Air cylinder, rotary compressor and refrigeration equipment

Abstract

The utility model discloses an air cylinder, a rotary compressor and refrigeration equipment, the outer periphery of the air cylinder is provided with a notch groove and a welding groove, the notch groove comprises a first groove wall surface, and the welding groove comprises a first welding groove adjacent to the notch groove; the connecting line of the center of the first welding groove and the center of the air cylinder is L, the connecting line of one side of the first groove wall face and the center of the air cylinder is H1, the connecting line of the other side of the first groove wall face and the center of the air cylinder is H2, the minimum included angle between L and H1 is alpha, the maximum included angle between H1 and H2 is beta, and alpha is larger than or equal to beta / 2. Alpha is larger than or equal to beta / 2, the first welding groove has enough distance relative to the notch groove, influence on the notch groove during welding can be relieved, deformation of the notch groove is relieved, overall deformation of the air cylinder is reduced, abnormal abrasion of an inner structure of the compressor caused by deformation of the air cylinder is reduced, and therefore vibration and noise are effectively reduced, and the service life of the compressor is prolonged. The operation reliability of the compressor is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a cylinder, a rotary compressor and a refrigeration device. Background Art

[0002] In rotary compressors, there are two main ways to fix the pump body to the housing: cylinder fixing and bearing fixing. In related technologies, when the bearing fixing method is adopted, the bearing structure is complex and the material and processing costs are high; while when the cylinder welding fixing method is adopted, the heat and stress generated by the welding can easily cause the cylinder to deform, resulting in greater vibration and noise during the operation of the compressor, reducing the reliability of the compressor. In actual engineering applications, especially in the field of high-speed and wide-band compressors, higher requirements are put forward for both the high-frequency noise of the pump body and the reliability of the compressor. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model provides a compressor that can reduce vibration and noise and improve the reliability of the compressor.

[0004] The utility model also provides a rotary compressor with the cylinder.

[0005] The utility model also provides a refrigeration device having the rotary compressor.

[0006] The cylinder according to the first embodiment of the utility model is applied to a rotary compressor, wherein the outer periphery of the cylinder is provided with a notch groove and a welding groove, wherein the notch groove includes a first groove wall surface, and the welding groove includes a first welding groove adjacent to the notch groove;

[0007] On the projection surface along the axial direction of the cylinder, the line connecting the center of the first welding groove and the center of the cylinder is L, along the circumference of the cylinder, the line connecting one side of the first groove wall and the center of the cylinder is H1, and the line connecting the other side of the first groove wall and the center of the cylinder is H2, the minimum angle between L and H1 is α, and the maximum angle between H1 and H2 is β, satisfying: α≥β / 2.

[0008] The cylinder according to the embodiment of the utility model has at least the following beneficial effects: by making α≥β / 2, the pump body assembly has a better modal frequency, and the modal frequency is far away from the vibration excitation frequency, which can reduce resonance; at the same time, the first welding groove is sufficiently far away from the notch groove, which can reduce the influence of the first welding groove on the notch groove when it is welded to the shell, reduce the deformation of the notch groove part, thereby reducing the overall deformation of the cylinder, and can reduce the abnormal wear of the roller and crankshaft caused by the deformation of the cylinder, thereby effectively reducing vibration and noise, and improving the reliability of the operation of the rotary compressor.

[0009] According to some embodiments of the present invention, the welding groove includes a second welding groove, and the notched groove is located between the first welding groove and the second welding groove;

[0010] On the projection surface along the axial direction of the cylinder, the line connecting the center of the notch groove and the center of the cylinder is H3, and the distance from the center of the first welding groove to H3 is equal to the distance from the center of the second welding groove to H3.

[0011] According to some embodiments of the utility model, the cylinder is further provided with an air suction hole, the second welding groove is adjacent to the air suction hole, and the air suction hole includes a hole wall surface;

[0012] On the projection surface along the axial direction of the cylinder, the line connecting the center of the second welding groove and the center of the cylinder is Y, along the circumference of the cylinder, the line connecting one side of the hole wall and the center of the cylinder is T1, and the line connecting the other side of the hole wall and the center of the cylinder is T2, the minimum angle between Y and T1 is λ, and the maximum angle between T1 and T2 is ω, satisfying: λ≥ω.

[0013] According to some embodiments of the utility model, the cylinder is further provided with an air suction hole, the welding groove comprises a third welding groove adjacent to the air suction hole, the third welding groove is located between the second welding groove and the air suction hole, and the air suction hole comprises a hole wall surface;

[0014] On the projection surface along the axial direction of the cylinder, the line connecting the center of the third welding groove and the center of the cylinder is P, along the circumference of the cylinder, the line connecting one side of the hole wall and the center of the cylinder is T1, and the line connecting the other side of the hole wall and the center of the cylinder is T2, the minimum angle between P and T1 is γ, and the maximum angle between T1 and T2 is ω, satisfying: γ≥ω.

[0015] According to some embodiments of the utility model, the cylinder is provided with an air suction hole, the welding groove includes a fourth welding groove adjacent to the air suction hole, the fourth welding groove and the first welding groove are respectively located on both sides of the notch groove, and the air suction hole includes a hole wall surface;

[0016] On the projection surface along the axial direction of the cylinder, the line connecting the center of the fourth welding groove and the center of the cylinder is F, along the circumference of the cylinder, the line connecting one side of the hole wall and the center of the cylinder is T1, and the line connecting the other side of the hole wall and the center of the cylinder is T2, the minimum angle between F and T1 is η, and the maximum angle between T1 and T2 is ω, satisfying: η≥ω.

[0017] According to some embodiments of the utility model, the cylinder is further provided with a sliding vane groove, the sliding vane groove includes a second groove wall surface, the welding groove includes a fifth welding groove adjacent to the sliding vane groove, and the fifth welding groove is located between the first welding groove and the sliding vane groove;

[0018] On the projection surface along the axial direction of the cylinder, the line connecting the center of the fifth welding groove and the center of the cylinder is K, along the circumference of the cylinder, the line connecting one side of the second groove wall and the center of the cylinder is J1, and the line connecting the other side of the second groove wall and the center of the cylinder is J2, the minimum angle between K and J1 is θ, and the maximum angle between J1 and J2 is δ, satisfying: θ≥δ.

[0019] According to some embodiments of the present invention, a line connecting the groove wall of the welding groove and the center of the cylinder is R, and a length of a portion of R passing through a solid part of the cylinder is greater than or equal to 23 mm.

[0020] According to some embodiments of the present invention, the number of the welding grooves is greater than or equal to 5.

[0021] According to some embodiments of the utility model, there are multiple welding grooves, and the multiple welding grooves are evenly distributed along the outer circumference of the cylinder.

[0022] The rotary compressor according to the second embodiment of the utility model comprises the cylinder described in the above embodiment.

[0023] The rotary compressor according to the embodiment of the utility model has at least the following beneficial effects: by adopting the cylinder of the embodiment of the first aspect, the cylinder sets α≥β / 2, so that the pump body assembly has a better modal frequency, and the modal frequency is far away from the vibration excitation frequency, which can reduce resonance; at the same time, the first welding groove is sufficiently far away from the notch groove, which can reduce the influence of the first welding groove on the notch groove when welding with the shell, reduce the deformation of the notch groove, thereby reducing the overall deformation of the cylinder, and can reduce the abnormal wear of the roller and crankshaft caused by the deformation of the cylinder, thereby effectively reducing vibration and noise, and improving the reliability of the operation of the rotary compressor.

[0024] According to some embodiments of the utility model, the rotary compressor includes a shell and a first cylinder and a second cylinder arranged in the shell, the shell includes a bottom wall, the first cylinder and the second cylinder are spaced apart along the height direction of the shell, the first cylinder is located on the side of the second cylinder away from the bottom wall, and the first cylinder is welded to the side wall of the shell through the welding groove.

[0025] The refrigeration device according to the embodiment of the third aspect of the utility model comprises the rotary compressor described in the above embodiment.

[0026] The refrigeration equipment according to the embodiment of the utility model has at least the following beneficial effects: by adopting the rotary compressor of the embodiment of the second aspect, by setting α≥β / 2, the pump body assembly has a better modal frequency, and the modal frequency is far away from the vibration excitation frequency, which can reduce resonance; at the same time, the first welding groove is sufficiently far away from the notch groove, which can reduce the influence of the first welding groove on the notch groove when it is welded to the shell, reduce the deformation of the notch groove part, thereby reducing the overall deformation of the cylinder, and can reduce the abnormal wear of the roller and crankshaft caused by the deformation of the cylinder, thereby effectively reducing vibration and noise, and improving the reliability of the operation of the rotary compressor.

[0027] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0029] Figure 1 A cross-sectional view of a partial structure of a rotary compressor according to an embodiment of the utility model;

[0030] Figure 2 It is a structural schematic diagram of a cylinder according to an embodiment of the utility model;

[0031] Figure 3 A schematic diagram of welding the cylinder and the housing according to an embodiment of the utility model;

[0032] FIG4( a ) is a schematic diagram of the structure of the cylinder A for simulation testing of the present invention;

[0033] FIG4( b ) is a schematic diagram of the structure of the cylinder B used in the simulation test of the present invention;

[0034] FIG5( a ) is a schematic diagram of the structure of the cylinder C used for simulation testing of the present invention;

[0035] FIG5( b ) is a schematic diagram of the structure of the cylinder D used in the simulation test of the present invention;

[0036] Figure 6 A cross-sectional view of the welding of the cylinder and the housing of the first embodiment of the utility model;

[0037] Figure 7 It is a front view of the cylinder of the first embodiment of the utility model;

[0038] Figure 8 A cross-sectional view of the welding of the cylinder and the housing of the second embodiment of the utility model;

[0039] Fig. 9A cross-sectional view of the welding of the cylinder and the housing of the third embodiment of the utility model;

[0040] Fig.10 A cross-sectional view of a portion of the structure of a cylinder according to an embodiment of the utility model;

[0041] Fig.11 A cross-sectional view of the welding of the cylinder and the housing of the fourth embodiment of the utility model;

[0042] Fig.12 A cross-sectional view of the welding of the cylinder and the housing in the fifth embodiment of the utility model;

[0043] Fig.13 A cross-sectional view of the welding of the cylinder and the housing of the sixth embodiment of the utility model;

[0044] Fig.14 This is a schematic structural diagram of a cylinder according to an embodiment of the utility model;

[0045] Fig.15 for Fig.14 A partial enlarged view of point A in the middle.

[0046] Figure Number:

[0047] Rotary compressor 10; housing 100;

[0048] Crankshaft 200; eccentric portion 210; motor assembly 300; rotor 310; stator 320;

[0049] Pump body assembly 400; cylinder 410; first cylinder 410a; second cylinder 410b;

[0050] Active chamber 411; air intake chamber 411a; air exhaust chamber 411b;

[0051] Sliding vane groove 412; second groove wall surface 4121; air suction hole 413; hole wall surface 4131;

[0052] Notched groove 414; first groove wall 4141; first edge 4142; second edge 4143;

[0053] Welding groove 415; first welding groove 415a; second welding groove 415b; third welding groove 415c; fourth welding groove 415d;

[0054] Fifth welding groove 415e; roller 420; slide 430;

[0055] Partition plate 500 ; first bearing 600 ; second bearing 700 ; first muffler 800 ; second muffler 900 . DETAILED DESCRIPTION

[0056] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0057] In the description of the present invention, it should be understood that the descriptions involving orientation, such as the orientation or positional relationship indicated as up, down, etc., are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0058] In the description of the present utility model, "a plurality" means more than two. If there is a description of "first" or "second", it is only for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0059] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0060] The present application provides a cylinder and a rotary compressor using the cylinder.

[0061] Please refer to Figure 1 , Figure 1 The rotary compressor 10 includes a housing 100 , a crankshaft 200 , a motor assembly 300 and a pump assembly 400 .

[0062] The motor assembly 300 is connected to the crankshaft 200. Specifically, the motor assembly 300 includes a rotor 310 and a stator 320. Generally speaking, the stator 320 is fixedly connected to the housing 100, the stator 320 is annular, and the rotor 310 is arranged in the inner ring of the stator 320, that is, the stator 320 is arranged around the rotor 310, and the crankshaft 200 is penetrated by the rotor 310 and fixedly connected to the rotor 310. The rotor 310 can rotate relative to the stator 320. Under the action of the magnetic field, the rotor 310 can be driven to rotate relative to the stator 320, so that the rotor 310 drives the crankshaft 200 to rotate.

[0063] The pump assembly 400 is used to move under the drive of the motor assembly 300 and the crankshaft 200 to compress the refrigerant. Figure 1 And refer to Figure 2 and Figure 3 , Figure 2 This is a schematic diagram of the structure of the cylinder of an embodiment of the utility model. Figure 3 The figure is a schematic diagram of the welding of the cylinder and the shell of the embodiment of the utility model. The pump body assembly 400 includes a cylinder 410, and the cylinder 410 is provided with an active cavity 411 and a roller 420 installed in the active cavity 411. The end of the crankshaft 200 away from the motor assembly 300 is arranged in the active cavity 411 of the cylinder 410, and the roller 420 is sleeved on the crankshaft 200 and is rotatably connected with the crankshaft 200. The crankshaft 200 can drive the roller 420 to move along the cavity wall of the active cavity 411. Among them, the crankshaft 200 is provided with an eccentric portion 210, the eccentric portion 210 is located in the active cavity 411, and the roller 420 is sleeved on the periphery of the eccentric portion 210. Specifically, during the operation of the compressor, the motor assembly 300 drives the crankshaft 200 to rotate, and the crankshaft 200 drives the eccentric portion 210 to rotate eccentrically, thereby driving the roller 420 to rotate eccentrically in the active cavity 411.

[0064] The cylinder 410 is provided with a vane groove 412, which is arranged along the radial direction of the cylinder 410, and one end of the vane groove 412 is connected with the active chamber 411. The pump body assembly 400 is also provided with a vane 430, which is arranged in the vane groove 412 so as to slide back and forth. One end of the vane 430 extends out of the vane groove 412 and abuts against the roller 420, and one end is always located in the vane groove 412. Then, the vane 430 can separate the active chamber 411 into an air suction chamber 411a and an air discharge chamber 411b, and as the roller 420 rotates continuously, the volumes of the air suction chamber 411a and the air discharge chamber 411b change continuously, so that normal pressure or low pressure gas enters the air suction chamber 411a and is compressed to form high pressure gas and is discharged from the air discharge chamber 411b, thereby realizing the compression function of the refrigerant.

[0065] The cylinder 410 is also provided with an air intake hole 413 and an air exhaust hole (not shown in the figure) connected to the active chamber 411. The air intake hole 413 is connected to the air intake chamber 411a, and the air exhaust hole is connected to the air exhaust chamber 411b. The air intake hole 413 and the air exhaust hole can be respectively arranged on opposite sides of the slide 430. In one embodiment, as Figure 2 As shown, the air suction hole 413 is disposed at one side of the sliding vane slot 412 and adjacent to the sliding vane slot 412 .

[0066] It is understandable that due to the eccentric rotation of one end of the crankshaft 200 connected to the pump body assembly 400, vibration is easily generated during the eccentric rotation of the crankshaft 200. At the same time, the refrigerant in the cylinder 410 generates vibration excitation due to the change in pressure during the compression process. The excitation effect on the cylinder 410 easily causes the entire pump body assembly 400 to vibrate and generate relatively large noise, affecting the reliability of the compressor operation. Therefore, it is particularly important to support and fix the pump body assembly 400.

[0067] In order to ensure the stability of the support and fixation of the pump body assembly 400, in the embodiment of the present application, the cylinder 410 is welded to the side wall of the housing 100. Figure 2 The cylinder 410 is provided with a plurality of welding grooves 415, and the plurality of welding grooves 415 are provided on the outer periphery of the cylinder 410. Among them, the welding grooves 415 can be designed as tapered grooves.

[0068] Accordingly, the housing 100 is provided with a plurality of welding ports (not shown), which penetrate the side wall of the housing 100 along the thickness direction of the housing 100. When welding the cylinder 410, the solder, the portion of the cylinder 410 forming the welding groove 415, and the portion of the side wall of the housing 100 forming the welding port are melted together under the welding heat, and after the three are solidified, the cylinder 410 is firmly connected to the side wall of the housing 100. By welding the cylinder 410 to the housing 100, the cylinder 410 and the housing 100 are connected as a whole, which enhances the stability of the support of the pump body assembly 400, and at the same time enhances the overall rigidity of the compressor, which has a certain effect on reducing vibration and noise.

[0069] Please refer to Table 1, which shows the simulation test data of the cylinder of the embodiment of the utility model with different numbers of welding grooves.

[0070] Pump assembly mode / Hz 3 welding slots 4 welding slots 5 welding slots 6 welding slots Rotor swing frequency 362 370 375 379 Pump assembly C-type mode 1621 1901 2019 2090 Pump assembly S-type mode 3211 3280 3477 3730

[0071] Among them, mode is a fixed attribute of an object. The mode of an object under different structures is different. The vibration excitation of an object close to the modal frequency is prone to resonance, resulting in increased vibration and noise. According to the above table, when the number of welding grooves 415 is 3, the C-type modal frequency of the pump body assembly 400 is 1621, and the S-type modal frequency is 3211; when the number of welding grooves 415 is 4, the C-type modal frequency of the pump body assembly 400 is 1901, and the S-type modal frequency is 3280; when the number of welding grooves 415 is 5, the C-type modal frequency of the pump body assembly 400 is 2019, and the S-type modal frequency is 3477. It can be seen that as the number of welding grooves 415 on the cylinder 410 increases, the modal frequency of the pump body assembly 400 of the rotary compressor 10 gradually increases, so that the modal frequency is far away from the vibration excitation frequency of the pump body assembly 400, which can reduce or avoid resonance, thereby reducing vibration and noise, which is beneficial to the reliability of the operation of the rotary compressor 10.

[0072] In order to effectively reduce the vibration and noise of the rotary compressor 10 , in one embodiment, the number of the welding grooves 415 is greater than or equal to five.

[0073] However, as the number of welding grooves 415 increases, on the one hand, more solid parts are removed from the cylinder 140, and the overall rigidity of the cylinder 410 is reduced. On the other hand, more welding heat and welding stress will be generated during the welding process of the cylinder 410, making the cylinder 410 easy to deform, especially the parts of the cylinder 410 with weaker rigidity are more prone to larger deformation. The deformation of the cylinder 410 will affect the rotation of the roller 420 and the crankshaft 200, and reduce reliability.

[0074] Please continue to refer to Figure 2 The cylinder 410 is provided with a notch groove 414, which is provided at the outer periphery of the cylinder 410. The notch groove 414 penetrates the upper and lower surfaces of the cylinder 410 in the thickness direction. The notch groove 414 is used to position the cylinder 410 so as to facilitate the assembly of the cylinder 410. Since the notch groove 414 is formed by removing part of the solid structure from the cylinder 410, the rigidity of the part of the cylinder 410 corresponding to the notch groove 414 is relatively low. During the welding process of the cylinder 410, the part at the notch groove 414 is prone to deformation, resulting in overall deformation of the cylinder 410, which affects the rotation of the roller 420 and the crankshaft 200, making the roller 420 and the crankshaft 200 prone to abnormal wear due to the deformation of the cylinder 410, increasing vibration and noise, and affecting the reliability of the operation of the rotary compressor 10.

[0075] Please refer to Figure 4(a) and Figure 4(b), Figure 4(a) is a schematic diagram of the structure of cylinder A for simulation test of the present invention, and Figure 4(b) is a schematic diagram of the structure of cylinder B for simulation test of the present invention. The number of welding grooves 415 of the two cylinders shown in the two figures is 5, and the positions of the welding grooves 415 of the two cylinders are the same, wherein cylinder A is not provided with notch grooves 414, and cylinder B is provided with notch grooves 414. Simulation tests are performed on the two cylinders respectively to obtain the simulation data in Table 2.

[0076]

[0077] According to Table 2, when the number of welding grooves 415 of the two cylinders is the same as 5, for cylinder A without notch groove 414, the C-type modal frequency of its pump body assembly 400 is 2019, and the S-type modal frequency is 3477, while for cylinder B with notch groove 414, the C-type modal frequency of its pump body assembly 400 is 1858, and the S-type modal frequency is 3443. Obviously, the modal frequency of cylinder B with notch groove 414 is lower than the modal frequency of cylinder A without notch groove 414, which also proves that notch groove 414 will affect the mode of cylinder 410.

[0078] To further determine the influence of the notch groove 414 on the mode of the pump body assembly 400, please refer to Figure 5(a) and Figure 5(b). Figure 5(a) is a schematic diagram of the structure of the cylinder C for the simulation test of the utility model, and Figure 5(b) is a schematic diagram of the structure of the cylinder D for the simulation test of the utility model. The number of welding grooves 415 of the two cylinders shown in the two figures is the same as 4, and both cylinders 410 are provided with notch grooves 414, and the notch grooves 414 are set at the same position. The difference is that one of the welding grooves 415 located on one side of the notch groove 414 in cylinder C is farther from the notch groove 414, and one of the welding grooves 415 located on one side of the notch groove 414 in cylinder D is closer to the notch groove 414. The positions of the remaining welding grooves 415 are the same. The simulation test of the two cylinders obtains the simulation data in Table 2. According to Table 2, for cylinder C, the C-type modal frequency of its pump body assembly 400 is 1901, and the S-type modal frequency is 3280. For cylinder D, the C-type modal frequency of its pump body assembly 400 is 1863, and the S-type modal frequency is 3272. That is to say, the closer the welding groove 415 is to the notch groove 414, the lower the modal frequency of the pump body assembly 400. It can be determined that the notch groove 414 affects the mode of the pump body assembly 400, and the closer the notch groove 414 is to the welding groove 415, the lower the modal frequency of the pump body assembly 400.

[0079] Therefore, the closer the welding groove 415 is to the notch groove 414, the lower the modal frequency of the pump body assembly 400 will be, making the modal frequency of the pump body assembly 400 closer to the vibration excitation frequency, making the pump body assembly 400 more likely to vibrate; moreover, the closer the welding groove 415 is to the notch groove 414, the more likely the heat and deformation generated during the welding process of the welding groove 415 will affect the notch groove 414, causing deformation at the notch groove 414, affecting the rotation of the roller 420 and the crankshaft 200, intensifying vibration and noise, and affecting the reliability of the operation of the rotary compressor 10.

[0080] Therefore, in order to reduce vibration and noise and improve the reliability of the operation of the rotary compressor 10, the position of the welding groove 415 is designed in the embodiment of the present application. Figure 6 and Figure 7 , Figure 6 This is a cross-sectional view of the welding of the cylinder and the housing of the first embodiment of the utility model. Figure 7 The front view of the cylinder of the first embodiment of the utility model is shown in FIG. The welding groove 415 includes a first welding groove 415 a adjacent to the notch groove 414 . It should be understood that the first welding groove 415 a refers to the welding groove 415 that is closest to the notch groove 414 among the plurality of welding grooves 415 .

[0081] like Figure 6As shown, on the projection surface along the axial projection of the cylinder 410, the line connecting the center of the first welding groove 415a and the center of the cylinder 410 is L, the notch groove 414 includes a first groove wall 4141, along the circumference of the cylinder 410, the line connecting one side of the first groove wall 4141 and the center of the cylinder 410 is H1, and the line connecting the other side of the first groove wall 4141 and the center of the cylinder 410 is H2, the minimum angle between L and H1 is α, and the maximum angle between H1 and H2 is β, satisfying the following relationship: α≥β / 2.

[0082] It can be understood that in order to minimize the angle between L and H1, H1 is the line closest to L, that is, H1 is the line connecting the point closest to L on the first groove wall 4141 and the center of the cylinder 410. Figure 6 For example, when the shape of the notch groove 414 is designed to be a regular semicircular groove, the point on the first groove wall 4141 closest to L is located at the connection between the first groove wall 4141 and the outer peripheral wall of the cylinder 410, such as Figure 7 As shown, a first edge 4142 and a second edge 4143 are formed at the connection between the first groove wall 4141 and the outer peripheral wall of the cylinder 410, and the first edge 4142 is located between the first welding groove 415a and the second edge 4143. For the first welding groove 415a, the minimum angle α between L1 and H1 is the central angle formed by a line connecting a point on the first edge 4142 and the center of the cylinder 410 and L1.

[0083] To maximize the angle between H1 and H2, H2 is the line farthest from H1, and the maximum angle β is the central angle formed by a line between a point on the first edge 4142 and the center of the cylinder 410 and a line between a point on the second edge 4143 and the center of the cylinder 410. The range of the central angle can cover the entire notch groove 414 area.

[0084] The smaller the angle between L and H1, the closer the distance between the first welding groove 415a and the boundary of the notch groove 414 is, and the closer the first welding groove 415a is to the notch groove 414, the greater the impact on the notch groove 414 when the cylinder 410 is welded to the shell 100 through the first welding groove 415a, and the easier it is to cause the notch groove 414 to deform and cause the cylinder 410 to deform as a whole, which is easy to cause abnormal wear of the roller 420 and the cylinder 410, affecting the reliability of the compressor. Moreover, the closer the first welding groove 415a is to the notch groove 414, the larger the non-solid part of the cylinder 410 corresponding to this area, and the overall structural rigidity of the cylinder 410 is reduced, causing the cylinder 410 to be more easily deformed. In addition, according to the above Table 2, the closer the first welding groove 415a is to the notch groove 414, the lower the modal frequency of the pump body assembly 400 will be, making the pump body assembly 400 more likely to vibrate. The applicant of the utility model conducted simulation tests on the cylinder 410 and found that when α≥β / 2, the cylinder 410 has a higher modal frequency and smaller deformation and vibration.

[0085] Then, the cylinder 410 of the embodiment of the utility model can reduce resonance by making α≥β / 2 so that the pump body assembly 400 has a higher modal frequency and the modal frequency is far away from the vibration excitation frequency; at the same time, the first welding groove 415a is sufficiently far away from the notch groove 414, which can reduce the impact of the first welding groove 415a on the notch groove 414 when it is welded to the shell 100, reduce the deformation of the notch groove 414, and thus reduce the overall deformation of the cylinder 410, which can reduce the abnormal wear of the roller 420 and the crankshaft 200 caused by the deformation of the cylinder 410, thereby effectively reducing vibration and noise, and improving the reliability of the operation of the rotary compressor 10.

[0086] To further reduce the deformation of the cylinder 410, in one embodiment, please refer to Figure 8 , Figure 8 This is a cross-sectional view of the cylinder and the housing welded in the second embodiment of the utility model. The welding groove 415 includes a second welding groove 415b, the notch groove 414 is located between the first welding groove 415a and the second welding groove 415b, and the line connecting the center of the notch groove 414 and the center of the cylinder 410 is H3, wherein the distance from the center of the first welding groove 415a to H3 is equal to the distance from the center of the second welding groove 415b to H3.

[0087] That is, the first welding groove 415a and the second welding groove 415b are symmetrically arranged about the line connecting the center of the notch groove 414 and the center of the cylinder 410, or in other words, Figure 8 As shown, the line connecting the center of the first welding groove 415a and the center of the cylinder 410 is L, and the angle between L and H3 is μ; the line connecting the center of the second welding groove 415b and the center of the cylinder 410 is Y, and the angle between Y and H3 is That is to say Then, through the above arrangement, during the welding process of the first welding groove 415a and the second welding groove 415b to the side wall of the shell 100 respectively, the heat transferred to the notch groove 414 by both is almost the same, so that the notch groove 414 can be heated evenly and the deformation caused by uneven heating on both sides of the notch groove 414 can be reduced.

[0088] Since the air intake hole 413 is formed by removing part of the solid structure of the cylinder 410, the strength and rigidity of the position where the air intake hole 413 is located are relatively weak. If the welding groove 415 is close to the air intake hole 413, the position at the air intake hole 413 is also prone to deformation, affecting the rotation of the roller 420, resulting in increased vibration and noise.

[0089] It is understandable that only one welding groove 415 may be provided between the notch groove 414 and the air intake hole 413, or a plurality of welding grooves 415 may be provided. Fig. 9 and Fig.10 , Fig. 9 This is a cross-sectional view of the welding of the cylinder and the housing in the third embodiment of the utility model. Fig.10 It is a cross-sectional view of a part of the structure of the cylinder according to the embodiment of the utility model. Only one second welding groove 415 b is provided between the notch groove 414 and the air intake hole 413 .

[0090] like Fig. 9 As shown, on the projection surface along the axial projection of the cylinder 410, the line connecting the center of the second welding groove 415b and the center of the cylinder 410 is Y, the air intake hole 413 includes a hole wall 4131, along the circumference of the cylinder 410, the line connecting one side of the hole wall 4131 and the center of the cylinder 410 is T1, and the line connecting the other side of the hole wall 4131 and the center of the cylinder 410 is T2, the minimum angle between Y and T1 is λ, and the maximum angle between T1 and T2 is ω, satisfying: λ≥ω.

[0091] It can be understood that in order to minimize the angle between Y and T1, T1 is the line closest to Y, that is, T1 is the line connecting the point on the hole wall 4131 closest to Y and the center of the cylinder 410. Fig.10 For example, the point on the hole wall 4131 closest to Y is the end point A connecting the hole wall 4131 and the active chamber 411 of the cylinder 410. The minimum angle θ between Y and T1 is the central angle formed by the line connecting the end point A and the center of the cylinder 410 and Y. To maximize the angle between T1 and T2, T2 is the line farthest from T1, such as Fig.10As shown, the line farthest from T1 is: the line connecting the endpoint B connecting the hole wall 4131 and the active cavity 411 of the cylinder 410 and the center of the cylinder 410, that is, the maximum angle ω between T1 and T2 is the central angle formed by the line connecting the endpoint B and the center line of the cylinder 410 and the line connecting the endpoint A and the center of the cylinder 410, and the range of the central angle can cover the entire suction hole 413 area.

[0092] The smaller the angle between Y and T1, the closer the distance between the second welding groove 415b and the boundary of the air intake hole 413 is, that is, the closer the second welding groove 415b is to the air intake hole 413, the greater the impact of the cylinder 410 on the air intake hole 413 when it is welded to the shell 100 through the second welding groove 415b, and the easier it is to cause the air intake hole 413 to deform, resulting in the overall deformation of the cylinder 410, causing abnormal wear of the roller 420 and the cylinder 410, affecting the reliability of the compressor. Moreover, the closer the second welding groove 415b is to the air intake hole 413, the larger the non-solid part of the cylinder 410 corresponding to this area, and the overall structural rigidity of the cylinder 410 is reduced, causing the cylinder 410 to be more easily deformed. By making λ≥ω, the second welding groove 415b has a larger distance relative to the intake hole 413, which can reduce the impact of the second welding groove 415b on the intake hole 413 when being welded to the shell 100, reduce the deformation of the intake hole 413, and thus reduce the overall deformation of the cylinder 410. It can reduce the abnormal wear of the vane 430, roller 420 and crankshaft 200 caused by the deformation of the cylinder 410, further reduce vibration and noise, and improve the reliability of the compressor operation.

[0093] In another embodiment, at least two welding grooves 415 are provided between the notch groove 414 and the air intake hole 413. Fig.10 And refer to Fig.11 , Fig.11 4 is a cross-sectional view of the cylinder and the housing welded in the fourth embodiment of the utility model. The welding groove 415 includes a third welding groove 415c adjacent to the air intake hole 413, and the third welding groove 415c is located between the second welding groove 415b and the air intake hole 413. It can be understood that the third welding groove 415c is located between the notch groove 414 and the air intake hole 413, and is the welding groove 415 closest to the air intake hole 413.

[0094] like Fig.11 As shown, on the projection surface along the axial projection of the cylinder 410, the line connecting the center of the third welding groove 415c and the center of the cylinder 410 is P, along the circumference of the cylinder 410, the line connecting one side of the hole wall 4131 and the center of the cylinder 410 is T1, and the line connecting the other side of the hole wall 4131 and the center of the cylinder 410 is T2, the minimum angle between P and T1 is γ, and the maximum angle between T1 and T2 is ω, satisfying: γ≥ω.

[0095] Similarly, the smaller the angle between P and T1, that is, the closer the third welding groove 415c is to the air intake hole 413, the greater the impact of the third welding groove 415c on the air intake hole 413 during welding, which can easily cause the air intake hole 413 to deform and cause the cylinder 410 to deform as a whole, resulting in abnormal wear of the roller 420 and the cylinder 410, affecting the reliability of the compressor; at the same time, the overall rigidity of the cylinder 410 is low, and the cylinder 410 is more likely to deform. By making γ≥ω, the third welding groove 415c has a larger distance relative to the air intake hole 413, which can reduce the impact of the third welding groove 415c on the air intake hole 413 when welding with the housing 100, reduce the deformation of the air intake hole 413, and thus reduce the overall deformation of the cylinder 410, which can reduce the abnormal wear of the vane 430, the roller 420 and the crankshaft 200 caused by the deformation of the cylinder 410, further reduce vibration and noise, and improve the reliability of the compressor operation.

[0096] In another embodiment, please combine Fig.10 And refer to Fig.12 , Fig.12 The cross-sectional view of the cylinder and the shell welding of the fifth embodiment of the utility model. The cylinder 410 is provided with an air intake hole 413, the welding groove 415 includes a fourth welding groove 415d adjacent to the air intake hole 413, the fourth welding groove 415d and the first welding groove 415a are respectively located on both sides of the notch groove 414, and the air intake hole 413 includes a hole wall surface 4131.

[0097] like Fig.12 As shown, on the projection surface along the axial projection of the cylinder 410, the line connecting the center of the fourth welding groove 415d and the center of the cylinder 410 is F, along the circumference of the cylinder 410, the line connecting one side of the hole wall 4131 and the center of the cylinder 410 is T1, and the line connecting the other side of the hole wall 4131 and the center of the cylinder 410 is T2, the minimum angle between F and T1 is η, and the maximum angle between T1 and T2 is ω, satisfying: η≥ω.

[0098] The principle of setting the fourth welding groove 415d to satisfy the relationship η≥ω is the same as the above Fig. 9 The second welding groove 415b of the third embodiment is the same as that of the second welding groove 415b of the third embodiment, and will not be described in detail here.

[0099] Since the vane groove 412 is also formed by removing part of the solid structure of the cylinder 410, the strength and rigidity of the part where the vane groove 412 is located are relatively weak. If the welding groove 415 is close to the vane groove 412, the vane groove 412 is also prone to deformation, which will affect the rotation of the roller 420 and the sliding of the vane 430, resulting in increased vibration and noise.

[0100] In this regard, in one embodiment, please combine Fig.10 And refer to Fig.13 , Fig.13This is a cross-sectional view of the welding of the cylinder and the housing according to the sixth embodiment of the utility model, in which the welding groove 415 includes a fifth welding groove 415e adjacent to the slide groove 412, and the fifth welding groove 415e is located between the first welding groove 415a and the slide groove 412. It can be understood that the fifth welding groove 415e is a welding groove 415 located between the first welding groove 415a and the slide groove 412 and is the most adjacent to the slide groove 412.

[0101] On the projection surface along the axial projection of the cylinder 410, the line connecting the center of the fifth welding groove 415e and the center of the cylinder 410 is K, and the slide groove 412 includes a second groove wall 4121. Along the circumference of the cylinder 410, the line connecting one side of the second groove wall 4121 and the center of the cylinder 410 is J1, and the line connecting the other side of the second groove wall 4121 and the center of the cylinder 410 is J2. The minimum angle between K and J1 is θ, and the maximum angle between J1 and J2 is δ, satisfying the following relationship: θ≥δ.

[0102] It can be understood that to minimize the angle between K and J1, J1 is the line closest to K. Fig.10 For example, the line closest to K is the line connecting the endpoint C on the second groove wall 4121 and the center of the cylinder 410. The minimum angle θ between K and J1 is the central angle formed by the line connecting the endpoint C and the center of the cylinder 410 and K. To maximize the angle between J1 and J2, J2 is the line farthest from J1. Fig.10 As shown, the line farthest from J1 is the line between the endpoint D and the center line of the cylinder 410, and the maximum angle between J1 and J2 is δ, which is the central angle formed by the line between the endpoint D and the center line of the cylinder 410 and the line between the endpoint C and the center of the cylinder 410. The range of this central angle can cover the entire area of ​​the slide slot 412.

[0103] The smaller the angle between K and J1, the closer the fifth welding groove 415e is to the boundary of the vane groove 412, that is, the closer the fifth welding groove 415e is to the vane groove 412, the greater the influence on the vane groove 412 when the cylinder 410 is welded to the shell 100 through the fifth welding groove 415e, the easier it is to cause the vane groove 412 to deform, resulting in the overall deformation of the cylinder 410, causing the vane 430 and the vane groove 412 to move poorly, causing abnormal wear of the vane 430 and the vane groove 412, and abnormal wear of the roller 420 and the cylinder 410, affecting the reliability of the compressor. Moreover, the closer the fifth welding groove 415e is to the vane groove 412, the larger the non-solid part of the cylinder 410 corresponding to this area, and the overall structural rigidity of the cylinder 410 is reduced, causing the cylinder 410 to be more easily deformed. By making θ≥δ, the fifth welding groove 415e has a larger distance relative to the vane groove 412, which can reduce the impact of the fifth welding groove 415e on the vane groove 412 when welded to the shell 100, reduce the deformation of the vane groove 412, and thus reduce the overall deformation of the cylinder 410. It can reduce abnormal wear of the vane 430, roller 420 and crankshaft 200 caused by the deformation of the cylinder 410, further reduce vibration and noise, and improve the reliability of the compressor operation.

[0104] In order to prevent the local welding heat of the cylinder 410 from being too high, a plurality of welding grooves 415 are evenly arranged along the outer periphery of the cylinder 410. In one embodiment, the plurality of welding grooves 415 are evenly arranged along the outer periphery of the cylinder 410 after first considering that the first welding groove 415a and the second welding groove 415b satisfy the above relationship.

[0105] It should be noted that the uniform distribution here can be a exactly uniform distribution (the angle between the center of any two adjacent welding grooves 415 and the center line of the cylinder 410 is the same), or it can be a roughly uniform distribution. For example, if the angle between the center of any two adjacent welding grooves 415 and the center line of the cylinder 410 has a small angle deviation (for example, less than 5°), it can also be considered to be within the range of uniform distribution.

[0106] By evenly distributing multiple welding grooves 415 along the outer periphery of the cylinder 410, the heat generated by each welding groove 415 can be evenly transferred to other areas of the cylinder 410, avoiding the situation where the distance between some welding grooves 415 is too close, resulting in excessive local heat in the cylinder 410, and making the thermal expansion of various parts of the cylinder 410 due to welding heat almost consistent, thereby reducing the deformation of the cylinder 410 caused by inconsistent thermal expansion, and reducing abnormal wear caused by deformation of the roller 420 and the crankshaft 200 leading to the cylinder 410, thereby reducing vibration and noise.

[0107] In order to further reduce vibration and noise and improve the reliability of the rotary compressor 10, in one embodiment, please refer to Fig.14 and Fig.15 , Fig.14 This is a schematic diagram of the structure of a cylinder according to an embodiment of the utility model. Fig.15 for Fig.14 The partial enlarged view of the position A in the middle. The line connecting the groove wall of the welding groove 415 and the center of the cylinder 410 is R, and the length of the part of R passing through the solid part of the cylinder 410 is greater than or equal to 23 mm.

[0108] It should be understood that the length of the part of the line R between the groove wall of the welding groove 415 and the center of the cylinder 410 passing through the solid part of the cylinder 410 refers to the length of the solid part remaining after removing the cavity part (such as the active cavity 411 and other groove structures, hole structures, etc.) between the line connecting a point on the groove wall of the welding groove 415 and the center of the cylinder 410 in the radial direction of the cylinder 410. Fig.15 As shown, for Fig.15 In the welding groove 415 shown in FIG, the length R passing through the solid part of the cylinder 410 is R1+R2+R3, and R1+R2+R3≥23 mm.

[0109] By limiting the radial length of this part of the solid structure to be greater than or equal to 23 mm, the radially weakest part of the cylinder 410 has a sufficient length to ensure the rigidity and strength of the cylinder 410 and further reduce the deformation of the cylinder 410.

[0110] In one embodiment, please refer to Figure 1 The rotary compressor 10 includes a first cylinder 410a and a second cylinder 410b, which are spaced apart along the height direction of the shell 100. The first cylinder 410a is located on the side of the second cylinder 410b away from the bottom wall of the shell 100. A partition 500 is provided between the first cylinder 410a and the second cylinder 410b to separate the first cylinder 410a from the second cylinder 410b.

[0111] The first cylinder 410a is a cylinder 410 conceived and manufactured by any of the above embodiments, and the first cylinder 410a is welded to the side wall of the housing 100 through the welding groove 415. By welding the first cylinder 410a to the housing 100, since the first cylinder 410a is located between the motor assembly 300 and the second cylinder 410b, the first cylinder 410a is close to the middle of the housing 100, which is beneficial to improve the overall rigidity of the rotary compressor 10.

[0112] In order to stably support and fix the crankshaft 200 and the motor assembly 300 to further reduce vibration and noise, the rotary compressor 10 also includes a first bearing 600 and a second bearing 700. The first bearing 600 is arranged on the side of the first cylinder 410a away from the second cylinder 410b and rotatably cooperates with the outer wall of the crankshaft 200. The second bearing 700 is arranged on the side of the second cylinder 410b away from the first cylinder 410a and rotatably cooperates with the outer wall of the crankshaft 200.

[0113] like Figure 1 As shown, the rotary compressor 10 may further be provided with a first muffler 800 and a second muffler 900 to absorb the noise generated during the exhaust process of the cylinder 410 .

[0114] The present application also provides a refrigeration device, which includes a rotary compressor 10 based on any of the above embodiments. The refrigeration device can be an electrical appliance such as an air conditioner or a refrigerator.

[0115] Since the refrigeration device adopts all the technical solutions of the rotary compressor 10 of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment.

[0116] The embodiments of the present invention are described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A cylinder, characterized in that: Applied to a rotary compressor, the outer periphery of the cylinder is provided with a notch groove and a welding groove, the notch groove includes a first groove wall surface, and the welding groove includes a first welding groove adjacent to the notch groove; On the projection surface along the axial direction of the cylinder, the line connecting the center of the first welding groove and the center of the cylinder is L, along the circumference of the cylinder, the line connecting one side of the first groove wall and the center of the cylinder is H1, and the line connecting the other side of the first groove wall and the center of the cylinder is H2, the minimum angle between L and H1 is α, and the maximum angle between H1 and H2 is β, satisfying: α≥β / 2.

2. The cylinder according to claim 1, characterized in that The welding groove includes a second welding groove, and the notch groove is located between the first welding groove and the second welding groove; On the projection surface along the axial direction of the cylinder, the line connecting the center of the notch groove and the center of the cylinder is H3, and the distance from the center of the first welding groove to H3 is equal to the distance from the center of the second welding groove to H3.

3. The cylinder according to claim 2, characterized in that The cylinder is also provided with an air suction hole, the second welding groove is adjacent to the air suction hole, and the air suction hole includes a hole wall surface; On the projection surface along the axial direction of the cylinder, the line connecting the center of the second welding groove and the center of the cylinder is Y, along the circumference of the cylinder, the line connecting one side of the hole wall and the center of the cylinder is T1, and the line connecting the other side of the hole wall and the center of the cylinder is T2, the minimum angle between Y and T1 is λ, and the maximum angle between T1 and T2 is ω, satisfying: λ≥ω.

4. The cylinder according to claim 2, characterized in that The cylinder is also provided with an air suction hole, the welding groove comprises a third welding groove adjacent to the air suction hole, the third welding groove is located between the second welding groove and the air suction hole, and the air suction hole comprises a hole wall surface; On the projection surface along the axial direction of the cylinder, the line connecting the center of the third welding groove and the center of the cylinder is P, along the circumference of the cylinder, the line connecting one side of the hole wall and the center of the cylinder is T1, and the line connecting the other side of the hole wall and the center of the cylinder is T2, the minimum angle between P and T1 is γ, and the maximum angle between T1 and T2 is ω, satisfying: γ≥ω.

5. The cylinder according to claim 1, characterized in that The cylinder is provided with an air suction hole, the welding groove comprises a fourth welding groove adjacent to the air suction hole, the fourth welding groove and the first welding groove are respectively located on both sides of the notch groove, and the air suction hole comprises a hole wall surface; On the projection surface along the axial direction of the cylinder, the line connecting the center of the fourth welding groove and the center of the cylinder is F, along the circumference of the cylinder, the line connecting one side of the hole wall and the center of the cylinder is T1, and the line connecting the other side of the hole wall and the center of the cylinder is T2, the minimum angle between F and T1 is η, and the maximum angle between T1 and T2 is ω, satisfying: η≥ω.

6. The cylinder according to any one of claims 1 to 5, characterized in that: The cylinder is further provided with a sliding vane groove, the sliding vane groove includes a second groove wall surface, the welding groove includes a fifth welding groove adjacent to the sliding vane groove, and the fifth welding groove is located between the first welding groove and the sliding vane groove; On the projection surface along the axial direction of the cylinder, the line connecting the center of the fifth welding groove and the center of the cylinder is K, along the circumference of the cylinder, the line connecting one side of the second groove wall and the center of the cylinder is J1, and the line connecting the other side of the second groove wall and the center of the cylinder is J2, the minimum angle between K and J1 is θ, and the maximum angle between J1 and J2 is δ, satisfying: θ≥δ.

7. The cylinder according to any one of claims 1 to 5, characterized in that: The line connecting the groove wall surface of the welding groove and the center of the cylinder is R, and the length of the part of R passing through the solid part of the cylinder is greater than or equal to 23 mm.

8. The cylinder according to any one of claims 1 to 5, characterized in that: The number of the welding grooves is greater than or equal to 5.

9. The cylinder according to any one of claims 1 to 5, characterized in that: The number of the welding grooves is multiple, and the multiple welding grooves are evenly distributed along the outer periphery of the cylinder.

10. A rotary compressor, characterized in that A cylinder comprising the cylinder according to any one of claims 1 to 9.

11. The rotary compressor according to claim 10, characterized in that: The rotary compressor includes a shell and a first cylinder and a second cylinder arranged in the shell, the shell includes a bottom wall, the first cylinder and the second cylinder are spaced apart along the height direction of the shell, the first cylinder is located on the side of the second cylinder away from the bottom wall, and the first cylinder is welded to the side wall of the shell through the welding groove.

12. Refrigeration equipment, characterized in that Including the rotary compressor described in claim 10 or 11.

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