Rotary compressor and refrigeration device

Abstract

A rotary compressor and a refrigeration device. The rotary compressor comprises a casing (100), a motor assembly (200), a pump body assembly (300), and a crankshaft (400). The casing (100) comprises a main housing (110), a first housing (120) and a second housing (130), wherein the first housing (120) is mounted at an upper end of the main housing (110), and the second housing (130) is mounted at a lower end of the main housing (110). The motor assembly (200) comprises a stator (210) and a rotor (220). The pump body assembly (300) comprises a cylinder (310) and a roller (320). The crankshaft (400) is fixedly connected to the rotor (220), and the crankshaft (400) is provided with an eccentric portion (410) rotatably matching the roller (320). The inner diameter of the cylinder (310) is D1, the inner diameter of the roller (320) is D2, and the height of the casing (100) is H1. In the height direction of the casing (100), the minimum distance between an upper end surface of an iron core (211) of the stator (210) and an upper end surface of the main housing (110) is H2, the maximum distance between an upper end surface of the rotor (220) and a lower end surface of the cylinder (310) is H3, and the maximum height of the cylinder (310) is H4, wherein 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.2.

Description

Rotary compressor and refrigeration equipment

[0001] Cross-reference to Related Applications

[0002] The present application claims priority to Chinese Patent Application No. 202410892075.9, filed on July 3, 2024, and entitled “Rotary Compressor and Refrigeration Equipment”, and Chinese Patent Application No. 202421570349.4, filed on July 3, 2024, and entitled “Rotary Compressor and Refrigeration Equipment”, the contents of which are incorporated herein by reference in their entirety. TECHNICAL FIELD

[0003] The present application relates to the technical field of compressors, in particular to a rotary compressor and a refrigeration equipment. BACKGROUND

[0004] During the operation of the compressor, the crankshaft rotates and sends the refrigeration oil in the oil pool upward to achieve the purpose of providing lubrication and heat dissipation for the moving parts inside the compressor. However, when the compressor operates at high speed, a large amount of refrigeration oil is output from the oil outlet at the top of the crankshaft, and part of the refrigeration oil will be discharged with the high-pressure refrigerant in gaseous form to the refrigeration system of the refrigeration equipment, causing an increase in oil discharge amount, a decrease in the amount of refrigeration oil inside the compressor, and a decrease in reliability. In addition, the high-pressure refrigerant contains a large amount of refrigeration oil, which can cause a decrease in refrigeration capacity. SUMMARY

[0005] The present application aims to at least partially solve one of the technical problems existing in the prior art. To this end, the present application proposes a rotary compressor and a refrigeration equipment having the above rotary compressor.

[0006] The rotary compressor according to the first aspect of the present application comprises an outer shell, a motor assembly, and a pump body assembly. The outer shell comprises a main shell, a first shell, and a second shell. The first shell is mounted to an upper end of the main shell, and the second shell is mounted to a lower end of the main shell. The motor assembly comprises a stator and a rotor. The stator is fixedly installed in the main shell, and the rotor is rotatably arranged in an inner hole of the stator. The pump body assembly comprises a cylinder and a roller. The cylinder is installed in the main shell and is provided with a compression chamber. The roller is rotatably arranged in the compression chamber. The crankshaft is fixedly connected with the rotor and comprises an eccentric portion. The eccentric portion is in rotational cooperation with the roller. The inner diameter of the cylinder is D1, the inner diameter of the roller is D2, the height of the outer shell is H1, the minimum distance between the upper end surface of the core of the stator and the upper end surface of the main shell is H2 along the height direction of the outer shell, the maximum distance between the upper end surface of the rotor and the lower end surface of the cylinder is H3, and the maximum height of the cylinder is H4. The following conditions are met: 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.2.

[0007] According to some embodiments of the present application, the minimum distance between the upper end surface of the stator and the upper end surface of the first housing in the height direction is H5, satisfying 0.2≤H5 / H1≤0.4.

[0008] According to some embodiments of the present application, the pump body assembly further comprises a first bearing mounted on the side of the cylinder facing the motor assembly, the first bearing comprising a journal arranged around the outer periphery of the crankshaft, the journal being provided with a first oil drain hole penetrating the inner and outer peripheral walls of the journal, the crankshaft being provided with an oil supply channel penetrating the upper and lower ends of the crankshaft in the height direction and a second oil drain hole penetrating the outer peripheral wall of the crankshaft and the inner peripheral wall of the oil supply channel, the two ends of the second oil drain hole being respectively communicated with the oil supply channel and the gap between the journal and the crankshaft.

[0009] According to some embodiments of the present application, the center lines of the first and second oil drain holes are both perpendicular to the height direction and located at the same height position, and the inner diameter of the first oil drain hole is greater than or equal to the inner diameter of the second oil drain hole.

[0010] According to some embodiments of the present application, the number of the first and second oil drain holes is both multiple, and the height positions of the multiple first and second oil drain holes correspond one by one.

[0011] According to some embodiments of the present application, the inner peripheral wall of the first bearing is further provided with a spiral oil groove extending from the upper end surface of the first bearing to the lower end surface of the first bearing, and the first oil drain hole is arranged staggered with the spiral oil groove.

[0012] According to some embodiments of the present application, the pump body assembly further comprises a muffler and an oil blocking piece, the muffler is sleeved on the outer periphery of the first bearing and is provided with an exhaust port, the oil blocking piece is mounted on the first bearing, and in the height direction, the oil blocking piece is located between the muffler and the lowest first oil drain hole, and the oil blocking piece blocks the exhaust port.

[0013] According to some embodiments of the present application, the oil blocking piece comprises a bottom plate and a side plate, the bottom plate is provided with a through hole and is sleeved on the first bearing, the side plate is connected to the periphery of the bottom plate and extends upward, the bottom plate is provided with a third oil drain hole, and in the radial direction of the crankshaft, the third oil drain hole is arranged staggered with the exhaust port.

[0014] According to some embodiments of the present application, one end of the bottom plate close to the crankshaft is higher than the other end of the bottom plate away from the crankshaft, and the third oil drain hole is located at the other end of the bottom plate away from the crankshaft.

[0015] According to the refrigeration equipment of the second aspect of the present application, the rotary compressor of the first aspect of the present application is adopted.

[0016] Additional aspects and advantages of the present application will be made apparent by the following description and the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0017] The present application will be further described below in conjunction with the accompanying drawings and embodiments, in which:

[0018] Fig. 1 is a sectional view of a rotary compressor according to an embodiment of the present application;

[0019] Fig. 2 is an enlarged view of A in Fig. 1;

[0020] Fig. 3 is a schematic view of a first bearing according to an embodiment of the present application;

[0021] Fig. 4 is a schematic view of a crankshaft according to an embodiment of the present application; and

[0022] Fig. 5 is a schematic view of an oil baffle according to an embodiment of the present application.

[0023] Reference signs: housing 100; main casing 110; first casing 120; exhaust pipe 121; second casing 130; oil sump 140; exhaust cavity 150; motor assembly 200; stator 210; core 211; coil 212; rotor 220; pump body assembly 300; cylinder 310; compression cavity 311; intake port 312; roller 320; first bearing 330; journal portion 331; first oil drain hole 332; spiral oil groove 333; muffler 340; exhaust port 341; oil baffle 350; bottom plate 351; side plate 352; through hole 353; third oil drain hole 354; partition plate 360; second bearing 370; crankshaft 400; eccentric portion 410; oil supply passage 420; second oil drain hole 430; liquid reservoir 500; intake pipe 510. DETAILED DESCRIPTION

[0024] Embodiments of the present application are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference signs represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the accompanying drawings are exemplary and are only for the purpose of explaining the present application, and cannot be understood as limiting the present application.

[0025] In the description of the present application, it should be understood that the orientation description, such as the orientation or position relationship indicated by the upper, lower, front, rear, left, right and the like, is based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application.

[0026] In the description of the present application, one or more is understood as one or more, more than two is understood as more than two, greater than, less than, more than, etc. are understood as not including the number, above, below, etc. are understood as including the number. If the first, second is described, it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features or the sequence of indicated technical features.

[0027] In the description of the present application, unless otherwise explicitly limited, the words such as setting, installing, connecting, assembling, cooperating and the like should be broadly understood, and the person skilled in the art can reasonably determine the specific meaning of the above words in the present application in combination with the specific content of the technical solution.

[0028] Referring to FIGS. 1-5, the first aspect of the present application provides a rotary compressor applied to a refrigeration equipment, which can be a refrigerator, an air conditioner or a water dispenser. The rotary compressor is used to compress and deliver refrigerant to the refrigeration system of the refrigeration equipment, so that the refrigeration system can realize heat exchange and refrigeration by using the refrigerant.

[0029] As shown in FIG. 1, it can be understood that the rotary compressor includes a shell 100, a motor assembly 200, a pump body assembly 300 and a crankshaft 400. Specifically, the shell 100 is a vertically arranged columnar structure with a cavity, and the shell 100 includes a main shell 110, a first shell 120 and a second shell 130. The main shell 110 is a cylindrical structure, the first shell 120 is installed at the upper end of the main shell 110, and the second shell 130 is installed at the lower end of the main shell 110. The first shell 120 and the main shell 110, and the second shell 130 and the main shell 110 are fixed by welding. Generally, the upper end of the first shell 120 is provided with an exhaust pipe 121, which is used to connect with the refrigeration system, so that the high-temperature and high-pressure refrigerant in the shell 100 enters the refrigeration system through the exhaust pipe 121. The lower part of the main shell 110 and the internal space of the second shell 130 form an oil pool 140, i.e. the oil pool 140 is located at the bottom of the shell 100. The oil pool 140 is used to store refrigeration oil to provide lubrication, heat dissipation and sealing during operation of the rotary compressor.

[0030] Referring to FIG. 1, it can be understood that the motor assembly 200 is installed in the shell 100, and specifically, the motor assembly 200 includes a stator 210 and a rotor 220, and generally, the stator 210 is composed of an iron core 211 and a wire package 212 wound on the iron core 211, and the stator 210 is fixedly installed on the inner circumferential wall of the main shell 110 by a hot-joint method, that is, the iron core 211 is fixedly connected with the inner circumferential wall of the main shell 110, and the middle of the stator 210 has an inner hole penetrating in the up-down direction, and the rotor 220 is rotatably installed in the inner hole of the stator 210. It can be easily understood that the motor assembly 200 has a certain distance from the first shell 120 in the up-down direction, and along the up-down direction, the space between the motor assembly 200 and the inner wall of the first shell 120 is defined as the exhaust cavity 150, that is, the exhaust cavity 150 is the space above the motor assembly 200 in the shell 100.

[0031] Referring to FIGS. 1 and 2, it can be understood that the pump body assembly 300 is installed in the shell 100 and located below the motor assembly 200, and specifically, the pump body assembly 300 includes cylinders 310 and rollers 320, and in this embodiment, the number of the cylinders 310 and the rollers 320 is both two and corresponds one by one, the two cylinders 310 are arranged in the up-down direction with a certain distance, and the two rollers 320 are rotatably installed in the compression cavities 311 of the two cylinders 310 to compress the refrigerant. The pump body assembly 300 further includes a first bearing 330, a muffler 340, a second bearing 370 and a partition plate 360, wherein the partition plate 360 is clamped between the two cylinders 310, the first bearing 330 is installed on the upper side of the upper cylinder 310, that is, the first bearing 330 is located on the side of the upper cylinder 310 facing the motor assembly 200, and the first bearing 330 includes a journal portion 331, the second bearing 370 is installed on the lower side of the lower cylinder 310, the muffler 340 is substantially in the form of a cover and is installed on the upper side of the first bearing 330, and the muffler 340 is sleeved on the outer periphery of the journal portion 331 of the first bearing 330, and the inner circumferential wall of the muffler 340 is arranged with a certain distance from the outer circumferential wall of the journal portion 331 of the first bearing 330 and defines an annular exhaust port 341, and the exhaust port 341 opens upward. The muffler 340, the first bearing 330, the two cylinders 310, the partition plate 360 and the second bearing 370 are connected into one whole body by bolts, and the first bearing 330 is fixedly connected with the inner circumferential wall of the main shell 110 by welding, so that the pump body assembly 300 is fixedly connected with the shell 100. It can be easily understood that the rotary compressor further includes a liquid accumulator 500 located on one side of the shell 100, and the cylinder 310 is provided with an air inlet 312, and the air inlet 312 is connected with the liquid accumulator 500 through an air inlet pipe 510, so that the gaseous refrigerant in the liquid accumulator 500 can enter the cylinder 310 to compress the refrigerant.

[0032] Of course, it can be understood that in other embodiments, the number of the cylinders 310 and the rollers 320 can be one, and in this case, the pump body assembly 300 does not include the partition plate 360. It can be easily understood that the fixed connection between the pump body assembly 300 and the outer shell 100 can be achieved by fixedly connecting the cylinder 310 with the main shell 110 or connecting the second bearing 370 with the main shell 110, and here, the detailed description is omitted.

[0033] Referring to FIG. 1, it can be understood that the crankshaft 400 is arranged in the up-down direction, the upper part of the crankshaft 400 is arranged through the rotor 220 and fixedly connected with the rotor 220, and the lower part of the crankshaft 400 is arranged through the first bearing 330, the two cylinders 310 and the partition plate 360, and the second bearing 370 in sequence, and in this case, the shaft neck part 331 of the first bearing 330 is arranged around the outer periphery of the crankshaft 400, and the crankshaft 400 can rotate relative to the shaft neck part 331. The lower part of the crankshaft 400 is provided with two eccentric parts 410 arranged in the up-down direction and spaced apart, and the two eccentric parts 410 are respectively in rotational cooperation with the two rollers 320. Therefore, the rotor 220 can drive the two rollers 320 to rotate in the two compression chambers 311 respectively through the crankshaft 400, so as to realize the compression of the refrigerant.

[0034] Referring to FIG. 1, it can be understood that the center of the crankshaft 400 is further provided with an oil supply channel 420, the oil supply channel 420 penetrates through the upper and lower end surfaces of the crankshaft 400 in the up-down direction, and the lower end of the oil supply channel 420 is in communication with the oil pool 140, and the upper end is in communication with the exhaust cavity 150. Generally, the inner circumferential wall of the lower end of the oil supply channel 420 is provided with an oil supply vane, and when the crankshaft 400 rotates, the oil supply vane can drive the refrigeration oil in the oil pool 140 to be upwardly transported through the oil supply channel 420. After the refrigeration oil is output from the upper end of the oil supply channel 420, it flows back to the oil pool 140 through the gaps between the components in the outer shell 100 under the action of gravity, so as to realize the lubrication and heat dissipation of the moving components in the outer shell 100.

[0035] Referring to FIG. 1, it can be understood that the inner diameter of the cylinder 310 is defined as D1, that is, the inner diameter of the compression chamber 311 of the cylinder 310 is D1, and the inner diameter of the roller 320 is D2, that is, the inner diameter of the shaft hole of the roller 320 cooperating with the eccentric part 410 is D2.

[0036] Referring to FIG. 1, it can be understood that the height of the outer shell 100 is defined as H1, i.e., the distance between the upper end surface of the first shell 120 and the lower end surface of the second shell 130 in the up-down direction is H1; along the height direction (i.e., the up-down direction) of the outer shell 100, the minimum distance between the upper end surface of the core 211 of the stator 210 and the upper end surface of the main shell 110 is H2, H2 reflecting the height position of the stator 210 in the main shell 110 and to some extent reflecting the height of the exhaust cavity 150; the maximum distance between the upper end surface of the rotor 220 (i.e., the upper end surface of the rotor core corresponding to the rotor 220) and the lower end surface of the lowest cylinder 310 is H3, H3 reflecting the relative position relationship between the rotor 220 and the lowest cylinder 310; the maximum height of the cylinder 310 is H4, i.e., the maximum distance between the upper end surface and the lower end surface of the cylinder 310; the minimum distance between the upper end surface of the stator 210 (i.e., the upper end surface of the wire package 212) and the upper end surface of the first shell 120 is H5, H5 reflecting the size of the exhaust cavity 150 to some extent.

[0037] Referring to FIG. 1, it can be understood that D1, D2, H1, H2, H3 and H4 satisfy: 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.2. (H1*D2*H4) / (D1*(H2+H3))=H1 / ((D1 / D2) / H4*(H2+H3)), wherein (D1 / D2) / H4 reflects the relationship between the inner diameter and the height of the compression cavity 311 of the cylinder 310 and the inner diameter of the roller 320, and to some extent reflects the size of the refrigerant compression amount of the cylinder 310. Generally, the upper end surface of the core 211 of the stator 210 is coplanar with the upper end surface of the rotor 220 or has a small height difference, and H2+H3 reflects the height position of the motor assembly 200 and the pump body assembly 300 in the main shell 110 to some extent.

[0038] With reference to FIG. 1, it can be understood that, on the one hand, under the premise that the height of the shell 100 and the refrigerant compression amount of the cylinder 310 are determined, that is, the values of H1 and (D1 / D2) / H4 are determined, if H1 / ((D1 / D2) / H4*(H2+H3))<0.8, the value of H2+H3 is large, and generally, the relative position of the motor assembly 200 and the pump body assembly 300 is determined, so the value of H2 is large, which makes the value of H5 large, the space of the exhaust cavity 150 is large, the exhaust resistance is large, which affects the refrigerant discharge, causes the compression amount of the compressor to decrease, and affects the refrigeration effect and energy efficiency; and the increase of the space of the exhaust cavity 150 can reduce the refrigeration oil taken out by the refrigerant, which can reduce the oil discharge amount to a certain extent. If H1 / ((D1 / D2) / H4*(H2+H3))>1.2, the value of H2+H3 is small, and generally, the relative position of the motor assembly 200 and the pump body assembly 300 is determined, so the value of H2 is small, which makes the value of H5 small, the space of the exhaust cavity 150 is small, which is beneficial to increase the refrigerant compression amount, but the refrigerant is more likely to take out the refrigeration oil, which causes the oil discharge amount to increase, and affects the reliability of the compressor.

[0039] With reference to FIG. 1, it can be understood that, on the other hand, under the premise that the height of the shell 100 and the installation height of the pump body assembly 300 are determined, that is, the values of H1 and H2+H3 are determined, if H1 / ((D1 / D2) / H4*(H2+H3))<0.8, the value of (D1 / D2) / H4 is large, and generally, the inner diameter of the main shell 110 is determined, which makes the inner diameters of the cylinder 310 and the roller 320 basically determined, so the value of H4 is small, the refrigerant compression amount decreases, and H3 decreases and H2 increases, which makes the space of the exhaust cavity 150 large, the oil discharge amount decreases, but causes the compression amount of the compressor to decrease seriously. If H1 / ((D1 / D2) / H4*(H2+H3))>1.2, the value of (D1 / D2) / H4 is small, and generally, the inner diameter of the main shell 110 is determined, which makes the inner diameters of the cylinder 310 and the roller 320 basically determined, so the value of H4 is large, the refrigerant compression amount increases, and H3 increases and H2 decreases, which makes the space of the exhaust cavity 150 small, which is beneficial to increase the refrigerant compression amount, but the refrigerant is more likely to take out the refrigeration oil, which causes the oil discharge amount to increase, and affects the reliability of the compressor.

[0040] Therefore, 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.2, for example, the value of (H1*D2*H4) / (D1*(H2+H3)) is 0.8, 0.9, 1, 1.1 or 1.2, etc., which makes the size of the cylinder 310 and the size of the exhaust cavity 150 in a proper range, so as to take into account the refrigerant compression amount and the oil discharge amount of the rotary compressor, which makes the refrigerant compression amount of the compressor meet the refrigeration amount requirement of the refrigeration equipment, improves the refrigeration effect and energy efficiency, at the same time, reduces the oil discharge amount of the compressor, and improves the reliability.

[0041] Referring to FIG. 1, it can be understood that the minimum distance H5 between the upper end surface of the stator 210 (i.e., the upper end surface of the wire package 212) and the upper end surface of the first housing 120 and the height H1 of the outer shell 100 satisfy: 0.2≤H5 / H1≤0.4. That is, the size of the exhaust cavity 150 is limited according to the height of the outer shell 100. If H5 / H1<0.2, under the premise that the height of the outer shell 100 is determined, the value of H5 is smaller, the space of the exhaust cavity 150 is reduced, which is beneficial to increase the refrigerant displacement, but will cause the oil discharge amount to increase, affecting the reliability of the compressor; if H5 / H1>0.4, the value of H5 is larger, the space of the exhaust cavity 150 is increased, which is beneficial to reduce the oil discharge amount, but the exhaust resistance is larger and affects the refrigerant discharge, resulting in the displacement of the compressor to decrease, affecting the refrigeration effect and energy efficiency. Therefore, 0.2≤H5 / H1≤0.4, for example, the value of H5 / H1 is 0.2, 0.3 or 0.4, etc., the size of the exhaust cavity 150 is further limited according to the height of the outer shell 100, so that the size of the exhaust cavity 150 is in a more appropriate range, the size of the exhaust cavity 150 is more accurate, so that the refrigerant displacement of the compressor can meet the refrigeration capacity requirement of the refrigeration equipment, improve the refrigeration effect and energy efficiency, at the same time, reduce the oil discharge amount of the compressor, improve the reliability.

[0042] As shown in FIG. 3 and FIG. 4, it can be understood that for a rotary compressor with high rotation speed, for example, a rotary compressor with a rotation frequency higher than 150 Hz, a large amount of refrigeration oil is transported upward through the oil supply channel 420 during high-speed operation, and a large amount of refrigeration oil is output from the upper end of the oil supply channel 420 to the exhaust cavity 150, which can cause the refrigerant to carry a large amount of refrigeration oil, resulting in an increase in oil discharge. Therefore, the shaft neck portion 331 of the first bearing 330 is provided with a first oil discharge hole 332, which penetrates the inner and outer peripheral walls of the shaft neck portion 331 in the radial direction of the first bearing 330, so that the two ends of the first oil discharge hole 332 are respectively connected to the outer peripheral space of the shaft neck portion 331 and the gap between the shaft neck portion 331 and the crankshaft 400. The crankshaft 400 is provided with a second oil discharge hole 430, which penetrates the outer peripheral wall of the crankshaft 400 and the inner peripheral wall of the oil supply channel 420 in the radial direction, so that the two ends of the second oil discharge hole 430 are respectively connected to the oil supply channel 420 and the gap between the shaft neck portion 331 and the crankshaft 400. The cross sections of the first oil discharge hole 332 and the second oil discharge hole 430 are circular, which is convenient for processing, and the center lines of the first oil discharge hole 332 and the second oil discharge hole 430 are perpendicular to the height direction of the shell 100 and located at the same height position. Therefore, when a large amount of refrigeration oil is transported upward through the oil supply channel 420, part of the refrigeration oil will flow through the second oil discharge hole 430 to the gap between the shaft neck portion 331 and the crankshaft 400, and the refrigeration oil will be discharged to the outer peripheral space of the first bearing 330 through the first oil discharge hole 332, thereby directly flowing back to the oil pool 140, thereby reducing the amount of refrigeration oil discharged from the upper end of the oil supply channel 420 and effectively reducing the oil discharge. Since the center lines of the first oil discharge hole 332 and the second oil discharge hole 430 are perpendicular to the height direction of the shell 100 and located at the same height position, during rotation of the crankshaft 400, the refrigeration oil flowing out through the second oil discharge hole 430 is more likely to enter the first oil discharge hole 332, thereby accelerating the discharge of refrigeration oil and facilitating the reduction of oil discharge.

[0043] It can be understood that the inner diameter of the first oil discharge hole 332 is greater than or equal to the inner diameter of the second oil discharge hole 430. In the present embodiment, the inner diameter of the first oil discharge hole 332 is equal to the inner diameter of the second oil discharge hole 430, so that the maximum allowable flow rate of the first oil discharge hole 332 is equal to the maximum allowable flow rate of the second oil discharge hole 430, and during rotation of the crankshaft 400, the refrigeration oil flowing out through the second oil discharge hole 430 is more likely to enter the first oil discharge hole 332, thereby accelerating the discharge of refrigeration oil and facilitating the reduction of oil discharge.

[0044] It can be understood that in other embodiments, the inner diameter of the first oil discharge hole 332 can be greater than the inner diameter of the second oil discharge hole 430, so that the maximum allowable flow rate of the first oil discharge hole 332 is greater than the maximum allowable flow rate of the second oil discharge hole 430, in order to facilitate the rapid discharge of refrigeration oil and thereby facilitate the reduction of oil discharge.

[0045] Referring to FIGS. 3 and 4, it can be understood that the number of the first oil discharge holes 332 and the number of the second oil discharge holes 430 can be multiple, and generally, the number of the first oil discharge holes 332 is equal to the number of the second oil discharge holes 430. The multiple first oil discharge holes 332 can be arranged at any position of the journal portion 331 of the first bearing 330, for example, arranged at intervals in the circumferential direction or arranged at intervals in the axial direction, and the height positions of the center lines of the multiple second oil discharge holes 430 correspond to the height positions of the center lines of the multiple first oil discharge holes 332 one by one. By arranging the multiple first oil discharge holes 332 and the multiple second oil discharge holes 430, the amount of refrigeration oil discharged through the first oil discharge holes 332 and the second oil discharge holes 430 can be increased when the rotary compressor is operated at a high speed, which is beneficial to reduce the oil discharge amount, and the multiple first oil discharge holes 332 arranged at intervals can ensure the structural strength of the first bearing 330.

[0046] It can be understood that the inner diameters of the first oil discharge holes 332 and the second oil discharge holes 430 are less than or equal to 1 mm, which avoids affecting the structural strength of the first bearing 330 and the crankshaft 400, and at the same time, avoids affecting the lubrication and heat dissipation performance of the compressor due to too large oil discharge amount of the first oil discharge holes 332 and the second oil discharge holes 430, which is beneficial to improve the reliability.

[0047] Referring to FIGS. 2 and 3, it can be understood that in order to improve the oil supply capacity, the inner peripheral wall of the journal portion 331 of the first bearing 330 is further provided with a spiral oil groove 333, the cross section of the spiral oil groove 333 is substantially fan-shaped, and the spiral oil groove 333 extends along a spiral line from the upper end surface of the first bearing 330 to the lower end surface of the first bearing 330. Therefore, during the rotation of the crankshaft 400, the refrigeration oil can be transported upward along the spiral oil groove 333 to improve the lubrication between the first bearing 330 and the crankshaft 400. The multiple first oil discharge holes 332 are staggered with the spiral oil groove 333, that is, the positions of the first oil discharge holes 332 do not coincide with the positions of the spiral oil groove 333, so as to avoid affecting the lubrication performance between the first bearing 330 and the crankshaft 400 due to the refrigeration oil in the spiral oil groove 333 being discharged through the first oil discharge holes 332, and to improve the reliability.

[0048] Referring to FIGS. 2 and 5, it can be understood that the pump body assembly 300 further comprises an oil baffle 350, specifically, the oil baffle 350 comprises a bottom plate 351 and a side plate 352, wherein the bottom plate 351 is substantially annular and is provided with a through hole 353 in the middle, the bottom plate 351 is perpendicular to the central axis of the crankshaft 400, and the side plate 352 is connected to the periphery of the bottom plate 351 and extends upward, so that the oil baffle 350 has an open upward basin structure. The bottom plate 351 is sleeved on the journal portion 331 of the first bearing 330 through the through hole 353 and is fixedly connected with the journal portion 331, for example, the bottom plate 351 is welded and fixed on the journal portion 331, or the bottom plate 351 is threadedly connected with the journal portion 331, or the bottom plate 351 is adhesively connected with the journal portion 331, the connection is stable and reliable, and the oil baffle 350 is prevented from falling off during the operation of the compressor. In the height direction of the shell 100, the bottom plate 351 is located above the exhaust port 341 of the muffler 340 and below the lowermost first oil drain hole 332, and the bottom plate 351 blocks the exhaust port 341, that is, the projection of the exhaust port 341 falls on the bottom plate 351 in the up-down direction. Therefore, the refrigeration oil discharged from the first oil drain hole 332 can be collected by the oil baffle 350, the refrigeration oil discharged from the first oil drain hole 332 can be prevented from flowing to the exhaust port 341 and flowing into the muffler 340, so as to avoid the problem of blocked exhaust, and the amount of refrigeration oil carried by the refrigerant can be reduced, and the oil discharge amount can be reduced.

[0049] Referring to FIGS. 2 and 5, it can be understood that the bottom plate 351 is further provided with a plurality of third oil drain holes 354, the plurality of third oil drain holes 354 are arranged at intervals in the circumferential direction of the crankshaft 400, and in the radial direction of the crankshaft 400, the plurality of third oil drain holes 354 are arranged staggered with the exhaust port 341. Therefore, the refrigeration oil in the oil baffle 350 can be discharged in time through the third oil drain holes 354 and flow back to the oil sump 140, the reliability is improved, and the refrigeration oil discharged from the third oil drain holes 354 can be prevented from flowing into the muffler 340 through the exhaust port 341 and affecting the exhaust.

[0050] Of course, it can be understood that the bottom plate 351 can also not be provided with the third oil drain holes 354, and the refrigeration oil in the oil baffle 350 is discharged from the upper end opening of the oil baffle 350. The oil baffle 350 can also be an annular plate, and the refrigeration oil is discharged from the periphery of the annular plate.

[0051] It can be understood that in other embodiments, the bottom plate 351 is higher at the end close to the crankshaft 400 than at the end away from the crankshaft 400, that is, the inner edge of the bottom plate 351 is higher than the outer edge of the bottom plate 351, that is, the shape of the bottom plate 351 is the same as the side surface shape of a circular truncated cone with a small upper end and a large lower end, and the third oil drain hole 354 is located at the end of the bottom plate 351 away from the crankshaft 400. Therefore, the bottom plate 351 is arranged to be inclined so that the refrigerant oil in the oil retaining member 350 flows quickly downward and is discharged through the third oil drain hole 354, facilitating the return of the refrigerant oil to the oil sump 140, and improving the reliability.

[0052] Of course, it can be understood that if the oil retaining member 350 is a ring-shaped plate, the shape of the ring-shaped plate can also be set to be the same as the side surface shape of a circular truncated cone with a small upper end and a large lower end, that is, the ring-shaped plate is arranged to be inclined so that the refrigerant oil quickly returns to the oil sump 140.

[0053] The refrigeration equipment of the second aspect embodiment of the present application comprises the rotary compressor of the first aspect embodiment of the present application.

[0054] The refrigeration equipment adopts all the technical solutions of the rotary compressor of the above embodiments, and therefore at least has all the beneficial effects brought by the technical solutions of the above embodiments.

[0055] The above describes some embodiments of the present application in combination with the drawings, but the present application is not limited to the above embodiments, and various changes can be made within the knowledge range of ordinary skilled in the art without departing from the purpose of the present application.

Claims

1. A rotary compressor, comprising: a housing comprising a main housing, a first housing and a second housing, the first housing being mounted to an upper end of the main housing, and the second housing being mounted to a lower end of the main housing; a motor assembly comprising a stator and a rotor, the stator being fixedly mounted in the main housing, and the rotor being rotatably arranged in a bore of the stator; a pump body assembly comprising a cylinder and a roller, the cylinder being mounted in the main housing, the cylinder being provided with a compression chamber, and the roller being rotatably arranged in the compression chamber; and a crankshaft fixedly connected with the rotor, the crankshaft comprising an eccentric portion, the eccentric portion being rotatably matched with the roller; wherein an inner diameter of the cylinder is D1, an inner diameter of the roller is D2, a height of the housing is H1, along the height direction of the housing, a minimum distance between an upper end surface of the stator and an upper end surface of the main housing is H2, a maximum distance between an upper end surface of the rotor and a lower end surface of the cylinder is H3, and a maximum height of the cylinder is H4, and the following condition is satisfied: 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.

2. Along the height direction, a minimum distance between the upper end surface of the stator and an upper end surface of the first housing is H5, and the following condition is satisfied: 0.2≤H5 / H1≤0.

4. The pump body assembly further comprises a first bearing, the first bearing being mounted to a side of the cylinder facing the motor assembly, the first bearing comprising a journal portion arranged around an outer periphery of the crankshaft, the journal portion being provided with a first oil drain hole, the first oil drain hole penetrating an inner peripheral wall and an outer peripheral wall of the journal portion, the crankshaft being provided with an oil supply channel and a second oil drain hole, the oil supply channel penetrating upper and lower ends of the crankshaft along the height direction, the second oil drain hole penetrating the outer peripheral wall of the crankshaft and an inner peripheral wall of the oil supply channel, and two ends of the second oil drain hole being respectively communicated with the oil supply channel and a gap between the journal portion and the crankshaft. Center lines of the first oil drain hole and the second oil drain hole are both perpendicular to the height direction and located at the same height position, and an inner diameter of the first oil drain hole is greater than or equal to an inner diameter of the second oil drain hole. The number of the first oil drain hole and the number of the second oil drain hole are both plural, and the height positions of the plural first oil drain holes and the plural second oil drain holes are one-to-one corresponding. The inner peripheral wall of the first bearing is further provided with a spiral oil groove, the spiral oil groove extending from an upper end surface of the first bearing to a lower end surface of the first bearing, and the first oil drain hole is arranged staggered with the spiral oil groove. The pump body assembly further comprises a muffler and an oil blocking member, the muffler being sleeved around an outer periphery of the first bearing and being provided with an exhaust port, the oil blocking member being mounted to the first bearing, and along the height direction, the oil blocking member is located between the muffler and a lowermost first oil drain hole, and the oil blocking member blocks the exhaust port.

2. The rotary compressor of claim 1, wherein, ​ 3. The rotary compressor of claim 1 or 2, wherein, ​ 4. The rotary compressor of claim 3, wherein, ​ 5. The rotary compressor of claim 3 or 4, wherein, ​ 6. The rotary compressor according to any one of claims 3 to 5, wherein ​ 7. The rotary compressor according to any one of claims 3 to 6, wherein ​ 8. The rotary compressor of claim 7, wherein, The oil blocking piece comprises a bottom plate and a side plate, the bottom plate is provided with a through hole and is sleeved on the first bearing, the side plate is connected to the periphery of the bottom plate and extends upward, the bottom plate is provided with a third oil drain hole, and the third oil drain hole is arranged in the radial direction of the crankshaft and is staggered with the exhaust port.

9. The rotary compressor of claim 8, wherein, The end of the bottom plate close to the crankshaft is higher than the end of the bottom plate away from the crankshaft, and the third oil drain hole is located at the end of the bottom plate away from the crankshaft.

10. A refrigeration apparatus comprising the rotary compressor according to any one of claims 1 to 9.

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