Compressor

Abstract

The utility model discloses a compressor. The compressor comprises a motor and a compression mechanism. A plurality of circulation holes are formed in the rotor in a penetrating mode in the axial direction of the rotor, and the total area of the sections of the circulation holes is S1 in the radial direction of the rotor. The crankshaft is connected with the rotor, the first bearing comprises a base plate and a shaft handle, the base plate is connected with the air cylinder, the shaft handle is arranged on the side, away from the air cylinder, of the base plate in a protruding mode, and the end, away from the rotor, of the crankshaft penetrates through the first bearing and is arranged in the air cylinder in a sleeved mode. The silencer covers the base plate in a buckled mode, at least part of the shaft handle is arranged between the silencer and the motor in a penetrating mode along the exhaust hole, an exhaust gap exists between the inner wall face of the exhaust hole and the outer wall face of the shaft handle in the radial direction of the crankshaft, the sectional area of the exhaust gap is S2 in the radial direction of the crankshaft, and the ratio of S1 to S2 is not smaller than 4.5. The problems that when the flow speed of the compressor is increased, the oil discharge amount is large, and when the flow speed is small, the exhaust efficiency is low are solved.

Description

TECHNICAL FIELD

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

[0002] The high-pressure gas compressed by the pump body of the compressor is usually discharged through the exhaust hole of the upper bearing muffler, then enters the cavity between the motor of the compressor and the upper bearing muffler, passes through the flow-through hole of the motor rotor, and is finally discharged from the exhaust pipe of the compressor.

[0003] However, when the flow rate of the high-pressure gas is too high, the high-pressure gas will carry a large amount of lubricating oil. A large amount of lubricating oil is taken out of the exhaust pipe together with the high-pressure gas, which increases the oil discharge of the compressor and also weakens the lubricating effect of the lubricating oil on the internal components of the compressor, thereby reducing the operating efficiency of the compressor. When the flow rate of the high-pressure gas is too low, the flow resistance loss of the gas is too large, which also affects the operating efficiency of the compressor. Therefore, the existing compressor has a large oil discharge when the flow rate is improved. CONTENT OF THE UTILITY MODEL

[0004] The main purpose of the present application is to provide a compressor to solve the problem of large oil discharge when the flow rate of the compressor is improved.

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

[0006] A motor comprising a stator and a rotor sleeved in the stator, along the axial direction of the rotor, a plurality of flow-through holes are provided through the rotor, and along the radial direction of the rotor, the total cross-sectional area of the plurality of flow-through holes is S1.

[0007] A compression mechanism comprising a crankshaft, a cylinder, a first bearing and a muffler, the crankshaft is connected with the rotor, the first bearing comprises a bottom plate and a shaft handle, the bottom plate is connected with the cylinder, and an exhaust structure is arranged on the bottom plate and communicates with the cylinder, the exhaust structure is used for discharging gas in the cylinder, the shaft handle is protruded from the side of the bottom plate away from the cylinder, one end of the crankshaft away from the rotor penetrates through the first bearing and is sleeved in the cylinder, the muffler is provided with an exhaust hole, the muffler is installed on the bottom plate and covers the exhaust structure, and the shaft handle is at least partially arranged along the exhaust hole between the muffler and the motor, along the radial direction of the crankshaft, there is an exhaust gap between the inner wall surface of the exhaust hole and the outer wall surface of the shaft handle, along the radial direction of the crankshaft, the cross-sectional area of the exhaust gap is S2, and the ratio between S1 and S2 is not less than 4.5.

[0008] Further, the ratio between S1 and S2 is not greater than 5.5.

[0009] Further, the size of the S1 is not less than 180 square millimeters.

[0010] Further, the flow-through holes include a plurality of flow-through holes, and the plurality of flow-through holes are arranged along the circumference of the rotor; and / or, along the axial direction of the rotor, the distance between the end face of the side of the rotor close to the muffler and the end point of the top end of the side of the muffler close to the rotor is L1, and 18 mm≤L1≤20 mm.

[0011] Further, the compressor further comprises a first balance block and a second balance block, and along the axial direction of the rotor, the first balance block and the second balance block are arranged at opposite ends of the rotor respectively, the first balance block is located away from the compression mechanism, the second balance block is located close to the compression mechanism, along the axial direction of the rotor, the projection outer contour of the first balance block is offset from the projection outer contour of the second balance block along the radial direction of the rotor, and along the radial direction of the rotor, the first balance block and the second balance block are located between the flow-through hole and the outer edge of the rotor.

[0012] Further, along the axial direction of the rotor, the projection outer contour of the side of the flow-through hole close to the first balance block overlaps with the projection outer contour of the side of the first balance block close to the flow-through hole; and / or,

[0013] Further, along the axial direction of the rotor, the projection outer contour of the side of the flow-through hole close to the second balance block overlaps with the projection outer contour of the side of the second balance block close to the flow-through hole.

[0014] Further, the first balance block and the second balance block are both arc-shaped block structures, and along the radial direction of the rotor, the outer diameter of the first balance block is L2, and 50 mm≤L2≤60 mm.

[0015] Further, along the radial direction of the rotor, the outer diameter of the second balance block is L3, and 50 mm≤L3≤60 mm.

[0016] Further, along the axial direction of the stator, the height of the first balance block is H1, and the height of the second balance block is H2, and 5 mm≤H1≤10 mm, and 12 mm≤H2≤16 mm.

[0017] Further, the compressor further comprises:

[0018] a shell, an installation cavity is arranged in the shell, the motor and the compression mechanism are installed in the installation cavity, and along the axial direction of the rotor, a gas outlet channel is arranged at the top of the shell, and the gas outlet channel communicates with the installation cavity.

[0019] The maximum width of the shell along the radial direction of the rotor is R, and 89mm≤R≤108mm.

[0020] Further, the distance between the end face of the stator away from the muffler and the inner wall surface of the shell along the axial direction of the rotor is L4, and 60mm≤L4≤90mm.

[0021] Further, the compressor further comprises:

[0022] An exhaust pipe is provided with the gas outlet channel along the axial direction of the rotor, and the exhaust pipe is at least partially arranged in the mounting cavity;

[0023] The length of the exhaust pipe in the mounting cavity is L5, and 5mm≤L5≤30mm; and / or the exhaust volume of the exhaust pipe per unit time is Q, and 5cm 3 ≤Q≤25cm 3 .

[0024] In the present application, by reasonably setting the cross-sectional area S1 of the flow-through hole on the rotor and the cross-sectional area S2 of the exhaust gap, and ensuring that the ratio between S1 and S2 is not less than 4.5, the flow rate of high-pressure gas can be effectively regulated. When the ratio between S1 and S2 is not less than 4.5, the compressor can effectively reduce the situation of entraining a large amount of lubricating oil due to the excessively high flow rate of high-pressure gas, thereby reducing the oil discharge of the compressor, ensuring that the lubricating oil can better remain in the lubricating pipeline inside the compressor, ensuring that the internal components of the compressor have good lubrication effect, ensuring that each component of the compressor can operate stably, and prolonging the service life of the compressor. In addition, the present application can also slow down the situation of lubricating oil adhering to the outside of the compressor, can improve the heat exchange efficiency of the compressor refrigeration system, and is conducive to improving the exhaust efficiency of the compressor. BRIEF DESCRIPTION OF DRAWINGS

[0025] The drawings described herein are used to provide further understanding of the present application, and form a part of the present application. The schematic embodiments of the present application and their descriptions are used to explain the present application, and do not constitute an improper limitation on the present application. In the drawings:

[0026] Figure 1 is a sectional view of the compressor disclosed in the present application;

[0027] Figure 2 is a sectional view of the compressor disclosed in the present application;

[0028] Figure 3 is a top view of the flow-through hole disclosed in the present application;

[0029] Figure 4 is a top view of the exhaust hole disclosed in the present application;

[0030] Figure 5 A graph of the relationship between the efficiency of the compressor disclosed in the present application and S1 / S2;

[0031] Figure 6 A graph of the relationship between the oil discharge rate of the compressor disclosed in the present application and S1 / S2;

[0032] Figure 7 A graph of the efficiency data of the compressor when the ratio of S1 to S2 is 4.98.

[0033] Among the above-mentioned drawings, the following reference signs are included:

[0034] 10, motor; 11, stator; 12, rotor; 121, flow-through hole; 20, compressor mechanism; 21, crankshaft; 22, cylinder; 23, first bearing; 231, base plate; 232, shaft handle; 24, muffler; 241, exhaust hole; 31, first balance weight; 32, second balance weight; 40, housing; 41, mounting cavity; 42, exhaust pipe; 421, gas outlet passage. DETAILED DESCRIPTION

[0035] 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 drawings and in combination with the embodiments.

[0036] It should be noted that the terms used herein are only intended to describe specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should also be understood that, when the terms "comprise" and / or "include" are used in the specification, there is a presence of the features, steps, operations, devices, components and / or combinations thereof.

[0037] The relative arrangement, numerical expressions and numerical values of the components and steps set forth in these embodiments do not limit the scope of the present application unless otherwise specifically stated. At the same time, it should be understood that the sizes of the various parts shown in the drawings are not drawn in proportion to the actual proportions. Techniques, methods and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered as part of the authorized specification, if appropriate. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference numbers and letters represent similar items in the following drawings, and therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0038] As Figures 1 to 7 shown, the application provides a compressor. The compressor comprises a motor 10 and a compression mechanism 20. The motor 10 comprises a stator 11 and a rotor 12. The rotor 12 is sleeved in the stator 11, and a plurality of flow-through holes 121 are arranged through the rotor 12 in the axial direction of the rotor 12. In the radial direction of the rotor 12, the total cross-sectional area of the plurality of flow-through holes 121 is S1. The compression mechanism 20 comprises a crankshaft 21, a cylinder 22, a first bearing 23, and a muffler 24. The crankshaft 21 is connected to the rotor 12. The first bearing 23 comprises a bottom plate 231 and a shaft handle 232. The bottom plate 231 is connected to the cylinder 22, and the bottom plate 231 is provided with an exhaust structure communicating with the cylinder 22. The exhaust structure is used for exhausting gas in the cylinder 22. The shaft handle 232 is protruded on the side of the bottom plate 231 away from the cylinder 22. One end of the crankshaft 21 away from the rotor 12 penetrates through the first bearing 23 and is sleeved in the cylinder 22.

[0039] The muffler 24 is provided with an exhaust hole 241. The muffler 24 is mounted on the bottom plate 231 and covers the exhaust structure. The shaft handle 232 is at least partially arranged through the exhaust hole 241 between the muffler 24 and the motor 10. In the radial direction of the crankshaft 21, there is an exhaust gap between the inner wall surface of the exhaust hole 241 and the outer wall surface of the shaft handle 232. In the radial direction of the crankshaft 21, the cross-sectional area of the exhaust gap is S2. The ratio between S1 and S2 is not less than 4.5.

[0040] In the embodiment, by reasonably setting the cross-sectional area S1 of the flow-through hole 121 on the rotor 12 and the cross-sectional area S2 of the exhaust gap, and ensuring that the ratio between S1 and S2 is not less than 4.5, the flow rate of the high-pressure gas can be effectively regulated. For example, the ratio between S1 and S2 can be selected as one of 4.5, 4.6, 4.7, 4.8, 4.9, 5.0, 5.1, 5.2, 5.3, 5.4, or 5.5. When the ratio between S1 and S2 is not less than 4.5, the compressor can effectively reduce the situation that a large amount of lubricating oil is entrained due to the excessively high flow rate of the high-pressure gas, thereby reducing the oil discharge amount of the compressor. The oil discharge amount of the compressor is the amount of lubricating oil discharged together with the high-pressure gas when the compressor is working. The embodiment can ensure that the lubricating oil can better remain in the lubricating pipeline inside the compressor, ensure that the internal components of the compressor have good lubrication effect, ensure that the components of the compressor can stably operate, and can prolong the service life of the compressor. If the ratio between S1 and S2 is less than 4.5, the flow rate of the high-pressure gas is relatively large, and the high-pressure gas will entrain more lubricating oil, and a large amount of lubricating oil will be discharged together with the high-pressure gas, which will result in a large oil discharge amount of the compressor. Such a setting can reduce the amount of lubricating oil inside the compressor, affect the lubrication effect of the lubricating oil on the internal components of the compressor, increase the wear between the components, and reduce the reliability and stability of the compressor. In addition, the compressor can also slow down the situation that the lubricating oil adheres to the outside of the compressor, and can improve the heat exchange efficiency of the refrigeration system. The compressor further includes a piston, the piston is sleeved on the outer periphery of the eccentric portion of the crankshaft, the rotation of the crankshaft 21 drives the rotation of the piston, the piston rotates in the cylinder, and the low-pressure refrigerant gas entering the cylinder is compressed, the compressed high-pressure gas enters the exhaust passage of the first bearing 23 from the exhaust cutout on the upper end surface of the cylinder, and then enters the muffler 24 through the exhaust valve piece, and then is discharged from the exhaust hole 241 of the muffler 24. After the high-pressure gas is discharged from the exhaust hole 241 of the muffler 24, the entire compressor is filled with high-pressure gas.

[0041] Further, the ratio between S1 and S2 is not greater than 5.5. For example, the ratio between S1 and S2 can be selected as one of 5.5, 5.4, 5.3, 5.2, 5.1, 5.0, 4.9, 4.8, 4.7, 4.6, 4.5, etc. When the ratio between S1 and S2 is not greater than 5.5, the ratio between S1 and S2 is within a reasonable range, in which the flow rate of the high-pressure gas is within an acceptable range, and the oil discharge amount of the compressor is not too high, so that the flow rate of the high-pressure gas can be ensured to be not too low, the high-pressure gas can be ensured to have a small resistance, the flow resistance loss of the high-pressure gas is effectively reduced, and the exhaust efficiency of the high-pressure gas is improved, and the oil discharge amount of the compressor can be ensured to be not too high, and there is enough lubricating oil in the compressor to maintain the lubrication of the components in the compressor. In this way, the exhaust efficiency of the compressor can be relatively high, and the problems of increased energy loss and reduced exhaust efficiency caused by too low flow rate of the high-pressure gas can be effectively avoided. If the ratio between S1 and S2 is greater than 5.5, the cross-sectional area of the exhaust gap relative to the flow hole 121 of the rotor 12 is too small, which can cause the flow rate of the high-pressure gas to be too slow, the flow resistance loss of the high-pressure gas can be significantly increased, the exhaust efficiency of the compressor can be reduced, and the output power of the compressor can be affected, so that the compressor cannot efficiently complete the gas compression and exhaust work.

[0042] When the ratio between S1 and S2 is between 4.5 and 5.5, for example, the ratio between S1 and S2 is selected as one of 4.5, 4.6, 4.7, 4.8, 4.9, 5.0, 5.1, 5.2, 5.3, 5.4, 5.5, etc., the flow rate of the high-pressure gas is improved, the flow rate loss of the high-pressure gas is small, and the oil discharge amount of the compressor is within an acceptable range, and the increase in the oil discharge amount of the compressor is small. When the high-pressure gas flows through the inside of the compressor, a large amount of lubricating oil is not wrapped due to too fast flow rate, so that there is enough lubricating oil in the compressor for lubricating each moving part, the wear of the parts caused by insufficient lubricating oil is reduced, and the service life of the compressor is prolonged. At the same time, when the ratio between S1 and S2 is between 4.5 and 5.5, the high-pressure gas flows smoothly in the compressor, so that the flow resistance loss of the high-pressure gas is small when the high-pressure gas is discharged from the exhaust hole 241 of the muffler 24, and the compressor can more effectively complete the gas compression and exhaust work.

[0043] Further, the size of S1 is not less than 180 square millimeters. For example, S1 can adopt one of 180 square millimeters, 185 square millimeters, 190 square millimeters, 195 square millimeters, 200 square millimeters, etc. The flow-through hole 121 of the rotor 12 has a relatively large area, which provides a wide passage for the high-pressure gas to pass through. During the operation of the compressor, the flow-through hole 121 can ensure that enough high-pressure gas can quickly pass through the flow-through hole 121 and then be discharged from the compressor. If the size of S1 is less than 180 square millimeters, the flow-through hole 121 of the rotor 12 is too small, which will limit the passing amount of high-pressure gas and then limit the discharge amount of high-pressure gas. In addition, if the flow-through hole 121 is too small, it will also cause the flow rate of high-pressure gas to be too fast. The high flow rate of gas in the oil pool environment will cause a large amount of lubricating oil to be taken away by the high-pressure gas, which will increase the oil discharge amount of the compressor and also aggravate the wear between the components inside the compressor body.

[0044] Further, the flow-through hole 121 includes a plurality of flow-through holes 121, and the plurality of flow-through holes 121 are arranged at intervals in the circumferential direction of the rotor 12. When the flow-through hole 121 is arranged at intervals in the circumferential direction of the rotor 12, the high-pressure gas can uniformly enter the inside of the rotor 12 from multiple directions, which increases the passing area of the high-pressure gas and improves the efficiency of the high-pressure gas passing through the rotor 12. During the operation of the compressor, the flow rate of the high-pressure gas inside the rotor 12 is more stable and uniform, which is beneficial to the discharge of the high-pressure gas and reduces the flow resistance loss caused by the non-uniform flow rate.

[0045] Among them, the interval between each two adjacent flow-through holes 121 is equal. The high-pressure gas can pass through the flow-through hole 121 more uniformly, which can ensure that the flow rate of the high-pressure gas in each flow-through hole 121 is the same and ensure the stability of the compressor. In addition, uniform gas flow and stable internal pressure also help to reduce the vibration and noise of the compressor.

[0046] Further, the distance between the end face of the rotor 12 close to the muffler 24 and the top end of the muffler 24 close to the rotor 12 is L1, and 18mm≤L1≤20mm. For example, L1 can be selected as one of 18mm, 18.5mm, 19mm, 19.5mm, 20mm, etc. Such a setting can provide a suitable flow path for the high-pressure gas flowing from the muffler 24 to the cavity between the rotor 12. Within this range, the high-pressure gas will not produce excessive diffusion and energy loss during the flow process due to the excessive distance between the rotor 12 and the muffler 24. In addition, the flow resistance of the high-pressure gas can be reduced, ensuring that the high-pressure gas can smoothly flow from the muffler 24 to the flow-through hole 121 inside the compressor, which helps to improve the exhaust efficiency of the compressor. If the size of L1 is less than 18mm, the distance between the stator 11 and the muffler 24 is too small, and the flow space between the high-pressure gas flowing from the muffler 24 to the flow-through hole 121 is too narrow. The high-pressure gas is easily subjected to a large flow resistance, which can cause uneven distribution of the flow rate of the high-pressure gas, and the local flow rate can be too high or too low, increasing the energy consumption of the high-pressure gas and thus reducing the exhaust efficiency of the compressor. In addition, the small distance between the stator 11 and the muffler 24 can also affect the heat exchange efficiency of the high-pressure gas, and the residence time of the high-pressure gas is too short to fully remove the heat in the compressor. If the size of L1 is greater than 20mm, the distance between the stator 11 and the muffler 24 is too large, which can cause the flow path of the high-pressure gas to be too long when flowing from the muffler 24 to the motor 10. The high-pressure gas is prone to diffusion and no longer maintains a compact flow state, which can reduce the flow rate of the high-pressure gas and thus reduce the exhaust efficiency of the compressor.

[0047] Further, the compressor further comprises a first balance block 31 and a second balance block 32. Along the axial direction of the rotor 12, the first balance block 31 and the second balance block 32 are respectively arranged at opposite ends of the rotor 12, the first balance block 31 is located at the end of the rotor 12 away from the compression mechanism 20, and the second balance block 32 is located at the end of the rotor 12 close to the compression mechanism 20. Along the radial direction of the rotor 12, the projection contour of the first balance block 31 and the projection contour of the second balance block 32 are located at different positions along the radial direction of the rotor 12, and the first balance block 31 and the second balance block 32 are located between the flow-through hole 121 and the outer edge of the rotor 12. The first balance block 31 and the second balance block 32 can effectively improve the dynamic balance of the rotor 12, can offset the unbalanced force generated by the rotor 12 during rotation, can balance the centrifugal force of the rotor 12 in each direction during rotation, and can further reduce the vibration and noise during operation of the motor 10. When the rotor 12 is well balanced, the movement of the crankshaft 21 and other components driven by the rotor 12 is also more stable, so that the gas in the cylinder 22 can be compressed at a more stable speed and stroke, the stable rise of the pressure of the gas during compression can be ensured, and the compressor can operate at a higher efficiency.

[0048] Further, along the axial direction of the rotor 12, the projected outer contour of the flow-through hole 121 on the side close to the first balance block 31 overlaps with the projected outer contour of the first balance block 31 on the side close to the flow-through hole 121.

[0049] Further, along the axial direction of the rotor 12, the projected outer contour of the flow-through hole 121 on the side close to the second balance block 32 overlaps with the projected outer contour of the second balance block 32 on the side close to the flow-through hole 121. Such arrangement effectively prevents the first balance block 31 and the second balance block 32 from occupying extra space, reduces the disturbance effect of the first balance block 31 and the second balance block 32 on the refrigerant gas inside the compressor, further guarantees the balance of the high-pressure gas, and is conducive to improving the exhaust efficiency of the high-pressure gas.

[0050] Further, the first balance block 31 and the second balance block 32 are both arc-shaped block structures, and along the radial direction of the rotor 12, the outer diameter of the first balance block 31 is L2, 50mm≤L2≤60mm.

[0051] Further, along the radial direction of the rotor 12, the outer diameter of the second balance block 32 is L3, 50mm≤L3≤60mm.

[0052] The first balance block 31 and the second balance block 32 adopt an arc block structure, wherein the inner wall surface of the side of the first balance block 31 and the second balance block 32 close to the flow-through hole 121 is an arc surface, and the inner diameter of the arc surface is the same as the inner diameter of the first balance block 31 and the inner diameter of the second balance block 32. This shape design can better fit the circumferential shape of the rotor 12 and more effectively play a balancing role during the rotation of the rotor 12. When the balance block is arc-shaped, the mass distribution can more evenly adjust the unbalanced force of the rotor 12 along the circumferential direction. L2 can be one of 50 mm, 51 mm, 52 mm, 53 mm, 54 mm, 55 mm, 56 mm, 57 mm, 58 mm, 59 mm, 60 mm, etc. The distance range of 50 mm≤L2≤60 mm makes the positions of the first balance block 31 and the second balance block 32 in the radial direction of the rotor 12 effectively balance the centrifugal force generated by the interaction of the structure of the rotor 12 itself, gas flow, and other components, so that the first balance block 31 and the second balance block 32 can generate appropriate torque to offset the unbalanced force, so that the rotor 12 can remain stable during high-speed rotation, reduce vibration and noise, and improve the overall operation stability of the compressor. If L2 or L3 is less than 50 mm, the distance between the outer edge of the side of the first balance block 31 and the second balance block 32 away from the flow-through hole 121 and the axis of the stator 11 is too close. During the operation of the compressor, the rotor 12 rotates at high speed, and the first balance block 31 and the second balance block 32 also rotate with it. The first balance block 31 and the second balance block 32 may not be able to generate enough torque to offset the unbalanced force of the rotor 12, affecting the normal operation of the compressor. If L2 or L3 is greater than 60 mm, the volume of the first balance block 31 and the second balance block 32 is too large, which will interfere with the stator 11, affect the normal operation of the motor 10, and also disturb the refrigerant gas in the compressor, affecting the flow rate and flow path of the high-pressure gas, and thus affecting the stability of the motor 10.

[0053] Further, along the axial direction of the stator 11, the height of the first balance block 31 is H1, and the height of the second balance block 32 is H2, 5mm≤H1≤10mm, and 12mm≤H2≤16mm. For example, H1 can be selected as one of 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, etc. H2 can be selected as one of 12mm, 13mm, 14mm, 15mm, 16mm, etc. The first balance block 31 and the second balance block 32 can provide precise balancing effect in the axial direction of the rotor 12, guarantee the good stability of the motor 10, reduce the axial vibration of the motor 10, and thus improve the working efficiency of the compressor. If H1<5mm or H2<12mm, the height of the first balance block 31 and the second balance block 32 is too small, and the first balance block 31 and the second balance block 32 are difficult to generate enough force to offset the unbalanced force of the rotor 12. If H1>10mm or H2>16mm, the height of the first balance block 31 and the second balance block 32 is too large, which occupies more installation space, and is not convenient for the motor 10 to be installed in the compressor.

[0054] The compressor further comprises a housing 40. The housing 40 is provided with a mounting cavity 41, and the motor 10 and the compression mechanism 20 are installed in the mounting cavity 41. Along the axial direction of the rotor 12, the top of the housing 40 is provided with an air outlet passage 421, and the air outlet passage 421 is in communication with the mounting cavity 41. When the top of the housing 40 is provided with the air outlet passage 421 in communication with the flow-through hole 121, this design provides a direct and efficient discharge path for high-pressure gas. The compressed high-pressure gas can smoothly enter the air outlet passage 421 through the flow-through hole 121. The housing 40 can also protect the motor 10 and the compression mechanism 20, and can protect the motor 10 and the compression mechanism 20 from damage caused by the external environment, and guarantee the stable operation of the motor 10 and the compression mechanism 20 in a relatively stable environment.

[0055] The maximum width of the shell 40 along the radial direction of the rotor 12 is R, and 89mm≤R≤108mm. For example, R can be selected as one of 89mm, 90mm, 91mm, 92mm, 93mm, 94mm, 95mm, 96mm, 97mm, 98mm, 99mm, 100mm, 101mm, 102mm, 103mm, 104mm, 105mm, 106mm, 107mm, and 108mm. Within this width range, the shell 40 can provide sufficient support and protection against vibration, pressure changes, and other conditions that occur during operation of the compressor, and also facilitates installation of the motor 10 and the compression mechanism 20 in the installation cavity 41. In addition, the compressor of the present application also takes into account the trend of smaller size and higher rotational speed, which can save production costs and improve the product upgrade trend of energy efficiency. If R is less than 89mm, the size of the shell 40 is too small, and the shell 40 cannot provide sufficient support and protection for the motor 10 and the compression mechanism 20. If R is greater than 108mm, the size of the shell 40 is too large, which is not conducive to the miniaturization trend of the compressor.

[0056] Further, along the axial direction of the rotor 12, the spacing between the end surface of the stator 11 away from the muffler 24 and the inner wall surface of the shell 40 is L4, and 60mm≤L4≤90mm. For example, L4 can be selected as one of 60mm, 65mm, 70mm, 75mm, 80mm, 85mm, and 90mm. In this way, the refrigerant gas can flow freely in the space between the stator 11 and the inner wall of the shell 40, effectively removing the heat generated by the stator 11. This helps to maintain the temperature of the stator 11 within a reasonable range, avoiding overheating that affects the performance of the motor 10, thereby improving the overall reliability and performance of the compressor. The present embodiment also provides convenience for the installation and layout of other components inside the compressor. In this area, auxiliary components such as wires, sensors, cooling devices, etc. can be reasonably arranged. For example, for some wires that need to be connected to the stator 11, this space can provide sufficient space for wiring. If L4 is less than 60mm, the space between the motor 10 and the shell 40 is small, which is not convenient for motor 10 installation operations. If L4 is greater than 90mm, the space between the motor 10 and the shell 40 is large, which will result in a decrease in the flow rate of high-pressure refrigerant gas, and the high-pressure refrigerant gas cannot be smoothly discharged from the shell 40.

[0057] Further, the compressor further comprises an exhaust pipe 42. An exhaust passage 421 is arranged in the exhaust pipe 42 along the axial direction of the rotor 12. The exhaust pipe 42 is at least partially arranged in the mounting cavity 41, and the length of the exhaust pipe 42 arranged in the mounting cavity 41 is L5, 5mm≤L5≤30mm. For example, L5 can be one of 5mm, 10mm, 15mm, 20mm, 25mm, 30mm, etc. In this way, the high-pressure gas in the compressor can be more smoothly transitioned into the exhaust pipe 42, and the energy loss and pressure fluctuation of the gas when entering the exhaust pipe 42 from the compressor can be reduced. If L5 is less than 5mm, the length of the exhaust pipe 42 arranged in the mounting cavity 41 is too short, which can cause the gas to be not smoothly transitioned when entering the exhaust pipe 42 from the compressor. Due to the short transition area, the gas can easily generate large pressure fluctuation and energy loss, which can reduce the exhaust efficiency of the compressor. If L5 is greater than 30mm, the length of the exhaust pipe 42 arranged in the mounting cavity 41 is too long, which can occupy too much space in the mounting cavity 41 and also hinder the flow path of the gas in the mounting cavity 41, causing the gas flow to generate vortex or local resistance increase.

[0058] Further, the exhaust amount of the exhaust pipe 42 per unit time is Q, 5cm 3 ≤Q≤25cm 3 . For example, Q can be one of 5cm 3 , 10cm 3 , 15cm 3 , 20cm 3 , 25cm 3 , etc. When the exhaust amount Q of the exhaust pipe 42 per unit time is within the range, the ratio between S1 and S2 is not less than 4.5 and not greater than 5.5, which can ensure that the high-pressure gas of the compressor has a high flow rate, the flow resistance of the high-pressure gas is small, the oil discharge amount is within an acceptable range, and the compressor has a high exhaust efficiency.

[0059] Specifically, as shown in Figures 5 to 6 , when the exhaust amount Q of the exhaust pipe 42 per unit time is 9.8cm 3 , S1≥180 square centimeters, it is obtained that the ratio between S1 and S2 is not less than 4.5 and not greater than 5.5, which can make the energy consumption of the compressor better and the oil discharge amount of the compressor lower, and the energy consumption and the oil discharge rate when the ratio between S1 and S2 is less than 4.5 and when the ratio between S1 and S2 is greater than 5.5 are relatively large.

[0060] As shown in Figure 7 , the curve Figure 7 represents that when the exhaust amount Q of the exhaust pipe 42 per unit time is 14cm 3When the working conditions of the compressor are 30Hz, 60Hz, 90Hz, 120Hz, 140Hz and APF working conditions respectively, the energy efficiency data of the ratio between S1 and S2 is 3.44 and 4.98 respectively. It can be seen that under the condition of the same exhaust volume, the energy efficiency of S1 / S2=4.95 is better than that of S1 / S2=3.44. The compressor can effectively reduce the situation that a large amount of lubricating oil is entrained due to the too high flow rate of high-pressure gas, thereby reducing the oil discharge of the compressor, ensuring that the lubricating oil can be better retained in the lubricating pipeline inside the compressor, ensuring that the internal components of the compressor have good lubrication effect, ensuring that each component of the compressor can stably operate, and can prolong the service life of the compressor. In addition, the present application can also slow down the situation that the lubricating oil adheres to the outside of the compressor, can improve the heat exchange efficiency of the refrigeration system, and is conducive to improving the exhaust efficiency of the compressor.

[0061] For the convenience of description, spatial relative terms such as "above", "upper", "on", "on top of", etc. can be used herein to describe the spatial relationship of one device or feature to another device or feature as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "on" other devices or structures will be positioned "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below" orientations. The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein are interpreted accordingly.

[0062] In addition, it should be noted that the use of "first", "second", and the like to qualify components is merely for the convenience of distinguishing the corresponding components, and the above terms have no special meaning unless otherwise stated, and therefore cannot be understood as limiting the scope of protection of the present application.

[0063] The above is only a preferred embodiment of the present application and is not intended to limit the present application. Those skilled in the art can 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 protection scope of the present application.

Claims

1. A compressor characterized by, The motor (10) comprises a stator (11) and a rotor (12) sleeved in the stator (11), a plurality of flow-through holes (121) are provided through the rotor (12) in the axial direction of the rotor (12), and the total cross-sectional area of the plurality of flow-through holes (121) is S1 in the radial direction of the rotor (12). The compression mechanism (20) comprises a crankshaft (21), a cylinder (22), a first bearing (23), and a muffler (24), the crankshaft (21) is connected with the rotor (12), the first bearing (23) comprises a chassis (231) and a shaft handle (232), the chassis (231) is connected with the cylinder (22), and the chassis (231) is provided with an exhaust structure communicating with the cylinder (22), the exhaust structure is used for exhausting gas in the cylinder (22), the shaft handle (232) is protruded from the side of the chassis (231) away from the cylinder (22), and one end of the crankshaft (21) away from the rotor (12) penetrates through the first bearing (23) and is sleeved in the cylinder (22). The muffler (24) is provided with an exhaust hole (241), the muffler (24) is mounted on the chassis (231) and covers the exhaust structure, and the shaft handle (232) penetrates at least partially through the exhaust hole (241) between the muffler (24) and the motor (10), there is an exhaust gap between the inner wall surface of the exhaust hole (241) and the outer wall surface of the shaft handle (232) in the radial direction of the crankshaft (21), the cross-sectional area of the exhaust gap is S2 in the radial direction of the crankshaft (21), and the ratio between S1 and S2 is not less than 4.

5. The ratio between S1 and S2 is not greater than 5.

5.

2. The compressor of claim 1, wherein, The size of S1 is not less than 180 square millimeters.

3. The compressor of claim 1 or 2, wherein The flow-through holes (121) comprise a plurality of flow-through holes (121) arranged at intervals in the circumferential direction of the rotor (12); and / or, the distance between the end face of the rotor (12) close to the muffler (24) and the top end point of the muffler (24) close to the rotor (12) is L1 in the axial direction of the rotor (12), and 18mm≤L1≤20mm.

4. The compressor of claim 1, wherein, ​ 5. The compressor of claim 1, wherein, The compressor further comprises a first balance block (31) and a second balance block (32) arranged at opposite ends of the rotor (12) in the axial direction of the rotor (12), wherein the first balance block (31) is arranged at the end of the rotor (12) away from the compression mechanism (20), the second balance block (32) is arranged at the end of the rotor (12) close to the compression mechanism (20), the projection outer contour of the first balance block (31) is offset from the projection outer contour of the second balance block (32) in the radial direction of the rotor (12), and the first balance block (31) and the second balance block (32) are both located between the flow-through hole (121) and the outer edge of the rotor (12) in the radial direction of the rotor (12). In the axial direction of the rotor (12), the projection outer contour of the flow-through hole (121) on the side close to the first balance block (31) overlaps the projection outer contour of the first balance block (31) on the side close to the flow-through hole (121); and / or, In the axial direction of the rotor (12), the projection outer contour of the flow-through hole (121) on the side close to the second balance block (32) overlaps the projection outer contour of the second balance block (32) on the side close to the flow-through hole (121).

6. The compressor of claim 5, wherein, The first balance block (31) and the second balance block (32) are both arc-shaped block structures, the outer diameter of the first balance block (31) is L2, and 50mm≤L2≤60mm in the radial direction of the rotor (12); and / or, The outer diameter of the second balance block (32) is L3 in the radial direction of the rotor (12), and 50mm≤L3≤60mm.

7. The compressor of claim 5, wherein, In the axial direction of the stator (11), the height of the first balance block (31) is H1, the height of the second balance block (32) is H2, 5mm≤H1≤10mm, and 12mm≤H2≤16mm.

8. The compressor of claim 1, wherein, The compressor further comprises: A shell (40) provided with a mounting cavity (41) inside, wherein the motor (10) and the compression mechanism (20) are mounted in the mounting cavity (41), and a gas outlet passage (421) is arranged at the top of the shell (40) in the axial direction of the rotor (12), and the gas outlet passage (421) communicates with the mounting cavity (41); In the radial direction of the rotor (12), the maximum width of the shell (40) is R, and 89mm≤R≤108mm.

9. The compressor of claim 8, wherein, In the axial direction of the rotor (12), the distance between the end face of the stator (11) away from the muffler (24) and the inner wall surface of the shell (40) is L4, and 60mm≤L4≤90mm.

10. The compressor of claim 8, wherein, The compressor further comprises: An exhaust pipe (42) provided with the gas outlet passage (421) in the axial direction of the rotor (12), and the exhaust pipe (42) at least partially penetrates into the mounting cavity (41). The length of the exhaust pipe (42) in the installation cavity (41) is L5, 5mm≤L5≤30mm. And / or, the exhaust pipe (42) exhaust volume per unit time is Q, 5cm 3 ≤ Q ≤ 25cm 3 .

Images