Compressor and refrigerating system

Abstract

The invention discloses a compressor and a refrigerating system. The compressor comprises a machine shell, a motor and a pump body assembly. The shell is provided with an accommodating cavity; the motor is arranged in the containing cavity and comprises a rotor and a stator arranged on the periphery of the rotor in a sleeving mode. The pump body assembly is arranged in the containing cavity, the pump body assembly comprises a crankshaft, a static scroll plate, a movable scroll plate and a support, the crankshaft sequentially penetrates through the support, the movable scroll plate, the static scroll plate and the motor, the crankshaft comprises an eccentric section, and the movable scroll plate is arranged on the eccentric section in a sleeving mode; the outer diameter D of the stator and the outer diameter D1 of the eccentric section meet the relational expression that D / D1 is larger than or equal to 5 and smaller than or equal to 7. The problem that in the prior art, a crankshaft of a scroll compressor is low in reliability can be solved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration, in particular to a compressor and a refrigeration system. BACKGROUND

[0002] The compressor is a core component of heat exchange equipment such as air conditioners and refrigerators, which is mainly divided into piston compressors, rotary compressors and scroll compressors. Among them, the scroll compressor is mainly composed of a motor, a crankshaft, a dynamic disc, a static disc, a cross slip ring and a main frame. The conventional scroll compressor is mainly divided into two types of pump body top and pump body bottom. The dynamic disc base plate of the two types of scroll compressors is provided with scroll teeth on one side and a bearing part on the other side. The eccentric shaft of the crankshaft is installed inside the bearing part. The eccentric shaft rotates to drive the dynamic disc to rotate. The dynamic disc and the static disc mesh to complete a series of processes such as suction, compression and exhaust.

[0003] At present, the dynamic scroll disc of the scroll compressor is mainly arranged on the eccentric part of the crankshaft. However, the geometric centers of the eccentric part and the scroll tooth meshing parts of the dynamic scroll disc and the static scroll disc are not at the same height. During the operation of the scroll compressor, the dynamic scroll disc will tilt to a certain extent, resulting in high noise and vibration of the scroll compressor. At the same time, the crankshaft will be worn, reducing the reliability of the crankshaft. SUMMARY

[0004] The main purpose of the present application is to provide a compressor and a refrigeration system to solve the problem of low reliability of the crankshaft of the scroll compressor in the prior art.

[0005] According to one aspect of the present application, a compressor is provided, comprising:

[0006] A shell having a receiving cavity;

[0007] A motor arranged in the receiving cavity, the motor comprising a rotor and a stator sleeved on the outer periphery of the rotor;

[0008] A pump body assembly arranged in the receiving cavity, the pump body assembly comprising a crankshaft, a static scroll disc, a dynamic scroll disc and a bracket, the crankshaft penetrating the bracket, the dynamic scroll disc, the static scroll disc and the motor in sequence, the crankshaft comprising an eccentric section, and the dynamic scroll disc being sleeved on the eccentric section;

[0009] Wherein, the outer diameter D of the stator and the outer diameter D1 of the eccentric section satisfy the relationship: 5≤D / D1≤7.

[0010] Further, the crankshaft further comprises a first section, the first section and the eccentric section being arranged in sequence along the axial direction of the crankshaft, and the static scroll disc being sleeved on one end of the first section close to the eccentric section.

[0011] The outer diameter D2 of the first section and the outer diameter D1 of the eccentric section satisfy the relationship: 1.05≤D1 / D2≤1.45.

[0012] Further, the outer diameter D1 of the eccentric section and the outer diameter D2 of the first section satisfy the relationship: D2≤D1.

[0013] Further, the crankshaft further comprises a second section, the first section, the eccentric section and the second section are sequentially arranged along the axial direction of the crankshaft, and the bracket is sleeved on one end of the second section close to the eccentric section.

[0014] The outer diameter D3 of the second section and the outer diameter D1 of the eccentric section satisfy the relationship: 1.25≤D1 / D3≤1.65.

[0015] Further, the outer diameter D1 of the eccentric section and the outer diameter D3 of the second section satisfy the relationship: D3≤D1.

[0016] Further, the outer diameter D of the stator satisfies the relationship: D≤114mm.

[0017] Further, the orbiting scroll plate comprises a gray cast iron orbiting scroll plate or a cast iron orbiting scroll plate with a tensile strength greater than 250Mpa; and / or,

[0018] The fixed scroll plate comprises a gray cast iron fixed scroll plate or a cast iron fixed scroll plate with a tensile strength greater than 250Mpa; and / or,

[0019] The bracket comprises a gray cast iron bracket or a cast iron bracket with a tensile strength greater than 250Mpa; and / or,

[0020] The crankshaft comprises a nodular cast iron crankshaft or a cast iron crankshaft with a tensile strength greater than 600Mpa; and / or,

[0021] The crankshaft comprises a 20Cr steel crankshaft or a 40Cr steel crankshaft.

[0022] Further, an oil supply channel is arranged on the crankshaft, and the oil supply channel extends from the end of the second section of the crankshaft towards the first section of the crankshaft.

[0023] Further, the compressor comprises a vertical compressor or a horizontal compressor.

[0024] In another aspect, the application further provides a refrigeration system comprising the above compressor.

[0025] Compared with the structure of the scroll compressor in the prior art, the present application sets the proportional relationship between the outer diameter of each shaft section of the crankshaft and the outer diameter of the stator, so as to ensure that the geometric center of the eccentric section and the meshing part of the scroll gear of the dynamic scroll and the static scroll are at the same height, thereby greatly reducing the overturning moment of the dynamic scroll, the dynamic scroll is not easy to overturn, the noise and vibration of the compressor are reduced to a certain extent, the eccentric section is not seriously worn due to the overturning of the dynamic scroll, the reliability of the scroll compressor is improved, and the miniaturization design of the scroll compressor is facilitated. BRIEF DESCRIPTION OF DRAWINGS

[0026] The accompanying drawings, which are included to provide a further understanding of the present application and constitute a part of this application, illustrate certain illustrative embodiments of the present application and together with the description serve to explain the present application. In the drawings:

[0027] Figure 1 A sectional view of the compressor disclosed in the embodiments of the present application;

[0028] Figure 2 A structure schematic view of the crankshaft disclosed in the embodiments of the present application;

[0029] Figure 3 A sectional view of the pump body assembly disclosed in the embodiments of the present application;

[0030] Figure 4 An exploded view of the pump body assembly (without the crankshaft) disclosed in the embodiments of the present application.

[0031] Among them, the above-mentioned drawings include the following reference signs:

[0032] 10, housing; 101, accommodating cavity; 20, motor; 21, rotor; 22, stator; 30, pump body assembly; 31, crankshaft; 311, first section; 312, eccentric section; 313, second section; 32, static scroll; 33, dynamic scroll; 331, second scroll tooth part; 34, bracket; 40, oil supply channel; 50, exhaust pipe; 60, cross slip ring; 70, sealing ring; 80, muffler. DETAILED DESCRIPTION

[0033] It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0034] It is to be understood that the terminology used herein is for the purpose of describing specific embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, steps, operations, elements, components, and / or groups thereof, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or groups thereof.

[0035] The relative arrangement of parts and steps, numerical expressions, and numerical values set forth in the examples are not intended to limit the scope of the present application unless otherwise specifically stated. It is to be understood that the actual dimensions of the various parts shown in the drawings are not necessarily to scale. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered as if they were specified in the patent specification. In all examples shown and discussed herein, any specific values are to be interpreted as merely illustrative and not limiting. Other examples of the example embodiments can have different values. It is noted that like numbers and letters refer to like elements throughout the several views of the drawings, and thus, once an element is defined in one drawing, it is not necessary to discuss it further in subsequent drawings.

[0036] As mentioned in the background, the eccentric part of the existing scroll compressor and the meshing part of the scroll gears of the dynamic scroll plate and the static scroll plate are not at the same height. When the scroll compressor is running, the dynamic scroll plate will tilt, resulting in relatively high noise and vibration of the scroll compressor, and also causing wear to the crankshaft, reducing the reliability of the crankshaft. Therefore, in order to improve the reliability of the crankshaft of the scroll compressor, the inventors of the present application have designed a new type of compressor, which will be described in detail below in combination with the drawings.

[0037] Referring to Figures 1 to 4 As shown in the drawings, the present application provides a compressor, which comprises a casing 10, a motor 20 and a pump body assembly 30.

[0038] The casing 10 has a receiving cavity 101; the motor 20 is arranged in the receiving cavity 101, and the motor 20 comprises a rotor 21 and a stator 22 sleeved on the outer periphery of the rotor 21; the pump body assembly 30 is arranged in the receiving cavity 101, and the pump body assembly 30 comprises a crankshaft 31, a static scroll plate 32, a dynamic scroll plate 33 and a bracket 34. The crankshaft 31 penetrates the bracket 34, the dynamic scroll plate 33, the static scroll plate 32 and the motor 20 in sequence, and the crankshaft 31 comprises an eccentric section 312, and the dynamic scroll plate 33 is sleeved on the eccentric section 312; wherein the outer diameter D of the stator 22 and the outer diameter D1 of the eccentric section 312 satisfy the relationship: 5≤D / D1≤7.

[0039] In the application, when the compressor is actually processed, the motor 20 and the pump body assembly 30 can be installed in the accommodating cavity 101, and the crankshaft 31 in the pump body assembly 30 is sequentially penetrated through the support 34, the moving scroll 33, the static scroll 32 and the motor 20, in the process, the motor 20 is drivingly connected with the crankshaft 31, when the motor 20 drives the crankshaft 31 to rotate, the moving scroll 33 can be driven to rotate, and in turn, the static scroll 32 is driven to rotate relative to the moving scroll 33, so as to compress the refrigerant and the like entering the inside of the pump body assembly 30 from outside; and in the process of the rotation of the crankshaft 31, since the moving scroll 33 is sleeved on the eccentric section 312 of the crankshaft 31, the moving scroll 33 will synchronously rotate with the eccentric section 312, and by setting the proportional relationship between the outer diameter D of the stator 22 and the outer diameter D1 of the eccentric section 312, it can be ensured that the geometric center of the meshing part of the scroll gears of the eccentric section 312 and the moving scroll 33 and the static scroll 32 is at the same height, so that the overturning moment of the moving scroll 33 is greatly reduced, the moving scroll 33 is not easy to overturn, the noise and vibration of the compressor are reduced to a certain extent, at the same time, the eccentric section 312 will not be severely worn due to the overturning of the moving scroll 33, and the reliability of the scroll compressor is improved. In addition, by limiting the proportional relationship between the stator 22 and the crankshaft 31, the production and manufacturing cost of the pump body assembly 30 and the compressor can also be reduced, which is beneficial to realize the miniaturization design of the compressor.

[0040] Specifically, the outer diameter D of the stator 22 and the outer diameter D1 of the eccentric section 312 in the embodiment satisfy the relationship: 5≤D / D1≤7, for example, D / D1 can be 5.0, 5.2, 5.4, 5.6, 5.8, 6.0, 6.2, 6.4, 6.6, 6.8, 7.0 and any value between them. In this way, the overturning moment of the moving scroll 33 can be reduced, so as to reduce the noise and vibration of the compressor, and the wear degree of the eccentric section 312 will not be increased, and the reliability of the scroll compressor is improved to a certain extent.

[0041] In the application, when the pump body assembly 30 is actually installed, the support 34 or the static scroll 32 can be fixed on the inner wall of the accommodating cavity 101 by welding, fastener connection and the like, the static scroll 32 can be fixedly installed on the support 34 by fastener connection and the like, and the moving scroll 33 is installed between the support 34 and the static scroll 32.

[0042] Optionally, the fastener in the application includes a fastening pin or a screw, and the application does not make specific limitations, as long as other deformation modes under the concept of the application are within the protection scope of the application.

[0043] Further, referring to Figures 1 to 2As shown, the crankshaft 31 in the embodiment further comprises a first section 311, the first section 311 and the eccentric section 312 are sequentially arranged along the axis direction of the crankshaft 31, and the static scroll 32 is sleeved on one end of the first section 311 close to the eccentric section 312; wherein the outer diameter D2 of the first section 311 and the outer diameter D1 of the eccentric section 312 satisfy the relationship: 1.05≤D1 / D2≤1.45, for example, D1 / D2 can be 1.05, 1.10, 1.15, 1.20, 1.25, 1.30, 1.35, 1.40, 1.45 and any value between them. In this way, the friction area between the crankshaft 31 and the dynamic scroll 33 and the static scroll 32 can be reduced, thereby avoiding the wear of the crankshaft 31, improving the performance of the compressor, optimizing the overall performance of the compressor, effectively ensuring the reliability of the crankshaft 31, and at the same time, arranging the first section 311 and the eccentric section 312 according to the above ratio relationship is conducive to realizing the miniaturization design of the pump body assembly 30 and the compressor. When D1 / D2 does not satisfy this ratio, the crankshaft 31 will be worn during the operation of the compressor, reducing the reliability of the crankshaft 31 and reducing the service life of the compressor.

[0044] Specifically, the outer diameter D1 of the eccentric section 312 and the outer diameter D2 of the first section 311 in the embodiment satisfy the relationship: D2≤D1. In this way, the crankshaft 31 can have high structural strength, thereby ensuring the smooth operation of the crankshaft 31 and reducing the vibration of the pump body assembly 30, thereby improving the reliability of the pump body assembly 30 and the compressor.

[0045] Further, referring to Figures 1 to 2 As shown, the crankshaft 31 in the embodiment further comprises a second section 313, the first section 311, the eccentric section 312 and the second section 313 are sequentially arranged along the axis direction of the crankshaft 31, and the bracket 34 is sleeved on one end of the second section 313 close to the eccentric section 312; wherein the outer diameter D3 of the second section 313 and the outer diameter D1 of the eccentric section 312 satisfy the relationship: 1.25≤D1 / D3≤1.65, for example, D1 / D3 can be 1.25, 1.30, 1.35, 1.40, 1.45, 1.50, 1.55, 1.60, 1.65 and any value between them. In this way, the friction area between the crankshaft 31 and the dynamic scroll 33 and the bracket 34 can be reduced, thereby avoiding the wear of the crankshaft 31, improving the performance of the compressor, optimizing the overall performance of the compressor, effectively ensuring the reliability of the crankshaft 31, and at the same time, arranging the second section 313 and the eccentric section 312 according to the above ratio relationship is conducive to realizing the miniaturization design of the pump body assembly 30 and the compressor. When D1 / D3 does not satisfy this ratio, the crankshaft 31 will be worn during the operation of the compressor, reducing the reliability of the crankshaft 31 and reducing the service life of the compressor.

[0046] Specifically, the outer diameter D1 of the eccentric section 312 and the outer diameter D3 of the second section 313 satisfy the relationship D3≤D1. In this way, the crankshaft 31 has high structural strength, ensuring smooth operation of the crankshaft 31 and reducing vibration of the pump body assembly 30, thereby improving the reliability of the pump body assembly 30 and the compressor.

[0047] In combination Figure 2 As shown, the crankshaft 31 includes a first section 311, an eccentric section 312, and a second section 313, which are arranged in sequence along the axis of the crankshaft 31. The motor 20 is mounted on the first section 311. The static scroll 32 is sleeved on the side of the first section 311 close to the eccentric section 312, and the side of the static scroll 32 close to the dynamic scroll 33 is provided with a first scroll tooth portion (not shown in the figure). The bracket 34 is sleeved on the side of the second section 313 close to the eccentric section 312 and surrounds the static scroll 32 to form a cavity. The dynamic scroll 33 is installed in the cavity and sleeved on the eccentric section 312, and the side of the dynamic scroll 33 close to the static scroll 32 is provided with a second scroll tooth portion 331 (as shown in Figure 4 When the motor 20 operates, it can drive the crankshaft 31 to rotate, thereby driving the dynamic scroll 33 to rotate, and further driving the first scroll tooth portion to rotate relative to the second scroll tooth portion 331 to compress the refrigerant inside the pump body assembly 30.

[0048] As can be understood, referring to Figure 1 As shown, the static scroll 32 is arranged close to the top of the accommodating cavity 101, and the top of the accommodating cavity 101 has an exhaust pipe 50. Compared with the structure in which the static scroll 32 is arranged close to the bottom of the accommodating cavity 101, in the embodiment, the refrigerant discharged from the pump body assembly 30 can be directly discharged into the top chamber of the accommodating cavity 101 and then discharged from the exhaust pipe 50, without the need to arrange a drainage channel or other structure on the static scroll 32. The compressed refrigerant can be directly discharged to the top of the accommodating cavity 101, and the exhaust passage is smoother. This not only reduces the production cost of the compressor, but also reduces the energy consumption of the compressor and improves the energy efficiency of the compressor.

[0049] Further, the outer diameter D of the stator 22 in the embodiment satisfies the relationship: D≤114mm, for example, D can be 114mm, 110mm, 106mm, 102mm, 98mm, 94mm, 90mm or 85mm, etc. Thus, the corresponding proportional relationship between the first section 311, the eccentric section 312 and the second section 313 can be achieved, thereby reducing the possibility of overturning of the orbiting scroll 33, reducing the noise and vibration of the pump body assembly 30 and the compressor to a certain extent, effectively ensuring the smooth operation of the compressor, and improving the reliability of the compressor.

[0050] Alternatively, the orbiting scroll 33 in the embodiment includes a gray cast iron (HT250) orbiting scroll or a cast iron orbiting scroll with a tensile strength greater than 250Mpa. Since the gray cast iron has high strength, good wear resistance and heat resistance, good damping performance, and good casting performance, etc., using it as the material for manufacturing the orbiting scroll 33 can make the orbiting scroll 33 bear a larger load, to a certain extent, reduce the overturning moment of the orbiting scroll 33, and the orbiting scroll 33 is not easy to overturn, thereby reducing the noise and vibration of the pump body assembly 30 and the compressor, and reducing the possibility of wear of the crankshaft 31, improving the reliability of the crankshaft 31, and thereby prolonging the service life of the compressor. And using the cast iron material with a tensile strength greater than 250Mpa to manufacture the orbiting scroll 33 can improve the load bearing capacity of the orbiting scroll 33, thereby reducing the noise and vibration of the pump body assembly 30 and the compressor, and reducing the possibility of wear of the crankshaft 31, improving the reliability of the crankshaft 31, and reducing the use of cast iron material, thereby reducing the manufacturing cost of the orbiting scroll 33.

[0051] Alternatively, the orbiting scroll 33 in the embodiment includes a gray cast iron (HT250) orbiting scroll or a cast iron orbiting scroll with a tensile strength greater than 250Mpa. Since the gray cast iron has high strength, good wear resistance and heat resistance, good damping performance, and good casting performance, etc., using it as the material for manufacturing the orbiting scroll 33 can make the orbiting scroll 33 bear a larger load, to a certain extent, reduce the overturning moment of the orbiting scroll 33, and the orbiting scroll 33 is not easy to overturn, thereby reducing the noise and vibration of the pump body assembly 30 and the compressor, and reducing the possibility of wear of the crankshaft 31, improving the reliability of the crankshaft 31, and thereby prolonging the service life of the compressor. And using the cast iron material with a tensile strength greater than 250Mpa to manufacture the orbiting scroll 33 can improve the load bearing capacity of the orbiting scroll 33, thereby reducing the noise and vibration of the pump body assembly 30 and the compressor, and reducing the possibility of wear of the crankshaft 31, improving the reliability of the crankshaft 31, and reducing the use of cast iron material, thereby reducing the manufacturing cost of the orbiting scroll 33.

[0052] Optionally, the bracket 34 in the embodiment comprises a gray cast iron bracket or a cast iron bracket with a tensile strength greater than 250Mpa. Since the gray cast iron has high strength, good wear resistance and heat resistance, good damping performance and good casting performance, using the gray cast iron as the material of the bracket 34 can make the bracket 34 bear a larger load, improve the reliability of the crankshaft 31, and thus prolong the service life of the compressor. Using the cast iron material with a tensile strength greater than 250Mpa to make the bracket 34 can not only improve the load-bearing capacity of the bracket 34 and the reliability of the crankshaft 31, but also reduce the use of cast iron material and the manufacturing cost of the bracket 34.

[0053] Optionally, the crankshaft 31 in the embodiment comprises a nodular cast iron (QT600) crankshaft or a cast iron crankshaft with a tensile strength greater than 600Mpa. Since the nodular cast iron has good wear resistance and damping performance, using the nodular cast iron as the material of the crankshaft 31 can reduce the noise and vibration of the pump body assembly 30 and the compressor, effectively ensure the smooth operation of the compressor, and improve the reliability of the compressor. At the same time, the outer circumferential surface of the crankshaft 31 is treated by phosphating, molybdenizing or coating with a high polymer material having self-lubricating property.

[0054] Optionally, the crankshaft 31 in the embodiment comprises a 20Cr steel crankshaft or a 40Cr steel crankshaft. Both the 20Cr steel and the 40Cr steel have high strength and good wear resistance, which improves the performance of the crankshaft 31, effectively avoids the adverse effects of excessive wear of the crankshaft 31 on the performance of the compressor during rotation, and prolongs the service life of the compressor. At the same time, the outer circumferential surface of the crankshaft 31 is subjected to surface hardening treatment such as high-frequency quenching, carburizing, nitriding or diamond-like carbon (DLC) coating, so that the surface hardness of the crankshaft 31 reaches HRC35 or above.

[0055] It should be noted that 20Cr and 40Cr are standard steel numbers in China, HRC is Rockwell hardness, and HRC35 means Rockwell hardness of 35.

[0056] Further, referring to Figure 1As shown, the crankshaft 31 in the embodiment is provided with an oil supply channel 40 extending from the end of the second section 313 of the crankshaft 31 towards the first section 311 of the crankshaft 31. Specifically, as the second section 313 of the crankshaft 31 in the embodiment is located at the bottom of the vertical compressor, when the oil supply channel 40 is provided on the crankshaft 31 and extends from the second section 313 of the crankshaft 31 towards the first section 311 of the crankshaft 31, the oil in the oil pool at the bottom of the vertical compressor can be conveniently transported from the end of the second section 313 towards the first section 311, facilitating the lubrication of the pump body assembly 30, thereby avoiding the overturning of the orbiting scroll 33 and the increase of the friction between the orbiting scroll 33 and the eccentric section 312, reducing the contact area between the orbiting scroll 33 and the crankshaft 31, to some extent, reducing the friction loss of the compressor and ensuring the reliability of the crankshaft 31.

[0057] Further, the compressor in the embodiment includes a vertical compressor (as shown in Figure 1 ) or a horizontal compressor (not shown in the figure). As the crankshaft 31 in the embodiment sequentially penetrates the bracket 34, the orbiting scroll 33, the fixed scroll 32 and the motor 20, when the compressor is a vertical compressor, the bracket 34 is arranged on the side close to the bottom of the accommodating cavity 101 (i.e. the bracket 34 is arranged close to the oil surface based on the oil surface), and the motor 20 is arranged on the side away from the bottom of the accommodating cavity 101 and is drivingly connected with the first section 311 of the crankshaft 31 to form a structure in which the pump body assembly 30 is installed in a down position. The crankshaft 31 is provided with the oil supply channel 40, and when the pump body assembly 30 is installed in a down position, the oil supply distance of the oil supply channel 40 can be shortened, so that the lubricating oil can quickly reach the bearing of the pump body assembly 30 during the start-up stage, facilitating the lubrication of the pump body assembly 30, to some extent, reducing the production and manufacturing cost of the pump body assembly 30 and the compressor, and being conducive to the miniaturization and high speed of the pump body assembly 30 and the compressor. In the horizontal compressor, the oil surface is not taken as the reference, but the crankshaft 31 still sequentially penetrates the rotor 21, the fixed scroll 32, the orbiting scroll 33 and the bracket 34.

[0058] Further, referring to Figure 1 and Figure 4 , the pump body assembly 30 in the embodiment further includes a cross slip ring 60 arranged between the orbiting scroll 33 and the bracket 34. In this way, the orbiting scroll 33 can be conveniently positioned. In addition, in order to facilitate the sealing of the gap between the bracket 34 and the orbiting scroll 33, a sealing ring 70 is arranged between the orbiting scroll 33 and the bracket 34 (as shown in Figure 4 ). After the pump body assembly 30 is assembled, as shown in Figure 3As shown, the sealing ring 70 is located in the groove of the bracket 34, and the top surface of the sealing ring 70 is attached to the orbiting scroll 33, and the outer surface of the sealing ring 70 is attached to the side wall surface of the groove. In this way, when the pump body assembly starts to work, the sealing ring 70 is close to the inner side of the crankshaft 31, which is a high-pressure gas space, and the outer side of the sealing ring 70 away from the crankshaft is a medium-pressure gas discharged during the gas compression process.

[0059] Alternatively, in other embodiments of the present application, the cross slip ring 60 can also be provided as a spherical coupling or a cylindrical pin coupling, etc., as long as it is other deformation modes under the concept of the present application, which is within the protection scope of the present application.

[0060] Further, referring to Figure 1 As shown, the pump body assembly 30 in the embodiment further includes a muffler 80, which is arranged on the side of the fixed scroll 32 away from the orbiting scroll 33, and the muffler 80 is provided with an air outlet hole (not shown in the figure). The muffler 80 is used for muffling the refrigerant. Specifically, the refrigerant is compressed by the orbiting scroll 33 and the fixed scroll 32, then discharged from the fixed scroll 32, and then enters the muffler 80. After the muffler 80 muffles the refrigerant, the refrigerant is discharged into the containing cavity, and finally discharged from the exhaust pipe 50 of the containing cavity to the outside of the compressor.

[0061] The compressor of the present application will be described in detail below in combination with specific embodiments.

[0062] Embodiment 1

[0063] Referring to Figure 1 As shown, the compressor in the embodiment includes a housing 10, a motor 20 and a pump body assembly 30. The motor 20 and the pump body assembly 30 are both installed in a containing cavity 101. The motor 20 includes a rotor 21 and a stator 22 sleeved on the outer periphery of the rotor 21. The pump body assembly 30 includes a crankshaft 31, a fixed scroll 32, an orbiting scroll 33 and a bracket 34. The crankshaft 31 penetrates the bracket 34, the orbiting scroll 33, the fixed scroll 32 and the motor 20 in sequence. The crankshaft 31 includes an eccentric section 312, and the orbiting scroll 33 is sleeved on the eccentric section 312.

[0064] In actual processing of the compressor, the compressor is processed according to the following size data, wherein the outer diameter of the stator 22 is 70 mm; the outer diameter of the eccentric section 312 is 12 mm; the outer diameter of the first section 311 is 10 mm; and the outer diameter of the second section 313 is 9 mm. In this way, D / D1=5.83, D1 / D2=1.2, D1 / D3=1.33, D2<D1, and D3<D1.

[0065] Embodiment 2

[0066] Unlike the embodiment 1, the outer diameter of the stator 22 in this embodiment is 90 mm; the outer diameter of the eccentric section 312 is 14 mm; the outer diameter of the first section 311 is 12 mm; and the outer diameter of the second section 313 is 10 mm. Thus, D / D1 = 6.43, D1 / D2 = 1.17, D1 / D3 = 1.4, D2 < D1, and D3 < D1.

[0067] Embodiment 3

[0068] Unlike the embodiment 1, the outer diameter of the stator 22 in this embodiment is 110 mm; the outer diameter of the eccentric section 312 is 16 mm; the outer diameter of the first section 311 is 13 mm; and the outer diameter of the second section 313 is 11 mm. Thus, D / D1 = 6.9, D1 / D2 = 1.23, D1 / D3 = 1.5, D2 < D1, and D3 < D1.

[0069] Comparative Example 1

[0070] The compressor of the comparative example 1 is different from the compressor of the embodiment 1 in that the outer diameter of the stator 22 in this embodiment is 80 mm; the outer diameter of the eccentric section 312 is 20 mm; the outer diameter of the first section 311 is 17 mm; and the outer diameter of the second section 313 is 15 mm. Thus, D / D1 = 4, D1 / D2 = 1.18, D1 / D3 = 1.33, D2 < D1, and D3 < D1.

[0071] Comparative Example 2

[0072] The compressor is different from the compressor of the embodiment 1 in that the outer diameter of the stator 22 in this embodiment is 121 mm; the outer diameter of the eccentric section 312 is 16 mm; the outer diameter of the first section 311 is 18 mm; and the outer diameter of the second section 313 is 12 mm. Thus, D / D1 = 7.56, D1 / D2 = 0.89, D1 / D3 = 1.33, D2 > D1, and D3 < D1.

[0073] Comparative Example 3

[0074] The compressor is different from the compressor of the embodiment 1 in that the outer diameter of the stator 22 in this embodiment is 133 mm; the outer diameter of the eccentric section 312 is 18 mm; the outer diameter of the first section 311 is 16 mm; and the outer diameter of the second section 313 is 14 mm. Thus, D / D1 = 7.39, D1 / D2 = 1.13, D1 / D3 = 1.29, D2 < D1, and D3 < D1.

[0075] Table 1 Reliability test of crankshaft

[0076]

[0077] As shown in Table 1, the outer diameter of each shaft section of the crankshaft 31 of the compressor of the present application and the outer diameter of the stator 22 satisfy the following relationships: 5.0≤D / D1≤7.0, 1.05≤D1 / D2≤1.45, 1.25≤D1 / D3≤1.65, D1≥D2, D1≥D3 and D≤114mm. In this way, the geometric center of the eccentric section 312 and the meshing part of the scroll gears of the dynamic scroll plate 33 and the static scroll plate 32 are at the same height, so that the overturning moment of the dynamic scroll plate 33 is greatly reduced, the dynamic scroll plate 33 is not easy to overturn, the noise and vibration of the compressor are reduced to a certain extent, at the same time, the eccentric section 312 is not severely worn due to the overturning of the dynamic scroll plate 33, the reliability of the scroll compressor is improved, and the miniaturization design of the scroll compressor is facilitated.

[0078] In summary, the compressor of the present application has the following advantages:

[0079] (1) The present application sets the proportional relationship between the outer diameter of each shaft section of the crankshaft and the outer diameter of the stator, which can ensure that the geometric center of the eccentric section and the meshing part of the scroll gears of the dynamic scroll plate and the static scroll plate are at the same height, so that the overturning moment of the dynamic scroll plate is greatly reduced, the dynamic scroll plate is not easy to overturn, the noise and vibration of the compressor are reduced to a certain extent, at the same time, the eccentric section is not severely worn due to the overturning of the dynamic scroll plate, the reliability of the scroll compressor is improved, and the miniaturization design of the scroll compressor is facilitated;

[0080] (2) The pump body assembly of the compressor of the present application is arranged on the side of the compressor close to the oil pool, and the motor is arranged on the side of the compressor away from the oil pool, the pump body assembly is in contact with the oil pool, which can shorten the oiling time when the compressor starts and improve the lubrication effect of the pump body assembly;

[0081] (3) The crankshaft of the present application penetrates the static scroll plate, the dynamic scroll plate and the bracket, and the dynamic scroll plate is not easy to overturn when rotating, which can reduce the vibration and noise of the compressor during operation;

[0082] (4) The static scroll plate of the present application is on the side of the dynamic scroll plate away from the oil pool, the exhaust passage is smoother, and the energy efficiency of the compressor is improved.

[0083] On the other hand, the present application also provides a refrigeration system, which comprises the compressor described above, so that the refrigeration system comprises all the technical effects of the compressor described above. Since the technical effects of the compressor have been described in detail in the foregoing, they will not be described here again.

[0084] For purposes of the description hereinafter, the terms "upper", "lower", "right", "left", "rear", "front", "vertical" and "horizontal" as can be perceived herein relative to the accompanying drawings refer to the orientation of the components being described. However, it is to be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device described herein relative to the other device or structure is inverted, then a spatially relative term such as "above" can be interpreted as meaning "below" or "below" can be interpreted as meaning "above". The device can also be oriented in other ways (rotated at 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly. The devices can be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

[0085] In addition, it should be pointed out that the use of "first", "second" and the like words to qualify parts, is only for the convenience of distinguishing the corresponding parts, and the above words have no special meaning unless otherwise stated, and therefore cannot be understood as limiting the scope of protection of the present application.

[0086] The preferred embodiments of the present application have been described above with the purpose of enabling not to limit the scope of protection of the present application, but of enabling a person skilled in the art to make various modifications and changes to the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A compressor characterized by, The application relates to a scroll compressor, comprising: a casing (10) having a receiving cavity (101); a motor (20) arranged in the receiving cavity (101), the motor (20) comprising a rotor (21) and a stator (22) sleeved on the outer periphery of the rotor (21); a pump body assembly (30) arranged in the receiving cavity (101), the pump body assembly (30) comprising a crankshaft (31), a static scroll (32), a dynamic scroll (33) and a bracket (34), the crankshaft (31) sequentially penetrating through the bracket (34), the dynamic scroll (33), the static scroll (32) and the motor (20), the crankshaft (31) comprising an eccentric section (312), and the dynamic scroll (33) being sleeved on the eccentric section (312); wherein the outer diameter D of the stator (22) and the outer diameter D1 of the eccentric section (312) satisfy the relationship 5<=D / D1<=7.

2. The compressor of claim 1, wherein, The crankshaft (31) further comprises a first section (311), the first section (311) and the eccentric section (312) being sequentially arranged along the axial direction of the crankshaft (31), and the static scroll (32) being sleeved on one end of the first section (311) close to the eccentric section (312); wherein the outer diameter D2 of the first section (311) and the outer diameter D1 of the eccentric section (312) satisfy the relationship 1.05<=D1 / D2<=1.

45.

3. The compressor of claim 2, wherein, The outer diameter D1 of the eccentric section (312) and the outer diameter D2 of the first section (311) satisfy the relationship D2<=D1.

4. The compressor of claim 2, wherein, The crankshaft (31) further comprises a second section (313), the first section (311), the eccentric section (312) and the second section (313) being sequentially arranged along the axial direction of the crankshaft (31), and the bracket (34) being sleeved on one end of the second section (313) close to the eccentric section (312); wherein the outer diameter D3 of the second section (313) and the outer diameter D1 of the eccentric section (312) satisfy the relationship 1.25<=D1 / D3<=1.

65.

5. The compressor of claim 4, wherein, The outer diameter D1 of the eccentric section (312) and the outer diameter D3 of the second section (313) satisfy the relationship D3<=D1.

6. The compressor of any one of claims 1 to 5, wherein, The outer diameter D of the stator (22) satisfies the relationship D<=114mm.

7. The compressor of any one of claims 1 to 5, wherein, The dynamic scroll (33) comprises a gray cast iron dynamic scroll or a cast iron dynamic scroll with a tensile strength greater than 250Mpa; and / or, The static scroll (32) comprises a gray cast iron static scroll or a cast iron static scroll with a tensile strength greater than 250Mpa; and / or, The bracket (34) comprises a gray cast iron bracket or a cast iron bracket with a tensile strength greater than 250Mpa; and / or, the crankshaft (31) comprises a nodular cast iron crankshaft or a cast iron crankshaft with a tensile strength greater than 600Mpa; and / or, the crankshaft (31) comprises a 20Cr steel crankshaft or a 40Cr steel crankshaft.

8. The compressor of any one of claims 1 to 5, wherein, An oil supply passage (40) is provided on the crankshaft (31) and extends from the end of the second section (313) of the crankshaft (31) toward the first section (311) of the crankshaft (31).

9. The compressor of claim 1, wherein, The compressor can be a vertical compressor or a horizontal compressor.

10. A refrigeration system characterized by, The refrigeration system can include the compressor of any one of claims 1 to 9.

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