The first flexible structure 420 is similar to a cantilever structure, which reduces the structural stiffness at the first flexible structure 420. Under the action of external force, the first flexible structure 420 is prone to deformation in the radial direction of the crankshaft 300.

[0055] Therefore, by setting the first flexible structure 420 and the annular groove 440, the structural stiffness of the first flexible structure 420 is reduced, making it easier for the first flexible structure 420 to deform. During the operation of the rotary compressor, when the end of the crankshaft 300 flexes, the crankshaft 300 comes into contact with the inner wall of the bushing 450. The contact area is mainly at the upper and lower ends of the bushing 450. At this time, the first flexible structure 420 deforms along with the end of the crankshaft 300, changing the contact between the crankshaft 300 and the inner wall of the bushing 450 from point contact to surface contact. This increases the contact area between the crankshaft 300 and the inner wall of the bushing 450, reduces surface pressure (the load per unit area), and increases the oil film thickness at the contact point, which increases the minimum oil film thickness. This improves the lubrication between the crankshaft 300 and the bushing 450, i.e., improves the lubrication between the crankshaft 300 and the bearing assembly 400, reduces wear, effectively extends the service life of the bearing assembly 400, and improves reliability, thereby improving the overall reliability of the rotary compressor.

[0056] In other embodiments, it is understood that when the through hole 413 is located below the shaft hole 430, the lower end of the bushing 450 extends out of the shaft hole 430 and into the through hole 413. At this time, the lower end of the bushing 450 is the first flexible structure 420, that is, the first flexible structure 420 is located at the end of the shaft hole 430 facing the motor assembly 200. Similarly, the first flexible structure 420 can increase the contact area between the crankshaft 300 and the inner wall of the bushing 450, improving lubrication, which will not be elaborated here.

[0057] Reference Figure 2As shown, it can be understood that, along the axial direction of the bearing body 410, the height of the first flexible structure 420 is defined as h, and along the radial direction of the bearing body 410, the inner diameter of the bushing 450 is defined as D, satisfying: h ≤ 0.5D. That is, the height of the first flexible structure 420 is less than or equal to half the inner diameter of the bushing 450. With a fixed inner diameter of the bushing 450, when the height of the first flexible structure 420 is greater than half the radial direction of the bushing 450, the flexibility of the first flexible structure 420 increases, the structural stiffness decreases significantly, the first flexible structure 420 itself is prone to deformation, the supporting force on the crankshaft 300 decreases, causing increased deformation of the crankshaft 300, and is also detrimental to maintaining the stability of the oil film thickness, i.e., the oil film thickness deteriorates. Therefore, by ensuring that h ≤ 0.5D, the first flexible structure 420 can effectively support itself while meeting the flexibility requirements, thereby maintaining the stability of the oil film thickness, increasing the minimum oil film thickness, improving lubrication, reducing wear, and thus improving the reliability of the bearing assembly 400 and the rotary compressor.

[0058] Reference Figure 2 As shown, it can be understood that, along the axial direction of the bearing body 410, the height of the bushing 450 is defined as H, satisfying: h / H≤2 / 3. That is, the height of the first flexible structure 420 is less than or equal to 2 / 3 times the height of the bushing 450. Generally speaking, the height of the bushing 450 is fixed. When the height of the first flexible structure 420 is too large, on the one hand, the structural stiffness of the first flexible structure 420 decreases, and the first flexible structure 420 itself is prone to deformation, which reduces the support force on the crankshaft 300, causing the crankshaft 300 to deform more, and it is not conducive to maintaining the stability of the oil film thickness, that is, the oil film thickness will deteriorate. On the other hand, if the height of the first flexible structure 420 is too large relative to the height of the bushing 450, the height of the part of the bushing 450 inside the shaft hole 430 will be too small, which will lead to insufficient support of the bearing assembly 400 on the crankshaft 300 as a whole, affecting the coaxiality between the stator 210 and the rotor 220, which will easily cause the stator 210 and the rotor 220 to rub against each other. At the same time, it will lead to increased deformation of the crankshaft 300.

[0059] Reference Figure 7 As shown, it is easy to understand that, under the same operating conditions, the deformation of crankshaft 300 increases with the increase of the ratio h / H.

[0060] Therefore, by making h / H≤2 / 3, under the condition that the first flexible structure 420 meets the flexibility requirements, it can be ensured that the first flexible structure 420 has an effective supporting role, so as to maintain the stability of the oil film thickness, increase the minimum oil film thickness, improve lubrication, reduce wear, and at the same time, ensure the overall supporting role of the bearing assembly 400 on the crankshaft 300, thereby improving the reliability of the bearing assembly 400 and the rotary compressor.

[0061] Reference Figure 2As shown, it can be understood that the height h of the first flexible structure 420 satisfies: 1.5mm ≤ h ≤ 20mm. When h is too small, the flexibility of the first flexible structure 420 is insufficient, failing to increase the contact area between the crankshaft 300 and the inner wall of the bushing 450, resulting in a too small minimum oil film thickness, deterioration of the oil film thickness, increased wear, and even abnormal wear. When h is too large, the flexibility of the first flexible structure 420 increases, but the structural stiffness will decrease significantly. The first flexible structure 420 itself is prone to deformation, reducing its support force on the crankshaft 300, causing increased deformation of the crankshaft 300, and making it difficult to maintain the stability of the oil film thickness, i.e., the oil film thickness will deteriorate.

[0062] Reference Figure 8 As shown, it is easy to understand that under the same operating conditions, the minimum oil film thickness first increases and then decreases as the height h of the first flexible structure 420 increases. When 1.5mm ≤ h ≤ 20mm is satisfied, the minimum oil film thickness is greater than or equal to 7.8μm; when h < 1.5mm or h > 20mm, the minimum oil film thickness is less than 7.8μm. Therefore, making 1.5mm ≤ h ≤ 20mm, for example, h = 2mm, h = 5mm, h = 8mm, h = 12mm, or h = 17mm, can ensure that the first flexible structure 420 has sufficient flexibility to increase the contact area between the crankshaft 300 and the inner wall of the bushing 450, thereby increasing the minimum oil film thickness, improving lubrication, and reducing wear. It also avoids the first flexible structure 420 having insufficient structural stiffness, which would lead to easy deformation and consequently deteriorate the oil film thickness, i.e., reduce the minimum oil film thickness. Therefore, making the minimum oil film thickness sufficiently large is necessary to improve lubrication.

[0063] Reference Figure 2 As shown, it can be understood that the wall thickness of the bushing 450 is defined as T along the radial direction of the bearing body 410. That is, the wall thickness of the first flexible structure 420 is T, satisfying: 1mm≤T≤4mm. It is easy to understand that when the wall thickness of the first flexible structure 420 is too small, the structural stiffness of the first flexible structure 420 decreases, the first flexible structure 420 itself is prone to deformation, the supporting force on the crankshaft 300 decreases, causing the deformation of the crankshaft 300 to increase, and it is not conducive to maintaining the stability of the oil film thickness, that is, the oil film thickness will deteriorate. When the wall thickness of the first flexible structure 420 is too large, the flexibility of the first flexible structure 420 is insufficient, and it is unable to increase the contact area between the crankshaft 300 and the inner wall of the bushing 450, resulting in a minimum oil film thickness that is too small, the oil film thickness deteriorates, wear intensifies, and even abnormal wear occurs.

[0064] Reference Figure 9As shown, it is easy to understand that under the same operating conditions, the minimum oil film thickness first increases and then decreases as the wall thickness T of the first flexible structure 420 increases. When 1mm ≤ T ≤ 4mm, the minimum oil film thickness is greater than or equal to 7.5μm; when T < 1mm or T > 4mm, the minimum oil film thickness is less than 7.5μm. Therefore, ensuring 1mm ≤ T ≤ 4mm, for example, T = 1mm, T = 2mm, T = 3mm, or T = 4mm, keeps the structural stiffness of the first flexible structure 420 within a suitable range, so that the minimum oil film thickness is sufficiently large to improve lubricity.

[0065] It is understandable that the inner diameter D of the bushing 450, the height h of the first flexible structure 420, and the thickness T of the first flexible structure 420 satisfy: h 3 / (D*T 3 )≤82.4, based on the relationship between the inner diameter D of the bushing 450, the height h of the first flexible structure 420, and the thickness T of the first flexible structure 420, the deformation of the first flexible structure 420 is limited, thereby ensuring that the deformation of the first flexible structure 420 will not be too large when bearing the load of the crankshaft 300, so as to provide sufficient support for the crankshaft 300, avoid the increase of the deformation of the crankshaft 300, and at the same time, it is beneficial to maintain the stability of the oil film thickness.

[0066] Reference Figure 4 As shown, in some other embodiments, it can be understood that the side of the first flexible structure 420 facing the annular groove 440 is an inclined surface, that is, the outer peripheral wall of the first flexible structure 420 is an inclined surface. From the opening of the annular groove 440 towards the bottom of the annular groove 440, that is, from top to bottom, the thickness of the first flexible structure 420 increases radially along the bearing body 410, that is, the wall thickness of the first flexible structure 420 increases. The end of the first flexible structure 420 away from the bottom of the annular groove 440 is defined as the head 421, and the end closer to the bottom of the annular groove 440 is defined as the root 422. Therefore, the stiffness of the first flexible structure 420 increases from the head 421 towards the root 422, that is, the stiffness of the first flexible structure 420 is variable. When the crankshaft 300 comes into contact with the first flexible structure 420, the contact begins at the head 421 of the first flexible structure 420. Therefore, during the operation of the crankshaft 300, the first flexible structure 420 deforms from the head 421, and the contact area between the crankshaft 300 and the first flexible structure 420 gradually increases. The stiffness of the first flexible structure 420 also gradually increases, which is conducive to the formation of an oil film between the crankshaft 300 and the bushing 450. At the same time, it can avoid the disadvantage of the force being concentrated at the root 422 of the first flexible structure 420 and the root 422 having a large force, which could cause the root 422 to break. This effectively improves the reliability of the bearing assembly 400.

[0067] Reference Figure 5As shown, in some embodiments, it is understood that the end of the bushing 450 facing the motor assembly 200 protrudes from the lower end of the main body 411 and forms a second flexible structure 460, that is, the lower end of the bushing 450 extends out of the shaft hole 430. It is readily understood that the second flexible structure 460 is arranged around the crankshaft 300, and the outer periphery of the second flexible structure 460 has no supporting structure, that is, the second flexible structure 460 is also similar to a cantilever structure. Referring to the first flexible structure 420, the second flexible structure 460 can also increase the contact area between the crankshaft 300 and the inner wall of the bushing 450, reduce surface pressure, and increase the oil film thickness at the contact point, that is, increase the minimum oil film thickness, thereby improving the lubrication between the crankshaft 300 and the bushing 450, that is, improving the lubrication between the crankshaft 300 and the bearing assembly 400, reducing wear, effectively extending the service life of the bearing assembly 400 and improving reliability, thereby improving the overall reliability of the rotary compressor. Further details are omitted here.

[0068] It is understood that the bushing 450 includes a friction-reducing coating, which is attached to the inner peripheral wall of the bushing 450. The friction-reducing coating can be a material such as polymer resin or graphite, thereby reducing the friction on the inner wall of the bushing 450, improving the lubrication between the crankshaft 300 and the bearing assembly 400, reducing wear, effectively extending the service life of the bearing assembly 400 and improving reliability, thereby improving the overall reliability of the rotary compressor.

[0069] Reference Figure 6 As shown, in some other embodiments, it is understood that the bearing body 410 does not have a bushing 450 in the shaft hole 430, and the first flexible structure 420 is integrally formed with the bearing body 410. In this case, the bearing body 410 is directly sleeved on the upper end of the crankshaft 300 through the shaft hole 430, and the first flexible structure 420 is located at the upper end of the shaft hole 430, that is, the first flexible structure 420 is located on the end face at the connection between the shaft hole 430 and the through hole 413, and the outer peripheral wall of the first flexible structure 420 and the inner peripheral wall of the through hole 413 are arranged at intervals, so that an annular groove 440 is formed between the outer peripheral wall of the first flexible structure 420 and the inner peripheral wall of the through hole 413. Similarly, the first flexible structure 420 of this structure can increase the contact area between the crankshaft 300 and the inner wall of the shaft hole 430, reduce the surface pressure, and increase the oil film thickness at the contact point, which means increasing the minimum oil film thickness. This improves the lubrication between the crankshaft 300 and the bearing body 410, reduces wear, effectively extends the service life of the bearing assembly 400, and improves its reliability, thereby improving the overall reliability of the rotary compressor. Further details are omitted here.

[0070] A second aspect of this utility model provides a refrigeration device, which can be an electrical appliance such as an air conditioner or refrigerator. The refrigeration device includes a rotary compressor as described in any of the above embodiments.

[0071] Since the refrigeration equipment adopts all the technical solutions of the rotary compressor in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments.

[0072] The embodiments of the present utility model have been described in detail above with reference to the accompanying drawings. However, the present utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present utility model.

Claims

1. A rotary compressor, characterized by, The application relates to a rotary compressor. The application relates to a rotary compressor. The application relates to a rotary compressor. The application relates to a rotary compressor. The application relates to a rotary compressor.

2. The rotary compressor of claim 1, wherein: The application relates to a rotary compressor.

3. The rotary compressor of claim 2, wherein: The application relates to a rotary compressor.

4. The rotary compressor of claim 3, wherein: The application relates to a rotary compressor.

5. The rotary compressor of claim 3, wherein: The application relates to a rotary compressor.

6. The rotary compressor according to any one of claims 3 to 5, characterized in that: The application relates to a rotary compressor.

7. The rotary compressor of claim 3, wherein: The application relates to a rotary compressor.

8. The rotary compressor of claim 3, wherein: The inner diameter of the shaft sleeve is D, the height of the first flexible structure is h along the axial direction of the bearing body, and the wall thickness of the shaft sleeve is T, which satisfies: h 3 / (D*T 3 )≤82.

4.

9. The rotary compressor of claim 3, wherein: The application relates to a rotary compressor.

10. The rotary compressor of claim 3, wherein: The application relates to a rotary compressor.

11. The rotary compressor of claim 3, wherein: The application relates to a rotary compressor.

12. The rotary compressor of claim 2, wherein: The application relates to a rotary compressor.

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