Rotary compressor and refrigeration equipment

Abstract

The utility model discloses a rotary compressor and refrigeration equipment, the rotary compressor comprises a shell, a motor assembly, a pump body assembly and a crankshaft, the shell comprises a main shell, a first shell and a second shell, and the first shell is installed at the upper end of the main shell; the motor assembly comprises a stator and a rotor; the pump body assembly comprises an air cylinder and a roller. The crankshaft is fixedly connected with the rotor and is provided with an eccentric part in running fit with the roller; wherein the inner diameter of the air cylinder is D1, the inner diameter of the roller is D2, the height of the shell is H1, the minimum distance between the upper end face of the iron core of the stator and the upper end face of the main shell is H2 in the height direction of the shell, the maximum distance between the upper end face of the rotor and the lower end face of the air cylinder is H3, the maximum height of the air cylinder is H4, and (H1 * D2 * H4) / (D1 * (H2 + H3)) is larger than or equal to 0.8 and smaller than or equal to 1.2. According to the rotary compressor, the oil output can be reduced, the oil content in a refrigerant is reduced, and the reliability is improved.

Description

Technical Field

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

[0002] During the operation of the compressor, the crankshaft rotates and the refrigerant oil in the oil pool is transported upward to provide lubrication and heat dissipation for the moving parts inside the compressor. However, when the compressor is running at high speed, a large amount of refrigerant oil is discharged from the oil outlet on the top of the crankshaft, and part of the refrigerant oil will be discharged into the refrigeration system of the refrigeration equipment in the form of gas along with the high-pressure refrigerant, resulting in an increase in the amount of oil discharged, a decrease in the amount of refrigerant oil inside the compressor, and a decrease in reliability. In addition, the high-pressure refrigerant contains a large amount of refrigerant oil, which will lead to a decrease in refrigeration capacity. 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 rotary compressor, which can reduce the oil discharge amount, reduce the oil content in the refrigerant, and improve reliability.

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

[0005] According to the rotary compressor of the first embodiment of the utility model, the housing includes a main housing, a first housing and a second housing, wherein the first housing is mounted on the upper end of the main housing and the second housing is mounted on the lower end of the main housing; a motor assembly includes a stator and a rotor, wherein the stator is fixedly mounted in the main housing and the rotor is rotatably arranged in the inner hole of the stator; a pump body assembly includes a cylinder and a roller, wherein the cylinder is mounted in the main housing and the cylinder is provided with a compression chamber and the roller is rotatably arranged in the compression chamber; a crankshaft is connected to the rotor The stator and the roller are fixedly connected, the crankshaft includes an eccentric portion, and the eccentric portion is rotatably matched with the roller; wherein the inner diameter of the cylinder is D1, the inner diameter of the roller is D2, the height of the shell is H1, and along the height direction of the shell, the minimum distance between the upper end surface of the iron core of the stator and the upper end surface of the main shell is H2, 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, satisfying: 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.2.

[0006] The rotary compressor according to the first aspect of the utility model has at least the following beneficial effects: combined with the size of the cylinder and the roller, wherein the size of the cylinder and the roller reflects the refrigerant compression of the pump body assembly to a certain extent, by limiting the overall height of the casing and the installation height of the stator and the installation height of the rotor to 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.2, the installation height position of the stator and the rotor in the casing is appropriate to ensure that the size of the space above the motor assembly in the casing is appropriate. Combined with the refrigerant compression, it is possible to avoid the problem of large exhaust resistance and reduced refrigerant displacement caused by excessive space above the motor assembly, and at the same time avoid the problem of increased oil discharge and reliability caused by too small space above the motor assembly, thereby effectively reducing the oil discharge and ensuring the refrigerant displacement of the compressor.

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

[0008] According to some embodiments of the utility model, the pump body assembly also includes a first bearing, which is installed on the side of the cylinder facing the motor assembly, and the first bearing includes a journal neck arranged around the outer periphery of the crankshaft, and the journal neck is provided with a first oil drain hole, and the first oil drain hole passes through the inner circumferential wall and the outer circumferential wall of the journal neck, and the crankshaft is provided with an oil supply channel and a second oil drain hole, and the oil supply channel passes through the upper and lower ends of the crankshaft along the height direction, and the second oil drain hole passes through the outer circumferential wall of the crankshaft and the inner circumferential wall of the oil supply channel, and the two ends of the second oil drain hole are respectively connected to the oil supply channel and the gap between the journal neck and the crankshaft.

[0009] According to some embodiments of the present invention, the center line of the first oil drain hole and the center line of the second oil drain hole 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 invention, the number of the first oil drain holes and the number of the second oil drain holes are both plural, and the height positions of the plurality of the first oil drain holes and the plurality of the second oil drain holes correspond one to one.

[0011] According to some embodiments of the utility model, the inner circumferential wall of the first bearing is further provided with a spiral oil groove, the spiral oil groove extends from the upper end surface of the first bearing to the lower end surface of the first bearing, and the first oil drain hole and the spiral oil groove are staggered.

[0012] According to some embodiments of the utility model, the pump body assembly also includes a muffler and an oil baffle, the muffler is sleeved on the outer periphery of the first bearing and is provided with an exhaust port, the oil baffle is installed on the first bearing, and along the height direction, the oil baffle is located between the muffler and the first oil drain hole at the bottom, and the oil baffle blocks the exhaust port.

[0013] According to some embodiments of the utility model, the oil baffle 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 along the radial direction of the crankshaft, the third oil drain hole is staggered with the exhaust port.

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

[0015] The refrigeration device according to the second embodiment of the utility model includes the rotary compressor of the first embodiment of the utility model.

[0016] The refrigeration equipment according to the embodiment of the second aspect of the utility model has at least the following beneficial effects: since the refrigeration equipment adopts the above-mentioned rotary compressor, combined with the dimensions of the cylinder and the roller, wherein the dimensions of the cylinder and the roller reflect the refrigerant compression amount of the pump body assembly to a certain extent, by limiting the overall height of the shell and the installation height of the stator and the installation height of the rotor to 0.8≤H1 / ((D1 / D2) / H4*(H2+H3))≤1.2, the installation height position of the stator and the rotor in the shell is appropriate to ensure that the size of the space above the motor assembly in the shell is appropriate, and combined with the refrigerant compression amount, it is possible to avoid the problem of large exhaust resistance and reduced refrigerant displacement caused by excessive space above the motor assembly, and at the same time avoid the problem of increased oil discharge and reliability caused by too small space above the motor assembly, thereby effectively reducing the oil discharge amount and ensuring the refrigerant displacement of the compressor, thereby ensuring the refrigeration capacity of the refrigeration equipment.

[0017] 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

[0018] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0019] Figure 1 is a cross-sectional view of a rotary compressor in an embodiment of the utility model;

[0020] Figure 2 yes Figure 1 A in the enlarged view;

[0021] Figure 3 This is a schematic diagram of the structure of the first bearing in an embodiment of the utility model;

[0022] Figure 4 It is a partial schematic diagram of a crankshaft in an embodiment of the utility model;

[0023] Figure 5 It is a structural schematic diagram of the oil retaining member in the embodiment of the utility model.

[0024] Reference numerals:

[0025] Shell 100; main shell 110; first shell 120; exhaust pipe 121; second shell 130; oil pool 140; exhaust chamber 150;

[0026] Motor assembly 200; stator 210; iron core 211; coil 212; rotor 220;

[0027] Pump body assembly 300; cylinder 310; compression chamber 311; air inlet 312; roller 320; first bearing 330; journal 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 360; second bearing 370;

[0028] Crankshaft 400; eccentric portion 410; oil supply passage 420; second oil drain hole 430;

[0029] Liquid reservoir 500; air intake pipe 510. DETAILED DESCRIPTION

[0030] 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.

[0031] In the description of the present invention, it should be understood that descriptions involving orientation, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations 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.

[0032] In the description of the present utility model, "several" means one or more, "more" means more than two, "greater than", "less than", "exceed" etc. are understood to exclude the number itself, and "above", "below", "within" etc. are understood to include the number itself. If there is a description of "first" or "second", it is only used 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.

[0033] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, assembling, and matching 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.

[0034] Reference Figures 1 to 5 As shown, the first embodiment of the utility model provides a rotary compressor, which is applied to a refrigeration device, which may be a refrigerator, an air conditioner or a water dispenser, etc. The rotary compressor is used to compress the refrigerant and transport it to the refrigeration system of the refrigeration device, so that the refrigeration system can use the refrigerant to achieve heat exchange and refrigeration.

[0035] Reference Figure 1 As shown, it can be understood that the rotary compressor includes a housing 100, a motor assembly 200, a pump assembly 300 and a crankshaft 400. Specifically, the housing 100 is a vertically arranged columnar structure and has a cavity. The housing 100 includes a main housing 110, a first housing 120 and a second housing 130, wherein the main housing 110 is a cylindrical structure, the first housing 120 is mounted on the upper end of the main housing 110, and the second housing 130 is mounted on the lower end of the main housing 110. The first housing 120 and the main housing 110, and the second housing 130 and the main housing 110 are fixed by welding. Generally speaking, an exhaust pipe 121 is provided at the upper end of the first housing 120, and the exhaust pipe 121 is used to connect to the refrigeration system so that the high-temperature and high-pressure refrigerant in the housing 100 enters the refrigeration system through the exhaust pipe 121. An oil pool 140 is formed at the lower portion of the main shell 110 and the inner space of the second shell 130, that is, the oil pool 140 is located at the bottom of the housing 100, and the oil pool 140 is used to store refrigeration oil to provide lubrication, heat dissipation and sealing during the operation of the rotary compressor.

[0036] Reference Figure 1As shown, it can be understood that the motor assembly 200 is installed in the housing 100. Specifically, the motor assembly 200 includes a stator 210 and a rotor 220. Generally speaking, the stator 210 is composed of an iron core 211 and a coil 212 wound around the iron core 211. The stator 210 is fixedly installed on the inner circumferential wall of the main housing 110 by shrink fitting, that is, the iron core 211 is fixedly connected to the inner circumferential wall of the main housing 110. The middle of the stator 210 has an inner hole that passes through in the up-down direction, and the rotor 220 is rotatably installed in the inner hole of the stator 210. It is easy to understand that the motor assembly 200 and the first housing 120 have a certain distance in the up-down direction. In the up-down direction, the space between the motor assembly 200 and the inner wall of the first housing 120 is defined as the exhaust chamber 150, that is, the exhaust chamber 150 is the space located above the motor assembly 200 in the housing 100.

[0037] Reference Figure 1 and Figure 2 As shown, it can be understood that the pump body assembly 300 is installed in the housing 100 and is located below the motor assembly 200. Specifically, the pump body assembly 300 includes a cylinder 310 and a roller 320. In this embodiment, the number of cylinders 310 and rollers 320 are two and one-to-one corresponding. The two cylinders 310 are arranged at intervals in the up and down directions, and the two rollers 320 are correspondingly rotatably installed in the compression chambers 311 of the two cylinders 310 to compress the refrigerant. The pump body assembly 300 also includes a first bearing 330, a muffler 340, a second bearing 370 and a partition 360, wherein the partition 360 is sandwiched 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 shaft neck 331, the second bearing 370 is installed on the lower side of the lower cylinder 310, the muffler 340 is roughly a cover structure and is installed on the upper side of the first bearing 330, and the muffler 340 is sleeved on the outer periphery of the shaft neck 331 of the first bearing 330, the inner peripheral wall of the muffler 340 and the outer peripheral wall of the shaft neck 331 of the first bearing 330 are spaced apart and define 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 360 and the second bearing 370 are connected as a whole by bolts, and the first bearing 330 is fixed to the inner peripheral wall of the main housing 110 by welding, so that the pump body assembly 300 is fixedly connected to the housing 100. It is easy to understand that the rotary compressor also includes a liquid reservoir 500 located on one side of the housing 100, and the cylinder 310 is provided with an air inlet 312, and the air inlet 312 is connected to the liquid reservoir 500 through an air inlet pipe 510, so that the gaseous refrigerant in the liquid reservoir 500 can enter the cylinder 310 to compress the refrigerant.

[0038] Of course, it is understood that in other embodiments, the number of the cylinder 310 and the roller 320 can be one, and in this case, the pump body assembly 300 does not include the partition 360. It is easy to understand that the pump body assembly 300 can be fixedly connected to the housing 100 by fixing the cylinder 310 to the main housing 110 or by connecting the second bearing 370 to the main housing 110, which will not be described in detail here.

[0039] Reference Figure 1 As shown, it can be understood that the crankshaft 400 is arranged in the up-down direction, the upper part of the crankshaft 400 is penetrated by the rotor 220 and fixedly connected with the rotor 220, and the lower part of the crankshaft 400 is sequentially penetrated by the first bearing 330, the two cylinders 310 and the partition 360, and the second bearing 370. At this time, the journal 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 journal 331. The lower part of the crankshaft 400 is provided with two eccentric parts 410 arranged at intervals in the up-down direction, and the two eccentric parts 410 are respectively rotatably matched with the two rollers 320. Therefore, the rotor 220 can drive the two rollers 320 to rotate in the two compression chambers 311 through the crankshaft 400 to achieve the compression of the refrigerant.

[0040] Reference Figure 1 As shown, it can be understood that an oil supply channel 420 is also provided at the center of the crankshaft 400. The oil supply channel 420 penetrates 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 communicated with the oil pool 140, and the upper end is communicated with the exhaust chamber 150. Generally speaking, an oiling blade is provided on the inner peripheral wall of the lower end of the oil supply channel 420. When the crankshaft 400 rotates, the oiling blade can drive the refrigeration oil in the oil pool 140 to be transported upward through the oil supply channel 420. After the refrigeration oil is discharged 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 housing 100 under the action of weight. In this way, the circulation is realized to provide lubrication and heat dissipation for the moving components in the housing 100.

[0041] Reference Figure 1 As shown, 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 in which the roller 320 cooperates with the eccentric part 410 is D2.

[0042] Reference Figure 1As shown, it can be understood that the height of the housing 100 is defined as H1, that is, the distance between the upper end surface of the first housing 120 and the lower end surface of the second housing 130 in the vertical direction is H1; along the height direction of the housing 100 (that is, the vertical direction), the minimum distance between the upper end surface of the iron core 211 of the stator 210 and the upper end surface of the main housing 110 is H2, and H2 reflects the height position of the stator 210 in the main housing 110 and reflects the height of the exhaust chamber 150 to a certain extent; the upper end surface of the rotor 220 (that is, The maximum distance between the upper end surface of the rotor core corresponding to the rotor 220 and the lower end surface of the cylinder 310 located at the bottom is H3, which reflects the relative position relationship between the rotor 220 and the bottom cylinder 310; the maximum height of the cylinder 310 is H4, which is 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 (that is, the upper end surface of the coil 212) and the upper end surface of the first shell 120 is H5, which reflects the size of the exhaust chamber 150 to a certain extent.

[0043] Reference Figure 1 As shown, 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 height of the compression chamber 311 of the cylinder 310 and the inner diameter of the roller 320, and reflects the amount of refrigerant compression of the cylinder 310 to a certain extent. Generally speaking, the upper end surface of the core 211 of the stator 210 is coplanar with the upper end surface of the rotor 220 or there is 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 housing 110 to a certain extent.

[0044] Reference Figure 1As shown, 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 larger. Generally speaking, the relative position of the motor assembly 200 and the pump body assembly 300 is determined, then the value of H2 is larger, which makes the value of H5 larger, the space of the exhaust chamber 150 increases, the exhaust resistance is larger and affects the discharge of the refrigerant, resulting in a decrease in the displacement of the compressor, affecting the refrigeration effect and energy efficiency; and the increase in the space of the exhaust chamber 150 can reduce the refrigerant oil being carried out by the refrigerant, which can reduce the oil discharge to a certain extent. If H1 / ((D1 / D2) / H4*(H2+H3))>1.2, the value of H2+H3 is smaller. Generally speaking, the relative positions of the motor assembly 200 and the pump body assembly 300 are determined, then the value of H2 is smaller, which makes the value of H5 smaller. The space of the exhaust chamber 150 is reduced, which is beneficial to increase the refrigerant displacement, but the refrigerant is more likely to bring out the refrigerant oil, resulting in an increase in the oil discharge volume, affecting the reliability of the compressor.

[0045] Reference Figure 1 As shown, it can be understood that, on the other hand, under the premise that the height of the casing 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 relatively large. Generally speaking, the inner diameter of the main shell 110 is determined, so that the inner diameters of the cylinder 310 and the roller 320 are basically determined, then the value of H4 is relatively small, the refrigerant compression amount decreases, and H3 decreases and H2 increases, then the space of the exhaust chamber 150 increases, and the oil discharge amount decreases, but it will cause the displacement of the compressor to be seriously reduced. If H1 / ((D1 / D2) / H4*(H2+H3))>1.2, the value of (D1 / D2) / H4 is small. Generally speaking, the inner diameter of the main shell 110 is determined, so that the inner diameters of the cylinder 310 and the roller 320 are basically determined. Then the value of H4 is large, the refrigerant compression amount increases, and H3 increases and H2 decreases, then the space of the exhaust chamber 150 decreases, which is beneficial to increase the refrigerant displacement, but the refrigerant is more likely to bring out the refrigerant oil, resulting in an increase in the oil discharge amount, affecting the reliability of the compressor.

[0046] Thus, 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., so that the size of the cylinder 310 and the size of the exhaust chamber 150 are within an appropriate range, taking into account the refrigerant displacement and oil discharge of the rotary compressor, so that the refrigerant displacement of the compressor can meet the refrigeration capacity requirements of the refrigeration equipment, improve the refrigeration effect and energy efficiency, and at the same time, reduce the oil discharge of the compressor to improve reliability.

[0047] Reference Figure 1 As shown, 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 coil 212) and the upper end surface of the first shell 120 and the height H1 of the shell 100 satisfy: 0.2≤H5 / H1≤0.4. In other words, the size of the exhaust chamber 150 is limited according to the height of the shell 100. If H5 / H1<0.2, under the premise that the height of the shell 100 is determined, the value of H5 is small, then the space of the exhaust chamber 150 is reduced, which is conducive to increasing the refrigerant displacement, but it will cause an increase in the oil discharge, affecting the reliability of the compressor; if H5 / H1>0.4, the value of H5 is large, then the space of the exhaust chamber 150 is increased, which is conducive to reducing the oil discharge, but the exhaust resistance is large and affects the discharge of the refrigerant, resulting in a decrease in the displacement of the compressor, 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, and the size of the exhaust chamber 150 is further limited according to the height of the shell 100, so that the size of the exhaust chamber 150 is within a more appropriate range and the size of the exhaust chamber 150 is more precise, 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, and at the same time, reduce the oil discharge of the compressor to improve reliability.

[0048] Reference Figure 3 and Figure 4As shown, it can be understood that, for a high-speed rotary compressor, such as a rotary compressor with a rotation frequency higher than 150Hz, during high-speed operation, a large amount of refrigerant oil is transported upward through the oil supply channel 420, and a large amount of refrigerant oil is output from the upper end of the oil supply channel 420 to the exhaust chamber 150, which will cause the refrigerant to bring out a large amount of refrigerant oil, resulting in an increase in the amount of oil discharge. To this end, the shaft neck 331 of the first bearing 330 is provided with a first oil drain hole 332, and the first oil drain hole 332 penetrates the inner circumferential wall and the outer circumferential wall of the shaft neck 331 along the radial direction of the first bearing 330, so that the two ends of the first oil drain hole 332 are respectively connected to the outer circumferential space of the shaft neck 331 and the gap between the shaft neck 331 and the crankshaft 400. The crankshaft 400 is provided with the second oil drain hole 430, and the second oil drain hole 430 penetrates the outer peripheral wall of the crankshaft 400 and the inner peripheral wall of the oil supply passage 420 in the radial direction, so that the two ends of the second oil drain hole 430 are respectively connected to the oil supply passage 420 and the gap between the journal 331 and the crankshaft 400. The cross-sections of the first oil drain hole 332 and the second oil drain hole 430 are both circular, which is convenient for processing, and the center line of the first oil drain hole 332 and the center line of the second oil drain hole 430 are both perpendicular to the height direction of the housing 100 and are located at the same height position. Therefore, when a large amount of refrigerant oil is transported upward through the oil supply passage 420, part of the refrigerant oil will flow to the gap between the journal 331 and the crankshaft 400 through the second oil drain hole 430, and the part of the refrigerant oil will be discharged to the outer peripheral space of the first bearing 330 through the first oil drain hole 332, and then directly flow back to the oil pool 140, so that the amount of refrigerant oil discharged from the upper end of the oil supply passage 420 can be reduced, and the amount of oil discharge can be effectively reduced. Since the center line of the first oil drain hole 332 and the center line of the second oil drain hole 430 are both perpendicular to the height direction of the outer shell 100 and are located at the same height position, during the rotation of the crankshaft 400, the refrigerant oil flowing out through the second oil drain hole 430 is more likely to enter the first oil drain hole 332, thereby accelerating the discharge of the refrigerant oil and helping to reduce the oil discharge volume.

[0049] It is understandable that the inner diameter of the first oil drain hole 332 is greater than or equal to the inner diameter of the second oil drain hole 430. In this embodiment, the inner diameter of the first oil drain hole 332 is equal to the inner diameter of the second oil drain hole 430, so that the maximum allowable flow rate of the first oil drain hole 332 is equal to the maximum allowable flow rate of the second oil drain hole 430. During the rotation of the crankshaft 400, the refrigerant oil flowing out through the second oil drain hole 430 is more likely to enter the first oil drain hole 332, thereby accelerating the discharge of the refrigerant oil, which is conducive to reducing the amount of oil discharge.

[0050] It can be understood that in other embodiments, the inner diameter of the first oil drain hole 332 can be larger than the inner diameter of the second oil drain hole 430, so that the maximum allowable flow rate of the first oil drain hole 332 is greater than the maximum allowable flow rate of the second oil drain hole 430, so that the refrigerant oil can be discharged quickly, which is beneficial to reduce the oil discharge volume.

[0051] Reference Figure 3 and Figure 4 As shown, it can be understood that the number of the first oil drain holes 332 and the number of the second oil drain holes 430 can be multiple. Generally speaking, the number of the first oil drain holes 332 is equal to the number of the second oil drain holes 430. The multiple first oil drain holes 332 can be arranged at any position of the shaft neck 331 of the first bearing 330, such as arranged at intervals along the circumferential direction or arranged at intervals along the axial direction, and the height position of the center line of the multiple second oil drain holes 430 corresponds to the height position of the center line of the multiple first oil drain holes 332. By setting the multiple first oil drain holes 332 and the multiple second oil drain holes 430, the amount of refrigerant oil discharged through the first oil drain holes 332 and the second oil drain holes 430 can be increased when the rotary compressor runs at high speed, which is conducive to reducing the amount of oil discharge, and the multiple first oil drain holes 332 arranged at intervals can ensure the structural strength of the first bearing 330.

[0052] It is understandable that the inner diameter of the first oil drain hole 332 and the second oil drain hole 430 is less than or equal to 1 mm, so as to avoid affecting the structural strength of the first bearing 330 and the crankshaft 400. At the same time, it is prevented that the oil discharge volume of the first oil drain hole 332 and the second oil drain hole 430 is too large to affect the lubrication and heat dissipation performance of the compressor, which is conducive to improving reliability.

[0053] Reference Figure 2 and Figure 3 As shown, it can be understood that, in order to improve the oiling capacity, the inner circumferential wall of the journal 331 of the first bearing 330 is also provided with a spiral oil groove 333, the cross section of the spiral oil groove 333 is roughly fan-shaped, and the spiral oil groove 333 extends from the upper end surface of the first bearing 330 to the lower end surface of the first bearing 330 along the spiral line. Therefore, during the rotation of the crankshaft 400, the refrigeration oil can be transported upward along the spiral oil groove 333 to improve the lubricity between the first bearing 330 and the crankshaft 400. The plurality of first oil discharge holes 332 are staggered with the spiral oil groove 333, that is, the position of the first oil discharge hole 332 does not overlap with the position of the spiral oil groove 333, thereby preventing the refrigeration oil in the spiral oil groove 333 from being discharged through the first oil discharge hole 332 and affecting the lubrication performance between the first bearing 330 and the crankshaft 400, thereby improving reliability.

[0054] Reference Figure 2 and Figure 5As shown, it can be understood that the pump body assembly 300 also includes an oil retaining member 350, specifically, the oil retaining member 350 includes a bottom plate 351 and a side plate 352, wherein the bottom plate 351 is roughly annular and has 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 retaining member 350 is a basin-shaped structure with an opening upward. The bottom plate 351 is sleeved on the shaft neck 331 of the first bearing 330 through the through hole 353 and is fixedly connected to the shaft neck 331, for example, the bottom plate 351 is welded and fixed to the shaft neck 331, or the bottom plate 351 and the shaft neck 331 are threadedly connected, or the bottom plate 351 is bonded to the shaft neck 331, and the connection is stable and reliable to prevent it from falling off during the operation of the compressor. In the height direction of the housing 100, the bottom plate 351 is located above the exhaust port 341 of the muffler 340 and below the first oil drain hole 332 at the bottom, and the bottom plate 351 blocks the exhaust port 341, that is, in the up-down direction, the projection of the exhaust port 341 falls on the bottom plate 351. Therefore, the refrigerant oil discharged from the first oil drain hole 332 can be collected by the oil baffle 350, and the refrigerant oil discharged from the first oil drain hole 332 can be prevented from flowing to the exhaust port 341 and into the muffler 340 to cause exhaust obstruction, and the amount of refrigerant oil carried by the refrigerant can be reduced, thereby reducing the amount of oil discharge.

[0055] Reference Figure 2 and Figure 5 As shown, it can be understood that the bottom plate 351 is also provided with a plurality of third oil drain holes 354, which are arranged at intervals along the circumference of the crankshaft 400, and along 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 refrigerant oil in the oil retaining member 350 can be discharged through the third oil drain holes 354 in time and flow back to the oil pool 140, thereby improving reliability and preventing the refrigerant oil discharged from the third oil drain holes 354 from flowing into the muffler 340 through the exhaust port 341 and affecting exhaust.

[0056] Of course, it is understandable that the bottom plate 351 may not be provided with the third oil drain hole 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 may also be an annular plate, and the refrigeration oil is discharged from the periphery of the annular plate.

[0057] It is understandable that in other embodiments, the end of the bottom plate 351 close to the crankshaft 400 is higher than the end of the bottom plate 351 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 shape of a 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 obliquely so that the refrigerant oil in the oil baffle 350 flows downward quickly and is discharged through the third oil drain hole 354, which facilitates the refrigerant oil to flow back to the oil pool 140, which is conducive to improving reliability.

[0058] Of course, it is understandable that if the oil baffle 350 is an annular plate, the shape of the annular plate can also be set to be the same as the side shape of a cone with a small upper end and a large lower end, that is, the annular plate is arranged at an angle so that the refrigerant oil can quickly flow back to the oil pool 140.

[0059] The refrigeration device of the second embodiment of the utility model comprises the rotary compressor of the first embodiment of the utility model.

[0060] Since the refrigeration equipment adopts all the technical solutions of the rotary compressor of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment.

[0061] The embodiments of the present invention are described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A rotary compressor, characterized in that: include: The housing comprises a main housing, a first housing and a second housing, wherein the first housing is mounted on the upper end of the main housing and the second housing is mounted on the lower end of the main housing; The motor assembly comprises a stator and a rotor, wherein the stator is fixedly mounted in the main housing, and the rotor is rotatably disposed in an inner hole of the stator; A pump body assembly, comprising a cylinder and a roller, wherein the cylinder is installed in the main housing, the cylinder is provided with a compression chamber, and the roller is rotatably arranged in the compression chamber; A crankshaft, fixedly connected to the rotor, the crankshaft comprising an eccentric portion, the eccentric portion rotatably engaged with the roller; Among them, the inner diameter of the cylinder is D1, the inner diameter of the roller is D2, the height of the shell is H1, along the height direction of the shell, the minimum distance between the upper end surface of the stator core and the upper end surface of the main shell is H2, 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, satisfying: 0.8≤(H1*D2*H4) / (D1*(H2+H3))≤1.

2.

2. The rotary compressor according to claim 1, characterized in that: Along the height direction, a minimum distance between an upper end surface of the stator and an upper end surface of the first housing is H5, satisfying: 0.2≤H5 / H1≤0.

4.

3. The rotary compressor according to claim 1, characterized in that: The pump body assembly also includes a first bearing, which is installed on the side of the cylinder facing the motor assembly. The first bearing includes a journal neck arranged around the outer periphery of the crankshaft, the journal neck is provided with a first oil drain hole, the first oil drain hole passes through the inner circumferential wall and the outer circumferential wall of the journal neck, the crankshaft is provided with an oil supply channel and a second oil drain hole, the oil supply channel passes through the upper and lower ends of the crankshaft along the height direction, the second oil drain hole passes through the outer circumferential wall of the crankshaft and the inner circumferential wall of the oil supply channel, and the two ends of the second oil drain hole are respectively connected to the oil supply channel and the gap between the journal neck and the crankshaft.

4. The rotary compressor according to claim 3, characterized in that: The center line of the first oil drain hole and the center line of the second oil drain hole 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.

5. The rotary compressor according to claim 3, characterized in that: The number of the first oil drain holes and the number of the second oil drain holes are both multiple, and the height positions of the multiple first oil drain holes and the multiple second oil drain holes correspond one to one.

6. The rotary compressor according to any one of claims 3 to 5, characterized in that: The inner circumferential wall of the first bearing is further provided with a spiral oil groove, which extends from the upper end surface of the first bearing to the lower end surface of the first bearing, and the first oil drain hole and the spiral oil groove are staggered.

7. The rotary compressor according to any one of claims 3 to 5, characterized in that: The pump body assembly also includes a muffler and an oil baffle. The muffler is sleeved on the outer periphery of the first bearing and is provided with an exhaust port. The oil baffle is installed on the first bearing, and along the height direction, the oil baffle is located between the muffler and the first oil drain hole at the bottom, and the oil baffle blocks the exhaust port.

8. The rotary compressor according to claim 7, characterized in that: The oil baffle 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 along the radial direction of the crankshaft, the third oil drain hole is staggered with the exhaust port.

9. The rotary compressor according to claim 8, characterized in that: An end of the bottom plate close to the crankshaft is higher than an 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. Refrigeration equipment, characterized in that Comprising a rotary compressor as claimed in any one of claims 1 to 9.

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