Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment, and belongs to the technical field of compressors, the compressor comprises a motor assembly, a pump body assembly, a crankshaft and a silencer, the motor assembly drives the crankshaft to rotate through a stator and a rotor, compressed air is discharged to the silencer through an exhaust port of an air cylinder, and exhaust noise is reduced through a silencing cavity; the crankshaft can penetrate through the first through hole of the cover body and the air outlet of the silencer, and due to the fact that the air outlet and the first through hole are oppositely arranged in the axial direction of the crankshaft, air is exhausted into the cover body through the air outlet and the first through hole, passes through the inner cavity of the cover body and then penetrates through the rotor through the vent hole to be exhausted; due to the fact that gas flows along the silencing cavity, the inner cavity of the cover body and the vent hole in sequence after being exhausted from the air cylinder, disturbance of airflow to a circulating oil way can be effectively reduced, circulating flow of lubricating oil is smoother, stability of oil return and oil spitting is guaranteed, a good lubricating effect is provided for a pump body assembly, and running reliability of the compressor is improved.

Description

Technical Field

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

[0002] In the related art, the rotary compressor supports the crankshaft by adding a support structure, which can effectively reduce the deformation of the crankshaft end and ensure the coaxiality of the stator and rotor in the motor assembly. However, the increase in the support structure and the thickness of the motor assembly will affect the oil circulation of the compressor, worsen the oil return and oil discharge of the compressor, and reduce 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 improve the oil circulation of the compressor, ensure the stability of oil return and oil discharge, and improve the reliability of the compressor operation.

[0004] The utility model also provides a refrigeration device comprising the compressor.

[0005] According to the compressor of the first embodiment of the utility model, the motor assembly includes a stator and a rotor, and the stator is arranged along the circumference of the rotor; the pump body assembly includes a cylinder and a main bearing, the main bearing is arranged at one end of the cylinder facing the motor assembly, and the main bearing is provided with an exhaust port connected to the compression chamber of the cylinder; one end of the crankshaft is connected to the rotor, and the other end passes through the main bearing and is rotatably arranged in the cylinder; the muffler is connected to the main bearing, and the muffler is provided with a muffler chamber connected to the exhaust port;

[0006] Among them, the rotor is provided with a vent hole arranged along the axial direction of the rotor, and a cover body is provided at one end of the rotor facing the pump body assembly, the inner cavity of the cover body is connected with the vent hole, and the cover body is provided with a first through hole; the muffler is arranged toward the cover body and is provided with an air outlet, the crankshaft passes through the air outlet and the first through hole, and the muffler chamber is connected with the inner cavity of the cover body through the air outlet.

[0007] The compressor according to the embodiment of the utility model has at least the following beneficial effects:

[0008] The motor assembly drives the crankshaft to rotate through the stator and the rotor, so that the crankshaft can drive the roller to move in the compression chamber of the cylinder to compress the refrigerant. The end of the cylinder facing the motor assembly supports the crankshaft through the main bearing, thereby improving the stability of the crankshaft operation; the compressed gas is discharged from the exhaust port of the main bearing to the muffler, and the exhaust noise is reduced through the muffler chamber; the first through hole of the cover body and the air outlet of the muffler can allow the crankshaft to pass through. Since the air outlet and the first through hole are arranged opposite to each other along the axial direction of the crankshaft, the gas is discharged into the cover body through the air outlet and the first through hole, and after passing through the inner cavity of the cover body, it is exhausted through the vent through the rotor; since the refrigerant gas is discharged from the cylinder and flows in sequence along the muffler chamber, the air outlet, the inner cavity of the cover body, and the vent, it can effectively reduce the disturbance of the airflow to the circulating oil circuit, so that the lubricating oil circulates more smoothly, thereby ensuring the stability of oil return and oil discharge, providing a good lubrication effect to the pump body assembly, and improving the reliability of the compressor operation.

[0009] According to some embodiments of the utility model, an end ring is provided on the end face of the muffler away from the main bearing, the end ring is extended toward the first through hole and surrounds the air outlet, the inner wall of the end ring is spaced apart from the outer wall of the crankshaft, and the outer diameter of the end ring is less than or equal to the aperture of the first through hole.

[0010] According to some embodiments of the utility model, the end face of the main bearing facing away from the cylinder is the first end face, the minimum distance between the top of the end ring and the first end face is H1, and the minimum distance between the cover body and the first end face is H2, satisfying: H1≥H2.

[0011] According to some embodiments of the utility model, the main bearing includes a flange portion and a shaft neck portion connected to the flange portion, the shaft neck portion is arranged in the direction of the rotor, the height of the shaft neck portion is greater than or equal to the height of the muffler, and the inner wall of the end ring is spaced apart from the outer wall of the shaft neck portion.

[0012] According to some embodiments of the present invention, the aperture of the air outlet is D1, along the radial direction of the shaft neck, the outer diameter of the portion of the shaft neck opposite to the inner wall of the end ring is D2, and the gap between the end ring and the shaft neck is mm. 2 The cross-sectional area of ​​the unit is S, the compressor is mm 3 The displacement in / min is C, which satisfies: 1.4x10 -3 ≤S / C≤5.5x10 -3 , and S=π*(D1 2 -D2 2 ) / 4.

[0013] According to some embodiments of the present invention, the compressor further comprises:

[0014] A housing, wherein a mounting cavity is provided in the housing, and the motor assembly, the pump assembly and the muffler are arranged in the mounting cavity;

[0015] The first oil deflector ring is arranged in the installation cavity and surrounds the pump body assembly. The first oil deflector ring is provided with a plurality of oil return holes, and the plurality of oil return holes are arranged along the circumference of the first oil deflector ring.

[0016] According to some embodiments of the utility model, the minimum distance between the first oil retaining ring and the cylinder is H3, the stator includes a stator core and a winding coil formed at both ends of the stator core, and the minimum distance between the winding coil at one end of the stator core facing the pump body assembly and the cylinder is H4, satisfying: 2mm≤H3≤H4-3mm.

[0017] According to some embodiments of the utility model, the cylinder is provided with a vane groove for installing a vane, the vane groove is arranged along the radial direction of the cylinder, and the first oil retaining ring is provided with a notch, the notch and the vane groove are arranged opposite to each other along the axial direction of the crankshaft.

[0018] According to some embodiments of the utility model, a second oil retaining ring is provided at one end of the rotor away from the cover body, a channel connected to the air vent is formed between the second oil retaining ring and the rotor, the second oil retaining ring is provided with a second through hole for the crankshaft to pass through, the aperture of the second through hole is D3, the part where the crankshaft and the rotor are connected is a main shaft section, the minimum outer diameter of the main shaft section is D4, satisfying: 1mm≤D3-D4≤5mm.

[0019] According to some embodiments of the utility model, a first balancing block is provided in the cover body, and the first balancing block is connected to the rotor; a second balancing block is provided at one end of the rotor away from the cover body, and a second oil retaining ring is provided at one end of the second balancing block away from the rotor, and a channel connected to the vent is formed between the second oil retaining ring and the rotor.

[0020] According to some embodiments of the present invention, the rotor includes a rotor core, the rotor core is provided with an axial hole and a plurality of the ventilation holes, the axial hole is connected to the crankshaft, and the plurality of the ventilation holes are spaced apart around the crankshaft along the circumference of the rotor core.

[0021] The refrigeration device according to the second embodiment of the utility model comprises the compressor described in the first embodiment.

[0022] The refrigeration device according to the embodiment of the utility model comprises the compressor of the embodiment of the first aspect and thus has at least the above-mentioned beneficial effects, which will not be described in detail here.

[0023] 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

[0024] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0025] Figure 1 It is a schematic diagram of the cross-sectional structure of a compressor of some embodiments of the utility model;

[0026] Figure 2 It is a schematic cross-sectional structure diagram of a pump body assembly in a compressor in some embodiments of the utility model;

[0027] Figure 3 It is a cross-sectional schematic diagram of a bearing system in a compressor in some embodiments of the utility model;

[0028] Figure 4 for Figure 1 The enlarged structural diagram of the A in the middle (with the flow direction mark of the refrigerant gas);

[0029] Figure 5 for Figure 1 A schematic diagram of the enlarged structure at A in the middle;

[0030] Figure 6 for Figure 1 A schematic diagram of the enlarged structure at B in the middle;

[0031] Figure 7 It is a schematic diagram of the top view of the pump body assembly and the first oil retaining ring in the compressor of some embodiments of the utility model;

[0032] Figure 8 for Figure 7 Schematic diagram of the enlarged structure at point C in the middle.

[0033] Reference numerals:

[0034] Housing 100; mounting cavity 110; exhaust pipe 120; first oil retaining ring 130; oil return hole 131; notch 132; support frame 140;

[0035] Motor assembly 200; stator 201; stator core 210; coil 211; rotor 202; rotor core 220; vent 221; cover 230; first through hole 231; inner cavity 232; second oil slinger 240; second through hole 241; first balancing block 250; second balancing block 260; channel 270;

[0036] Pump body assembly 300; first cylinder 310; first compression chamber 311; first roller 312; first sliding plate groove 313; second cylinder 320; second compression chamber 321; second roller 322; main bearing 330; flange 331; journal 332; auxiliary bearing 340; partition 350;

[0037] Crankshaft 400; main shaft section 410; eccentric section 420; deflection portion 421; oil passage 430;

[0038] Muffler 500; muffler cavity 510; air outlet 520; exhaust gap 521; end ring 530;

[0039] Liquid reservoir 600; air intake pipe 610;

[0040] Motor bearing 700;

[0041] Compressor 1000. DETAILED DESCRIPTION

[0042] 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.

[0043] In the description of the present invention, it should be understood that the descriptions involving orientation, such as up, down, left, right, axial, radial, etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply 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.

[0044] In the description of the utility model, if there is a description of first and 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.

[0045] 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.

[0046] Reference Figures 1 to 8As shown, the compressor 1000 of the embodiment of the utility model is applied to a refrigeration system or a heat pump system, etc. The compressor 1000 is specifically a rotary compressor, which can be used in refrigeration systems such as air conditioners and refrigerators, and can also be used in heat pump systems such as air-energy water heaters and floor heating systems. The rotary compressor 1000 is described below with a specific example.

[0047] Reference Figure 1 As shown, the compressor 1000 of the embodiment of the utility model includes a housing 100, a motor assembly 200 and a pump body assembly 300. The housing 100 is provided with an installation cavity 110, and the motor assembly 200 and the pump body assembly 300 are fixedly connected in the installation cavity 110. The motor assembly 200 provides a power source for the pump body assembly 300, and the refrigerant can be compressed through the pump body assembly 300. The compressor 1000 also includes an exhaust pipe 120 and a liquid reservoir 600. The exhaust pipe 120 is connected to the upper end of the housing 100, and the liquid reservoir 600 is connected to the housing 100. The liquid reservoir 600 is connected to the pump body assembly 300 through the air inlet pipe 610, and provides the pump body assembly 300 with refrigerant gas.

[0048] It is understandable that the pump assembly 300 and the motor assembly 200 can be fixed in the housing 100 by welding, or by shrink fitting, or by other feasible fixing methods, which are not specifically limited here. The bottom of the installation cavity 110 is formed as an oil pool, which is used to store lubricating oil. The lubricating oil is used to lubricate the pump assembly 300 and the motor assembly 200, thereby improving the operating stability of the compressor 1000.

[0049] Reference Figure 1 and Figure 2 As shown, the pump assembly 300 in the embodiment is a double-cylinder structure. Specifically, the pump assembly 300 includes a first cylinder 310, a second cylinder 320, a main bearing 330, a secondary bearing 340 and a partition 350. The first cylinder 310 is arranged on the upper side of the second cylinder 320, the partition 350 is arranged between the first cylinder 310 and the second cylinder 320, the main bearing 330 is arranged on the upper side of the first cylinder 310, and the secondary bearing 340 is arranged on the lower side of the second cylinder 320, that is, the first cylinder 310 and the second cylinder 320 are arranged between the main bearing 330 and the secondary bearing 340. The first cylinder 310 is provided with a first compression chamber 311 and a first roller 312 installed in the first compression chamber 311; the second cylinder 320 is provided with a second compression chamber 321 and a second roller 322 installed in the second compression chamber 321. The first cylinder 310 and the second cylinder 320 are respectively fixedly connected to the housing 100 to achieve fixed installation of the pump assembly 300. In some embodiments, the pump assembly 300 can also be fixedly connected to the housing 100 through components such as a main bearing 330 and a secondary bearing 340.

[0050] Reference Figure 2 As shown, the lower part of the crankshaft 400 passes through the main bearing 330, the first cylinder 310, the partition 350, the second cylinder 320 and the auxiliary bearing 340 in sequence, and two eccentric parts 421 are provided at the lower part of the crankshaft 400. The two eccentric parts 421 are arranged along the upper and lower intervals and are rotatably provided in the first compression chamber 311 and the second compression chamber 321 respectively. One of the eccentric parts 421 is connected to the first roller 312, and the other eccentric part 421 is connected to the second roller 322. The first roller 312 and the second roller 322 are driven to rotate by the crankshaft 400, thereby realizing the compression of the refrigerant in the first compression chamber 311 and the second compression chamber 321.

[0051] Reference Figure 3 As shown, it can be understood that the support and positioning of the crankshaft 400 are achieved by the main bearing 330 and the secondary bearing 340. The main bearing 330 is the first supporting structure of the crankshaft 400, and the secondary bearing 340 is the second supporting structure of the crankshaft 400. The crankshaft 400 is supported by the first supporting structure and the second supporting structure to improve the working stability of the first cylinder 310 and the second cylinder 320.

[0052] In addition, a motor bearing 700 is provided above the motor assembly 200, and the motor bearing 700 supports the end of the crankshaft 400 away from the pump body assembly 300. Specifically, a support frame 140 is also provided in the installation cavity 110, and the support frame 140 is welded or fixedly connected to the housing 100 in other ways, and the motor bearing 700 is connected to the support frame 140. The motor bearing 700 is the third support structure of the crankshaft 400. The motor bearing 700, the main bearing 330, the auxiliary bearing 340 and the crankshaft 400 together constitute the bearing system of the compressor 1000, that is, the crankshaft 400 is supported and positioned by the first support structure, the second support structure and the third support structure, so that the bearing system operates more stably, and by adding the motor bearing 700, the deformation of the shaft end of the crankshaft 400 can be effectively reduced, and the coaxiality of the stator 201 and the rotor 202 in the motor assembly 200 can be ensured.

[0053] Reference Figure 3 As shown, an oil passage 430 is provided in the crankshaft 400, and the oil passage 430 penetrates the crankshaft 400 along the axial direction of the crankshaft 400. Since an oil pool is provided in the housing 100, the lower end of the oil passage 430 is open and communicated with the oil pool. When the compressor 1000 is running, the crankshaft 400 rotates at a high speed, and the lubricating oil in the oil pool is transported upward through the oil passage 430 to lubricate the pump body assembly 300, the crankshaft 400 and other components, reduce wear, and can take away part of the heat generated during the rotation of the crankshaft 400 through the lubricating oil, thereby improving the reliability of the rotary compressor 1000.

[0054] It should be noted that the pump body assembly 300 is not limited to a dual-cylinder structure. In some embodiments, the pump body assembly 300 is a single-cylinder structure. For example, the pump body assembly 300 includes a first cylinder 310, and the main bearing 330 and the auxiliary bearing 340 are respectively located on the upper and lower sides of the first cylinder 310. For details, please refer to the structure shown in the first cylinder 310 in the above embodiment.

[0055] Reference Figure 1 As shown, in the embodiment, the motor assembly 200 includes a stator 201 and a rotor 202. The stator 201 is annular and fixedly connected to the inner wall of the housing 100. The stator 201 is arranged around the rotor 202 so that the rotor 202 can rotate in the stator 201. The rotor 202 is provided with an axial hole, and the crankshaft 400 is passed through the axial hole so that the crankshaft 400 is fixedly connected to the rotor 202. The rotor 202 can rotate relative to the stator 201. The crankshaft 400 is driven by the rotor 202 to drive the two eccentric parts 421 to rotate, thereby realizing the compression of the refrigerant in the first cylinder 310 and the second cylinder 320.

[0056] It can be understood that the main bearing 330 is provided with an exhaust port (not shown in the drawings), wherein the first compression chamber 311 of the first cylinder 310 is connected to the exhaust port. Since the second cylinder 320 is located below the first cylinder 310, in some embodiments, the second compression chamber 321 is connected to the exhaust port through the exhaust channel 270, and the exhaust channel 270 runs through the partition 350 and the first cylinder 310. In this way, after being compressed by the first compression chamber 311 and the second compression chamber 321, the high-temperature and high-pressure refrigerant gas will be discharged from the exhaust port and flow from bottom to top to the exhaust pipe 120.

[0057] Reference Figure 1 and Figure 2 As shown, the compressor 1000 further includes a muffler 500, in which a muffler chamber 510 is provided. The muffler 500 is connected to the main bearing 330. For example, the muffler 500 can be fixedly mounted on the upper end of the main bearing 330 by screws or rivets. The lower end of the muffler 500 is an open port, and the muffler 500 covers the upper end surface of the main bearing 330, so that the muffler chamber 510 is connected to the exhaust port through the open port. The upper end of the muffler 500 is provided with an outlet 520. After being compressed, the refrigerant enters the muffler chamber 510 from the exhaust port, and then passes through the muffler chamber 510 and is discharged from the outlet 520. The muffler chamber 510 plays a role in noise reduction, thereby reducing the exhaust noise of the pump body assembly 300 through the muffler 500.

[0058] Reference Figure 2As shown, it should be noted that the muffler 500 is arranged around the crankshaft 400, and the air outlet 520 is arranged at the center of the muffler 500. The air outlet 520 is not only used for exhausting the muffler chamber 510, but also for passing the crankshaft 400. The crankshaft 400 includes a main shaft section 410 and an eccentric section 420 connected to each other. The main shaft section 410 is connected to the motor assembly 200, and the eccentric portion 421 is arranged on the eccentric section 420. It can be understood that the aperture of the air outlet 520 is larger than the main shaft section 410 of the crankshaft 400, so that there is a certain gap between the inner wall of the air outlet 520 and the crankshaft 400, so that the refrigerant gas can be discharged from the gap.

[0059] It is understandable that during the operation of the compressor 1000, the lubricating oil in the oil pool will be transported upward to lubricate the pump body assembly 300, the crankshaft 400 and other components. When the oil circuit is smooth, the oil discharge and oil return are balanced, the oil level can be kept stable, and good lubrication performance is guaranteed. However, considering that the third support structure is added to the upper part of the installation cavity 110, and in order to improve the power and running stability of the motor assembly 200, multiple layers of electromagnetic coils are stacked in the axial direction of the rotor 202 to improve the performance of the motor assembly 200, that is, the motor assembly 200 has the effect of high thickness (stack thickness). The third support structure and high thickness will deteriorate the oil return and oil discharge of the compressor 1000, and reduce the reliability of the compressor 1000. Therefore, the embodiment of the utility model needs to improve the oil circuit circulation of the compressor 1000, ensure the stability of oil return and oil discharge, and improve the reliability of the operation of the compressor 1000.

[0060] Reference Figure 1 and Figure 4 As shown, the rotor 202 includes a rotor core 220, and the crankshaft 400 is connected to the rotor core 220. The rotor core 220 is provided with a plurality of air holes 221. The plurality of air holes 221 penetrate the rotor core 220 along the axial direction of the rotor core 220. The air holes 221 are arranged at intervals around the crankshaft 400 along the circumference of the rotor core 220 to allow the refrigerant gas to pass through the rotor 202, thereby preventing the motor assembly 200 from blocking the exhaust of the compressor 1000. In the embodiment, a cover body 230 is provided at the lower end of the rotor core 220. The cover body 230 is cylindrical and is covered on the end surface of the rotor core 220. The cover body 230 has an inner cavity 232, which is connected to the vent hole 221. A first through hole 231 is provided in the middle of the cover body 230. The aperture of the first through hole 231 is larger than the outer diameter of the main shaft section 410 of the crankshaft 400, so that the main shaft section 410 can pass through the cover body 230 through the first through hole 231, and a gap is formed between the inner wall of the first through hole 231 and the outer wall of the main shaft section 410, so that the refrigerant gas can enter the inner cavity 232 of the cover body 230 from the first through hole 231.

[0061] Reference Figure 4As shown, it can be understood that the upper end of the muffler 500 is extended toward the direction of the cover body 230, so that the air outlet 520 is close to the first through hole 231. Since the air outlet 520 and the first through hole 231 are arranged relative to each other along the axial direction of the crankshaft 400, the air outlet 520 is connected to the first through hole 231, so that the muffler chamber 510 is connected with the inner cavity 232 of the cover body 230 through the air outlet 520, and the refrigerant gas is discharged to the inner cavity 232 of the cover body 230 through the air outlet 520 and the first through hole 231. After passing through the inner cavity 232 of the cover body 230, the refrigerant gas passes through the rotor core 220 through the vent 221 for exhaust. Figure 4 The direction indicated by the middle arrow is the flow direction of the refrigerant gas. Since the refrigerant gas flows along the silencer cavity 510, the gas outlet 520, the inner cavity 232 of the cover body 230 and the vent hole 221 in sequence after being discharged from the exhaust port, the disturbance of the air flow to the circulating oil circuit can be effectively reduced, so that the circulation flow of the lubricating oil is smoother, thereby ensuring the stability of oil return and oil discharge, providing a good lubrication effect to the pump body assembly 300, and improving the reliability of the operation of the compressor 1000.

[0062] It should be noted that, in order to ensure that the oil pool has enough lubricating oil to lubricate the pump body assembly 300, the crankshaft 400 and other components, the oil level of the oil pool will be higher than the bottom of the crankshaft 400, and the oil pool will further soak part of the pump body assembly 300, for example, the oil level of the oil pool reaches the position of the partition 350. When the compressor 1000 is running, the lubricating oil will be transported upward and return downward after lubrication, that is, it will circulate in the up and down directions. The circulating oil path of the lubricating oil will pass through the space between the motor assembly 200 and the pump body assembly 300. When the circulating oil path is smooth, the oil discharge and oil return are balanced, and the oil level of the oil pool remains stable.

[0063] In the related art, when the rotor 202 does not have a cover body 230, the high-temperature and high-pressure gas has a high flow rate after being discharged from the muffler 500. When passing through the above-mentioned space, the high-speed airflow will enter the space between the motor assembly 200 and the pump body assembly 300, causing disturbances to the circulating oil circuit, thereby affecting the oil return and oil discharge, and the oil level in the oil pool will also drop, thereby reducing the lubrication effect on the pump body assembly 300. In the embodiment of the utility model, the silencer 500 cooperates with the cover body 230. The refrigerant gas enters the silencer chamber 510 after being discharged from the exhaust port. After being discharged from the silencer chamber 510 through the air outlet 520, the refrigerant gas does not directly enter the above-mentioned space, but enters the inner cavity 232 of the cover body 230 along the air outlet 520 and the first through hole 231, and then flows upward along the vent hole 221 to the exhaust pipe 120. In other words, the space between the motor assembly 200 and the pump body assembly 300 through which the exhaust gas flows is reduced. Therefore, the disturbance of the air flow to the circulating oil circuit can be effectively reduced, and the circulating oil circuit is smoother, ensuring the balance between oil return and oil discharge. The oil level is also more stable, ensuring better lubrication effect, and improving the reliability of the operation of the compressor 1000.

[0064] Reference Figure 5 As shown, the end surface of the muffler 500 away from the main bearing 330 is protruded to form an end ring 530, the end ring 530 is extended toward the first through hole 231, and the end ring 530 is arranged in a ring shape around the crankshaft 400, and the end ring 530 is arranged to form an outlet 520. Since the outlet 520 is not only for the crankshaft 400 to pass through, but also for discharging refrigerant gas, the aperture D1 of the outlet 520 is larger than the outer diameter D4 of the main shaft section 410, that is, D1>D4, and the inner wall of the end ring 530 is spaced from the outer wall of the crankshaft 400, so that an exhaust gap 521 is formed between the end ring 530 and the crankshaft 400. It can be understood that the larger the aperture D1 of the outlet 520 is than the outer diameter D4 of the main shaft section 410, the larger the size of the exhaust gap 521, and the larger the exhaust volume. The specific size of the exhaust gap 521 can be set according to the displacement of the compressor 1000. It should be noted that the aperture D1 of the gas outlet 520 is the inner diameter of the end ring 530 .

[0065] Reference Figure 5 As shown, it can be understood that the outer diameter D5 of the end ring 530 is less than or equal to the aperture D6 of the first through hole 231, that is, D5≤D6, so that the cover body 230 will not block the exhaust gap 521, and the gas discharged from the exhaust gap 521 can enter the inner cavity 232 of the cover body 230 through the first through hole 231. When D5≤D6 is satisfied, the end ring 530 can extend toward the first through hole 231 and extend into the cover body 230, ensuring that the airflow discharged from the exhaust gap 521 can enter the inner cavity 232 of the cover body 230, effectively reducing the airflow flowing to the outside of the cover body 230, thereby reducing the disturbance caused to the oil circuit. In some embodiments, when the outer diameter D5 of the end ring 530 is larger than the aperture D6 of the first through hole 231, the end ring 530 cannot pass through the first through hole 231. At this time, the top end of the end ring 530 can be set close to the bottom end of the cover body 230, so that the airflow discharged from the exhaust gap 521 can smoothly enter the inner cavity 232 of the cover body 230.

[0066] It should be noted that, when the compressor 1000 is working, the cover 230 rotates with the rotor core 220, while the muffler 500 is fixed and stationary. In order to avoid interference of the muffler 500 with the cover 230, Figure 5 In the illustrated embodiment, the aperture of the first through hole 231 and the outer diameter of the end ring 530 are set to satisfy D5<D6, so that even if the end ring 530 extends into the inner cavity 232 of the cover body 230, it will not interfere with the cover body 230.

[0067] Reference Figure 5As shown, in some embodiments, the upper end face of the main bearing 330 is the first end face, the minimum distance between the upper top of the end ring 530 and the first end face is H1, and the minimum distance between the cover 230 and the first end face is H2, satisfying: H1≥H2. It can be understood that when D5≤D6 is satisfied, the end ring 530 can pass through the first through hole 231 and extend into the cover 230. Since the muffler 500 is connected to the first end face, the distance between the bottom end of the muffler 500 and the upper top of the end ring 530 is the overall height of the muffler 500. Therefore, when H1>H2, it means that the overall height of the muffler 500 is greater than the distance between the cover body 230 and the first end face. At this time, the upper end of the end ring 530 passes through the first through hole 231 and extends into the cover body 230, so that the air outlet 520 is directly connected to the inner cavity 232 of the cover body 230, and the refrigerant gas is directly discharged into the inner cavity 232 of the cover body 230 through the exhaust gap 521, and then flows upward along the vent 221 to the exhaust pipe 120. The airflow does not need to pass through the space between the motor assembly 200 and the pump body assembly 300, thereby effectively reducing the disturbance of the airflow to the oil circuit in the space, and the circulating oil circuit is smoother, ensuring the balance between oil return and oil discharge, and the oil level is more stable.

[0068] It should be noted that Figure 5 In the illustrated embodiment, the overall height of the muffler 500 is equal to the distance between the cover body 230 and the first end face, that is, H1=H2 is satisfied. At this time, the upper end face of the end ring 530 is flush with the bottom face of the cover body 230, the air outlet 520 is connected to the first through hole 231, and the refrigerant gas can also be directly discharged to the inner cavity 232 of the cover body 230 through the exhaust gap 521, which has the effect of reducing the disturbance of the air flow to the oil path in the above space. It can be understood that the overall height of the muffler 500 is not higher than the distance between the rotor core 220 and the first end face, so as to avoid interference between the top of the end ring 530 and the rotor core 220.

[0069] Reference Figure 4 and Figure 5 As shown, it can be understood that the main bearing 330 includes a flange portion 331 and a journal portion 332, the journal portion 332 is connected to the upper side of the flange portion 331, and the journal portion 332 is extended along the axial direction of the crankshaft 400 toward the rotor 202. The crankshaft 400 is supported by the journal portion 332, further improving the stability of the operation of the crankshaft 400 and ensuring the coaxiality of the stator 201 and the rotor 202. The end face of the flange portion 331 away from the first cylinder 310 is the first end face, and the first end face is arranged around the journal portion 332. The muffler cavity 510 is an annular cavity surrounding the journal portion 332.

[0070] Specifically, in the embodiment, the height H5 of the journal portion 332 is greater than or equal to the height of the muffler 500, and the inner wall of the end ring 530 is spaced from the outer wall of the journal portion 332. That is to say, the journal portion 332 is added between the end ring 530 and the crankshaft 400. In order to meet the exhaust of the muffler chamber 510, the gap between the end ring 530 and the journal portion 332 forms an exhaust gap 521. When H1≤H5 is satisfied, on the one hand, the journal portion 332 can provide a stable supporting force to the crankshaft 400. On the other hand, considering that the exhaust gap 521 is small, the muffler 500 is separated from the crankshaft 400 by the journal portion 332, which can avoid the contact between the muffler 500 and the crankshaft 400 and cause wear or loosening, thereby improving the structural stability.

[0071] Reference Figure 5 As shown, it can be understood that the larger the size of the exhaust gap 521 between the end ring 530 and the shaft neck 332, the greater the exhaust volume. The size of the exhaust gap 521 is the distance between the inner wall of the end ring 530 and the outer wall of the shaft neck 332. The exhaust volume can be adjusted by designing the size of the exhaust gap 521, and the change in the size of the exhaust gap 521 will also affect the overall displacement of the compressor 1000. Therefore, the specific size of the exhaust gap 521 needs to be set according to the displacement of the compressor 1000, that is, the exhaust gap 521 needs to be designed within a reasonable size range.

[0072] Specifically, when the size of the exhaust gap 521 is too small, the exhaust volume of the muffler 500 will be reduced, affecting the performance of the compressor 1000; when the size of the exhaust gap 521 is too large, the exhaust volume of the muffler 500 will increase, and the aerodynamic noise will also increase, reducing the noise reduction effect of the muffler 500, and the airflow will easily disturb the oil circuit, reducing the stability of the oil surface.

[0073] Based on this, in the embodiment of the utility model, since the upper end of the journal 332 and the end ring 530 are arranged opposite to each other along the radial direction of the journal 332, the size of the upper end of the journal 332 and the size of the end ring 530 are optimized, wherein the outer diameter of the upper end of the journal 332 is D2, the cross-sectional area of ​​the exhaust gap 521 between the end ring 530 and the journal 332 is S, and the displacement of the compressor 1000 is C, which satisfies: 1.4x10 -3 ≤S / C≤5.5x10 -3 , and S=π*(D1 2 -D2 2 ) / 4. The cross-sectional area S of the exhaust gap 521 is π*(D1 2 -D2 2 ) / 4 represents the difference between the cross-sectional area of ​​the air outlet 520 and the cross-sectional area of ​​the journal 332; the unit of the cross-sectional area is mm 2 (square millimeters), the unit of displacement is mm3 / min (cubic millimeters per minute), the above formula is also expressed as the exhaust gap 521 in mm 2 The cross-sectional area S of the compressor under the unit 1000 in mm 3 The ratio of displacement C in / min units specifically meets the following requirements: 1.4x10 -3 min / mm≤S / C≤5.5x10 -3 min / mm. Specifically, from the numerical ratio, the cross-sectional area S of the exhaust gap 521 is greater than or equal to 1.4x10 -3 times the displacement C of the compressor 1000, and less than or equal to 5.5x10 -3 times the displacement C of the compressor 1000, that is, the cross-sectional area of ​​the exhaust gap 521 cannot be too large or too small. For example, the displacement of the compressor 1000 is 2x10 6 mm 3 / min, according to the above formula, the cross-sectional area S of the exhaust gap 521 can be calculated to be in the range of 2.8x10 3 mm 2 ≤S≤1.1x10 4 mm 2 .

[0074] Reference Figure 2 As shown, it should be noted that in the related art, when the rotor 202 does not have the cover 230, the refrigerant gas will disturb the circulating oil circuit, affecting the oil return and oil discharge, and the oil level in the oil pool will drop. Figure 2 The position indicated by L1 is the position of the oil level. At this time, the operating frequency is 160Hz. The oil level of the oil pool is only maintained below the partition 350, and does not reach the specified oil level height, which reduces the lubrication effect on the pump assembly 300. The optimal oil level height is approximately 5mm above the partition 350. The matching structure of the muffler 500 and the cover 230 of the embodiment of the utility model is adopted, and further meets: 1.4x10 -3 ≤S / C≤5.5x10 -3 , and S=π*(D1 2 -D2 2 ) / 4, which can not only ensure the displacement requirement of the compressor 1000, but also enable the refrigerant gas to be directly discharged to the inner cavity 232 of the cover body 230 through the exhaust gap 521, reduce the disturbance of the air flow to the oil path of the space, ensure the balance of oil return and oil discharge, and increase the stability of the oil level. Compared with the solutions in the related art, Figure 2The position indicated by L2 is the position of the oil level in the embodiment of the utility model. The position of the oil level will be higher. The working frequency of the experimental process is 200 Hz. The oil level of the oil pool can reach 5 mm above the partition 350, or even exceed the height of 5 mm. The oil pool below the middle end surface of the first cylinder 310 can be in a full state, thereby significantly improving the lubrication effect.

[0075] Reference Figure 2 , Figure 4 and Figure 5 As shown, the compressor 1000 also includes a first oil retainer ring 130, which is arranged in the installation cavity 110. The first oil retainer ring 130 can be fixedly connected to the inner wall of the housing 100, or fixedly connected to the main bearing 330, or fixedly connected to the first cylinder 310, and can be fixed by welding. The first oil retainer ring 130 is arranged around the pump body assembly 300 and has a ring structure. In the embodiment, the first oil retainer ring 130 is located above the first cylinder 310 and close to the first end face of the main bearing 330. It can be understood that since the muffler 500 is connected to the first end face, the oil pool is separated from the space above the pump body assembly 300 by the first oil retainer ring 130, and the air outlet 520 is located above the first oil retainer ring 130, which effectively blocks the influence of the airflow on the oil pool, making the oil level of the oil pool more stable; and effectively blocks the upward diversion of the lubricating oil, which is conducive to reducing the oil discharge amount of the compressor 1000.

[0076] Reference Figure 7 As shown, the first oil retaining ring 130 is provided with three oil return holes 131, and the three oil return holes 131 are arranged at intervals along the circumference of the first oil retaining ring 130. When the lubricating oil in the space above the pump body assembly 300 returns, it will pass through the first oil retaining ring 130 through the oil return holes 131 and return to the oil pool, so that the first oil retaining ring 130 can not only block the disturbance of the airflow to the oil pool, but also does not affect the return of the lubricating oil. It can be understood that the number of oil return holes 131 is not limited to three, and two, four or more can also be provided. In addition, the shape of the oil return hole 131 can be circular, elongated, etc., which is not specifically limited here.

[0077] Reference Figure 5As shown, in some embodiments, the minimum distance between the first oil retaining ring 130 and the first cylinder 310 is H3, the stator 201 includes a stator core 210, and a winding is wound on the stator core 210. The winding forms a coil 211 at both ends of the stator core 210, and the minimum distance between the coil 211 at the lower end of the stator core 210 and the cylinder is H4, satisfying: 2mm≤H3≤H4-3mm, that is, the minimum distance H3 between the first oil retaining ring 130 and the first cylinder 310 is greater than or equal to 2mm. When H3 is less than 2mm, the distance between the first oil retaining ring 130 and the first cylinder 310 is too small, which may easily cause the problem of poor oil return, affecting the effect of stabilizing the oil level. Since the coil 211 and the cylinder need to meet the safety distance requirement, so that the coil 211 cannot be too close to the cylinder, the minimum distance H3 between the first oil retaining ring 130 and the first cylinder 310 also needs to meet H3≤H4-3mm, that is, the distance between the first oil retaining ring 130 and the coil 211 cannot be too large, so as to improve the operating safety of the compressor 1000. For example, the minimum distance H4 between the coil 211 at the lower end of the stator core 210 and the first cylinder 310 is 30mm, and the minimum distance H3 between the first oil retaining ring 130 and the first cylinder 310 meets: H3≤27mm.

[0078] Reference Figure 7 and Figure 8 As shown, the first cylinder 310 is provided with a first vane groove 313, which is arranged along the radial direction of the first cylinder 310. The first vane groove 313 is used to install the first vane, and the first vane can slide in the first vane groove 313. The upper side of the first vane groove 313 is open. The first oil retaining ring 130 is provided with a notch 132, which is arranged opposite to the first vane groove 313 along the axial direction of the crankshaft 400, that is, the first vane groove 313 is connected to the notch 132, and the lubricating oil collected on the first oil retaining ring 130 can flow into the first vane groove 313 along the notch 132, so that the first vane and the first vane groove 313 can be lubricated, thereby improving the lubrication effect and operation reliability of the pump body assembly 300.

[0079] It is understandable that, along the axial direction of the crankshaft 400, the projection of the notch 132 and the projection of the first vane groove 313 may overlap, that is, the notch 132 and the first vane groove 313 are arranged opposite to each other; the projection of the notch 132 and the projection of the first vane groove 313 may also partially overlap, so that the lubricating oil can flow into the first vane groove 313 along the notch 132. The specific size of the notch 132 can be set according to the actual size of the first vane groove 313.

[0080] Reference Figure 1 and Figure 6As shown, in some embodiments, a second oil retainer ring 240 is provided at the upper end of the rotor core 220, and the second oil retainer ring 240 and the rotor core 220 are spaced apart to form a channel 270, and the second oil retainer ring 240 is arranged opposite to the gas outlet end of the vent hole 221, so that the vent hole 221 is connected with the channel 270, and a second through hole 241 is provided in the middle of the second oil retainer ring 240 for the crankshaft 400 to pass through. It can be understood that the oil-gas mixture of the refrigerant gas and the lubricating oil flowing out through the vent hole 221 can flow along the channel 270 to the inner wall of the housing 100 or the coil 211 at the upper end of the stator core 210. Due to the centrifugal force generated by the high-speed rotation of the rotor, the oil-gas mixture can be thrown outward. Due to the inconsistent density of the lubricating oil and the refrigerant gas, under the action of gravity, the lubricating oil can be separated from the refrigerant gas, so that the lubricating oil can flow back downward, and the refrigerant gas will flow upward to the exhaust pipe 120, thereby reducing the oil discharge amount of the compressor 1000.

[0081] Reference Figure 6 As shown, in the embodiment, the aperture of the second through hole 241 is D3, and the minimum outer diameter of the main shaft section 410 is D4, which satisfies: 1mm≤D3-D4≤5mm. It can be understood that the upper end of the main shaft section 410 passes through the second through hole 241, and the outer diameter of the main shaft section 410 at the upper end is smaller. The aperture of the second through hole 241 is selected and designed according to the outer diameter of the main shaft section 410. For example, the outer diameter of the upper end of the main shaft section 410 is 12mm, and the aperture D3 of the second through hole 241 ranges from 13mm≤D3≤17mm. That is to say, when the size of the crankshaft 400 is fixed, the aperture of the second through hole 241 cannot be too small or too large. The difference between the aperture and the minimum outer diameter of the main shaft section 410 needs to be greater than or equal to 1mm and less than or equal to 5mm, so as to ensure that most of the oil-gas mixture can flow to the outside along the channel 270, effectively separate the lubricating and refrigerant gases, and reduce the amount of oil discharge.

[0082] Reference Figure 4 and Figure 6As shown, it should be noted that a first balancing block 250 is installed at the lower end of the rotor core 220, and a second balancing block 260 is installed at the upper end of the rotor core 220. The first balancing block 250 is located in the cover body 230, and the second balancing block 260 is located between the second oil retaining ring 240 and the rotor core 220. The second oil retaining ring 240 is fixedly connected to the end face of the second balancing block 260 away from the rotor core 220, and the second oil retaining ring 240 is separated from the rotor core 220 by the second balancing block 260 to form a channel 270. The first balancing block 250 and the second balancing block 260 are arranged along the radial opposite sides of the rotor core 220, so as to improve the balance of the rotor 202 during rotation, reduce the radial deviation amplitude of the rotor 202, improve the coaxiality of the stator 201 and the rotor 202, and improve the balancing effect. In addition, since the first balancing weight 250 is installed in the inner cavity 232 of the cover 230, that is, the cover 230 wraps the first balancing weight 250, when the rotor 202 rotates at a high speed, the disturbance of the airflow to the oil pool can be reduced, further improving the stability of the oil surface.

[0083] The utility model embodiment also provides a refrigeration device, including the compressor 1000 shown in the above embodiment. The refrigeration device can be an air conditioner, a refrigerator and other equipment. When the compressor 1000 is working, the refrigerant gas is discharged into the cover body 230 at the lower end of the rotor 202 through the outlet 520 of the muffler 500, and passes through the inner cavity 232 of the cover body 230 and then passes through the rotor 202 through the vent 221 for exhaust; because the gas flows along the muffler cavity 510, the inner cavity 232 of the cover body 230 and the vent 221 in sequence after being discharged from the cylinder, it can effectively reduce the disturbance of the airflow to the circulating oil circuit, so that the circulation of the lubricating oil is smoother, thereby ensuring the stability of oil return and oil discharge, ensuring that the pump body assembly 300 has a good lubrication effect, improving the stability of the operation of the compressor 1000, and making the operation of the refrigeration equipment more reliable.

[0084] Since the refrigeration device includes the compressor 1000 of the above embodiment, it has at least the above beneficial effects, which will not be described in detail here.

[0085] Of course, the present invention is not limited to the above-mentioned embodiments, and technicians familiar with the field may make equivalent modifications or substitutions without violating the spirit of the present invention. These equivalent modifications or substitutions are all included in the scope defined by the claims of this application.

Claims

1. A compressor, characterized in that: include: A motor assembly, comprising a stator and a rotor, wherein the stator is arranged along the circumference of the rotor; A pump body assembly, comprising a cylinder and a main bearing, wherein the main bearing is arranged at one end of the cylinder facing the motor assembly, and the main bearing is provided with an exhaust port communicating with the compression chamber of the cylinder; A crankshaft, one end of which is connected to the rotor, and the other end of which passes through the main bearing and is rotatably disposed in the cylinder; a muffler connected to the main bearing, the muffler being provided with a muffler chamber communicating with the exhaust port; Among them, the rotor is provided with a vent hole arranged along the axial direction of the rotor, and a cover body is provided at one end of the rotor facing the pump body assembly, the inner cavity of the cover body is connected with the vent hole, and the cover body is provided with a first through hole; the muffler is arranged toward the cover body and is provided with an air outlet, the crankshaft passes through the air outlet and the first through hole, and the muffler chamber is connected with the inner cavity of the cover body through the air outlet.

2. The compressor according to claim 1, characterized in that The end face of the muffler away from the main bearing is provided with an end ring, the end ring extends toward the first through hole and surrounds the air outlet, the inner wall of the end ring is spaced apart from the outer wall of the crankshaft, and the outer diameter of the end ring is less than or equal to the aperture of the first through hole.

3. The compressor according to claim 2, characterized in that The end face of the main bearing facing away from the cylinder is the first end face, the minimum distance between the top end of the end ring and the first end face is H1, and the minimum distance between the cover body and the first end face is H2, satisfying: H1≥H2.

4. The compressor according to claim 2, characterized in that The main bearing includes a flange portion and a journal portion connected to the flange portion, the journal portion is arranged toward the direction of the rotor, the height of the journal portion is greater than or equal to the height of the muffler, and the inner wall of the end ring is spaced apart from the outer wall of the journal portion.

5. The compressor according to claim 4, characterized in that The aperture of the air outlet is D1, along the radial direction of the shaft neck, the outer diameter of the part of the shaft neck opposite to the inner wall of the end ring is D2, and the gap between the end ring and the shaft neck is mm. 2 The cross-sectional area of ​​the unit is S, the compressor is mm 3 The displacement in / min is C, which satisfies: 1.4x10 -3 ≤S / C≤5.5x10 -3 , and S=π*(D1 2 -D2 2 ) / 4.

6. The compressor according to claim 1, characterized in that The compressor also includes: A housing, wherein a mounting cavity is provided in the housing, and the motor assembly, the pump assembly and the muffler are arranged in the mounting cavity; The first oil deflector ring is arranged in the installation cavity and surrounds the pump body assembly. The first oil deflector ring is provided with a plurality of oil return holes, and the plurality of oil return holes are arranged along the circumference of the first oil deflector ring.

7. The compressor according to claim 6, characterized in that The minimum distance between the first oil retaining ring and the cylinder is H3, the stator includes a stator core and a winding coil formed at both ends of the stator core, and the minimum distance between the winding coil at one end of the stator core facing the pump body assembly and the cylinder is H4, satisfying: 2mm≤H3≤H4-3mm.

8. The compressor according to claim 6, characterized in that The cylinder is provided with a vane groove for installing a vane, the vane groove is arranged along the radial direction of the cylinder, the first oil retaining ring is provided with a notch, the notch and the vane groove are arranged opposite to each other along the axial direction of the crankshaft.

9. The compressor according to claim 1, characterized in that A second oil retaining ring is provided at one end of the rotor away from the cover body, a channel connected to the air vent is formed between the second oil retaining ring and the rotor, the second oil retaining ring is provided with a second through hole for the crankshaft to pass through, the aperture of the second through hole is D3, the part where the crankshaft and the rotor are connected is a main shaft section, the minimum outer diameter of the main shaft section is D4, and satisfies: 1mm≤D3-D4≤5mm.

10. The compressor according to claim 1, characterized in that A first balancing block is provided in the cover body, and the first balancing block is connected to the rotor; a second balancing block is provided at one end of the rotor away from the cover body, and a second oil retaining ring is provided at one end of the second balancing block away from the rotor, and a channel connected to the vent is formed between the second oil retaining ring and the rotor.

11. The compressor according to claim 1, characterized in that The rotor comprises a rotor core, wherein the rotor core is provided with an axial hole and a plurality of ventilation holes, wherein the axial hole is connected to the crankshaft, and the plurality of ventilation holes are arranged at intervals around the crankshaft along the circumference of the rotor core.

12. A refrigeration device, characterized in that: A compressor comprising the compressor according to any one of claims 1 to 11.

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