Compressor and refrigeration equipment

Abstract

The compressor comprises a shell, a motor assembly, a supporting assembly and a crankshaft, the shell is provided with an inner cavity and an oil pool, the motor assembly comprises a rotor, the supporting assembly comprises a motor bearing provided with a shaft hole, the crankshaft comprises a first shaft section and a second shaft section which are connected with each other, and the second shaft section is fixedly connected with the rotor. The first shaft section penetrates through the shaft hole, the crankshaft is provided with an oil supply channel, and the oil supply channel is communicated with the oil pool; the first shaft section is provided with an oil supply hole, the two ends of the oil supply hole are communicated with the oil supply channel and the shaft hole respectively, the inner diameter of the oil supply hole is D1, the distance between the center of an outlet of the oil supply hole and the lower end face of the crankshaft is H1 in the direction of the central axis of the crankshaft, and D1 / H1 is larger than or equal to 0.008 and smaller than or equal to 0.012. According to the compressor, the oil supply amount of the matching position of the motor bearing and the crankshaft can be increased, the lubricating performance is improved, abrasion of the motor bearing and the crankshaft is reduced, and the 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] The compressor adopts a double support structure to improve the running stability. The double support structure includes a motor bearing, which is located above the motor assembly in the compressor. The kinematic pair between the motor bearing and the crankshaft is also lubricated by the refrigerant oil output through the center shaft hole of the crankshaft. However, due to the high position of the motor bearing, when the motor assembly runs at a low speed, the oil supply to the kinematic pair between the motor bearing and the crankshaft is insufficient, which will increase the wear of the motor bearing and the crankshaft and affect 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 increase the oil supply to the matching point between the motor bearing and the crankshaft, improve the lubrication performance, reduce the wear of the motor bearing and the crankshaft, and thus improve the reliability of the compressor.

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

[0005] The compressor according to the first embodiment of the utility model includes a shell, which is provided with an inner cavity and an oil pool, wherein the oil pool is located at the bottom of the inner cavity; a motor assembly, including a stator and a rotor arranged in the inner cavity, wherein the stator is connected to the shell and is arranged around the outer periphery of the rotor; a support assembly, which is located above the motor assembly, wherein the support assembly includes a bracket and a motor bearing arranged in the inner cavity, wherein the bracket is connected to the shell, and the motor bearing is mounted on the bracket and is provided with an axial hole; a crankshaft, including a first shaft section and a second shaft section connected to each other, wherein the second shaft section is fixedly connected to the rotor , the first shaft section is located above the rotor and penetrates the shaft hole, the crankshaft is provided with an oil supply channel, the oil supply channel passes through both ends of the crankshaft along the direction of the central axis of the crankshaft, and the oil supply channel is connected with the oil pool; wherein, the first shaft section is provided with an oil supply hole, one end of the oil supply hole is connected with the oil supply channel, and the other end is connected with the shaft hole, the inner diameter of the oil supply hole is D1, and along the direction of the central axis of the crankshaft, the distance between the center of the outlet of the oil supply hole and the lower end surface of the crankshaft is H1, satisfying: 0.008≤D1 / H1≤0.012.

[0006] The compressor according to the embodiment of the first aspect of the utility model has at least the following beneficial effects: by adding an oil supply hole in the first shaft section, the two ends of the oil supply hole are connected to the oil supply channel and the shaft hole respectively, so that the refrigerant oil can directly enter the shaft hole through the oil supply hole to increase the oil supply amount and improve the lubrication performance; at the same time, the inner diameter D1 of the oil supply hole and the distance H1 between the center of the outlet of the oil supply hole and the lower end surface of the crankshaft satisfy 0.008≤D1 / H1≤0.012, and the inner diameter and height position of the oil supply hole are optimized to ensure that the oil supply through the oil supply hole is sufficient, and even if the compressor runs at a low speed, the oil supply demand for the matching point of the motor bearing and the crankshaft can be met, and the oil pressure of the refrigerant oil can be guaranteed, thereby improving the lubrication performance between the motor bearing and the crankshaft, reducing the wear of the motor bearing and the crankshaft, and further improving the reliability of the compressor.

[0007] According to some embodiments of the utility model, the oil supply channel includes a first oil supply section and a second oil supply section that are interconnected, the oil supply hole is connected to the first oil supply section, the second oil supply section is located at an end of the first oil supply section away from the oil supply hole and is connected to the oil pool, the maximum inner diameter of the first oil supply section is D2, and the maximum inner diameter of the second oil supply section is D3, satisfying: D2<D3.

[0008] According to some embodiments of the present invention, the inner diameter D1 of the oil supply hole and the maximum inner diameter D2 of the first oil supply section satisfy: 0.3≤D1 / D2≤0.5.

[0009] According to some embodiments of the present invention, the maximum inner diameter D2 of the first oil supply section and the maximum inner diameter D3 of the second oil supply section satisfy: 0.5≤D2 / D3≤0.7.

[0010] According to some embodiments of the utility model, the compressor further comprises an oiling vane, which is installed in the second oil supply section and protrudes downward from the lower end surface of the crankshaft, and the lower end of the oiling vane extends into the oil pool.

[0011] According to some embodiments of the present invention, along the direction of the central axis of the crankshaft, the upper end of the oiling blade extends to the connection between the first oil supply section and the second oil supply section.

[0012] According to some embodiments of the present invention, along the direction of the central axis of the crankshaft, the distance between the center of the outlet of the oil supply hole and the lower end of the first oil supply section is H2, and the maximum height of the oiling blade is H3, satisfying: 1.5≤H2 / H3≤1.7.

[0013] According to some embodiments of the present invention, along the direction of the central axis of the crankshaft, the maximum height of the oiling blade is H3, and the distance between the lower end surface of the crankshaft and the lower end of the oiling blade is H4, satisfying: 0.15≤H4 / H3≤0.25.

[0014] According to some embodiments of the present invention, the central axis of the oil supply hole is perpendicular to the central axis of the crankshaft; or, the oil supply hole is arranged inclined upward, and one end of the oil supply hole connected to the oil supply channel is lower than the other end.

[0015] According to some embodiments of the utility model, the support assembly further includes a shaft sleeve, the shaft sleeve is installed in the shaft hole, and one end of the oil supply hole away from the oil supply channel faces the inner circumferential wall of the shaft sleeve.

[0016] The refrigeration device according to the embodiment of the second aspect of the utility model comprises the compressor of the embodiment of the first aspect of the utility model.

[0017] According to the refrigeration equipment of the embodiment of the second aspect of the utility model, there are at least the following beneficial effects: since the refrigeration equipment adopts the above-mentioned compressor, by adding an oil supply hole in the first shaft section, the two ends of the oil supply hole are connected to the oil supply channel and the shaft hole respectively, so that the refrigerant oil can directly enter the shaft hole through the oil supply hole to increase the oil supply amount and improve the lubrication performance; at the same time, the inner diameter D1 of the oil supply hole and the distance H1 between the center of the outlet of the oil supply hole and the lower end surface of the crankshaft satisfy 0.008≤D1 / H1≤0.012, and the inner diameter and height position of the oil supply hole are optimized to ensure that the oil supply through the oil supply hole is sufficient, even if the compressor runs at a low speed, the oil supply demand for the matching point of the motor bearing and the crankshaft can be met, and the oil pressure of the refrigerant oil can be guaranteed, thereby improving the lubrication performance between the motor bearing and the crankshaft, reducing the wear of the motor bearing and the crankshaft, and further improving the reliability of the compressor.

[0018] 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

[0019] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0020] Figure 1 is a front cross-sectional view of a compressor in some embodiments of the utility model;

[0021] Figure 2 is a cross-sectional view of the crankshaft and the oiling blade after assembly in some embodiments of the utility model;

[0022] Figure 3 yes Figure 1 Enlarged view of point A in the middle;

[0023] Figure 4 yes Figure 1 The enlarged view of point B in the figure;

[0024] Figure 5 It is a partial cross-sectional view of the first shaft section in some other embodiments of the utility model;

[0025] Figure 6 It is a curve diagram showing the relative oil supply rate of the oil supply hole in some embodiments of the utility model as D1 / H1 changes;

[0026] Figure 7 It is a curve diagram showing the relative oil supply rate of the oil supply hole in some embodiments of the utility model as D1 / D2 changes;

[0027] Figure 8 It is a curve diagram showing the relative oil supply rate of the oil supply hole in some embodiments of the utility model as D2 / D3 changes;

[0028] Fig. 9 It is a schematic diagram of a curve showing the relative oil supply rate of the oil supply hole changing with H4 / H3 in some embodiments of the present invention.

[0029] Reference numerals:

[0030] Shell 100; inner cavity 110; oil pool 120; exhaust pipe 130;

[0031] Motor assembly 200; stator 210; rotor 220; through hole 221;

[0032] Support assembly 300; bracket 310; motor bearing 320; shaft hole 321; shaft sleeve 330;

[0033] Pump assembly 400; crankshaft 410; first shaft section 411; second shaft section 412; oil supply passage 413; first oil supply section 4131; second oil supply section 4132; oil supply hole 414; eccentric portion 415; oiling blade 420; first cylinder 430; compression chamber 431; piston 432; air inlet 433; second cylinder 440; partition 450; first bearing 460; second bearing 470; first muffler 480; second muffler 490;

[0034] Liquid reservoir 500. DETAILED DESCRIPTION

[0035] 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.

[0036] 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.

[0037] 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.

[0038] In the description of the present utility model, 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 utility model based on the specific content of the technical solution.

[0039] As rotary compressors develop towards high speed, high efficiency and high accumulation, the operating stability of rotary compressors is particularly important. Therefore, in order to ensure the operating stability of rotary compressors, rotary compressors adopt a double support structure, that is, on the premise that the crankshaft is supported by the bearing of the pump assembly, a motor bearing is added to support the upper end of the crankshaft, thereby effectively reducing the flexural deformation of the upper end of the crankshaft, ensuring the coaxiality of the stator and rotor of the motor assembly, and thus ensuring the operating stability of the rotary compressor.

[0040] The lubrication between the motor bearing and the crankshaft is also achieved by using the refrigerant oil output from the center oil hole of the crankshaft in the oil supply system. However, due to the high position of the motor bearing, the oil supply system does not supply enough oil to the matching point between the motor bearing and the crankshaft, especially when the compressor is running at a low speed, the oil supply is even more insufficient, which will cause the wear of the motor bearing and the crankshaft to increase, affecting the reliability of the compressor.

[0041] For this purpose, refer to Figures 1 to 9 As shown, the first embodiment of the utility model provides a compressor, which is applied to refrigeration equipment. The refrigeration equipment can be a refrigerator, an air conditioner, a water dispenser, etc. The compressor compresses the refrigerant and transports it to the refrigeration system of the refrigeration equipment, so that the refrigeration system can use the refrigerant to achieve heat exchange and refrigeration.

[0042] Reference Figure 1As shown, it can be understood that the compressor is a rotary compressor. Specifically, the compressor includes a housing 100, a motor assembly 200, a support assembly 300, a pump body assembly 400 and a crankshaft 410. Among them, the housing 100 is roughly columnar and has an inner cavity 110, and the motor assembly 200, the support assembly 300 and the pump body assembly 400 are all arranged in the inner cavity 110 of the housing 100. The bottom of the inner cavity 110 stores refrigeration oil and forms an oil pool 120. During the operation of the compressor, the refrigeration oil is mainly used to provide lubrication to the motor assembly 200, the support assembly 300 and the pump body assembly 400. Of course, to a certain extent, the refrigeration oil can be used for heat dissipation and sealing (such as oil seals). The top of the housing 100 is also provided with an exhaust pipe 130 for discharging refrigerant.

[0043] Reference Figure 3 and Figure 4 As shown, it can be understood that the motor assembly 200 includes a stator 210 and a rotor 220, the stator 210 is fixedly connected to the inner peripheral wall of the housing 100 by welding or by shrink fitting, and the rotor 220 is rotatably arranged in the inner hole of the stator 210, that is, the stator 210 is arranged around the outer periphery of the rotor 220. A recess is provided on part of the outer peripheral wall of the stator 210 and a reflux channel is formed between the inner peripheral wall of the housing 100, and the reflux channel penetrates both ends of the stator 210 in the up-down direction. The rotor 220 is provided with a through hole 221, and the through hole 221 penetrates both ends of the rotor 220 in the up-down direction. The reflux channel and the through hole 221 both connect the upper space and the lower space of the motor assembly 200. The side close to the rotation axis of the rotor 220 is the inner side, and the side away from the rotation axis of the rotor 220 is the outer side. The up-down direction is the direction of the rotation axis of the rotor 220.

[0044] Reference Figure 1As shown, it can be understood that the pump assembly 400 is used to compress the refrigerant into high-temperature and high-pressure gas. The pump assembly 400 is located below the motor assembly 200. In this embodiment, the pump assembly 400 is a double-cylinder structure to increase the refrigerant compression amount. Specifically, the pump assembly 400 includes a first cylinder 430, a second cylinder 440, a partition 450, a first bearing 460, a second bearing 470, a first muffler 480, a second muffler 490 and an oiling blade 420. The first cylinder 430 and the second cylinder 440 are both welded to the wall of the housing 100. The first cylinder 430 is located above the second cylinder 440. The first cylinder 430 is provided with a compression chamber 431 and a piston 432 rotatably arranged in the compression chamber 431. The peripheral wall of the first cylinder 430 is also provided with an air inlet 433 connected to the compression chamber 431, and the air inlet 433 is used to connect to the liquid reservoir 500. The upper end surface of the first cylinder 430 is provided with an air outlet connected to the compression chamber 431, and the air outlet is used to discharge the refrigerant compressed in the compression chamber 431 to the inner cavity 110 of the housing 100. The structure of the second cylinder 440 can refer to the structure of the first cylinder 430.

[0045] Of course, the pump body assembly 400 may also be a single-cylinder structure, that is, it only includes one cylinder.

[0046] Reference Figure 1 As shown, it can be understood that the partition 450 is sandwiched between the first cylinder 430 and the second cylinder 440, the first bearing 460 is installed on the upper side of the first cylinder 430, the second bearing 470 is installed on the lower side of the second cylinder 440, the first muffler 480 is covered on the upper side of the first bearing 460, and the second muffler 490 is covered on the lower side of the second bearing 470. It is easy to understand that the first bearing 460, the first muffler 480 and the partition 450 are all provided with holes connected to the air outlet so that the compressed refrigerant can be discharged into the inner cavity 110. The first muffler 480 and the second muffler 490 can block the noise in the cylinder from being transmitted to a certain extent to reduce the operating noise of the compressor.

[0047] Reference Figure 1 and Figure 2As shown, it can be understood that the crankshaft 410 is arranged in the up-down direction, and the crankshaft 410 includes a first shaft section 411 and a second shaft section 412. The first shaft section 411 is connected to the upper end of the second shaft section 412, and the first shaft section 411 and the second shaft section 412 are coaxial. The lower part of the second shaft section 412 is sequentially penetrated through the combination of the first muffler 480 and the first bearing 460, the first cylinder 430, the partition 450, the second cylinder 440, the second bearing 470 and the second muffler 490, and the second shaft section 412 is rotatably matched with the first bearing 460 and the second bearing 470. The lower part of the second shaft section 412 has two eccentric parts 415 arranged at intervals in the up-down direction, the eccentric directions of the two eccentric parts 415 are different, and the two eccentric parts 415 are rotatably connected to the pistons 432 in the first cylinder 430 and the second cylinder 440, respectively. The upper portion of the second shaft section 412 is disposed through the rotor 220 and is fixedly connected to the rotor 220. It is easy to understand that the central axis of the crankshaft 410 coincides with the rotation axis of the rotor 220, and the rotor 220 can drive the crankshaft 410 to rotate. The first shaft section 411 is located above the rotor 220.

[0048] Reference Figure 1 and Figure 3 As shown, it can be understood that the support assembly 300 is located above the motor assembly 200. Specifically, the support assembly 300 includes a bracket 310 and a motor bearing 320. The bracket 310 is welded and fixed to the wall of the housing 100. The bracket 310 has a hollow structure so that the space above the bracket 310 is connected to the space below. The motor bearing 320 is fixedly installed on the bracket 310 by screws or bolts, and the motor bearing 320 is provided with an axial hole 321 that penetrates in the up and down direction. The first shaft section 411 is penetrated in the axial hole 321 and rotates with the motor bearing 320.

[0049] Reference Figure 1 As shown, it can be understood that, therefore, the motor bearing 320 provides support for the upper end of the crankshaft 410, and the first bearing 460 and the second bearing 470 cooperate to provide support for the lower end of the crankshaft 410, that is, a double support structure, which is beneficial to ensure the rotational stability of the crankshaft 410, thereby ensuring the coaxiality of the rotor 220 and the stator 210 of the motor assembly 200, and improving the reliability and operating stability of the compressor.

[0050] Reference Figure 1 and Figure 2As shown, it can be understood that the crankshaft 410 is provided with an oil supply channel 413 arranged in the up-down direction, and the oil supply channel 413 passes through both ends of the crankshaft 410 in the up-down direction, wherein the lower end of the oil supply channel 413 is communicated with the oil pool 120, and the upper end of the oil supply channel 413 is communicated with the top space of the inner cavity 110 of the housing 100. Generally speaking, the central axis of the oil supply channel 413 coincides with the central axis of the crankshaft 410, which is convenient for processing. The oiling blade 420 is arranged in the oil supply channel 413 and is located at the lower part of the second shaft section 412.

[0051] Reference Figure 1 and Figure 4 As shown, it can be understood that the lower end surface of the second shaft section 412 of the crankshaft 410 is flush with the lower end surface of the second bearing 470, avoiding the disadvantage that the crankshaft 410 protrudes downward from the second bearing 470 and stirs the refrigerant oil to cause eddy currents and affect the oil supply, which is beneficial to ensure the oil supply.

[0052] Reference Figure 1 As shown, it can be understood that during the operation of the compressor, the rotor 220 drives the crankshaft 410 to rotate. On the one hand, the crankshaft 410 drives the piston 432 to rotate through the eccentric portion 415 to compress the refrigerant, and the compressed refrigerant is discharged into the inner cavity 110 through the air outlet and the holes on the first bearing 460 and the first muffler 480. The mixture of the refrigerant and the refrigeration oil then flows upward to the space above the support assembly 300 through the through hole 221 on the rotor 220 and the hollow structure of the bracket 310. After oil and gas separation, the refrigerant is discharged into the refrigeration system of the refrigeration equipment through the exhaust pipe 130, and the refrigeration oil flows back to the oil well at the bottom. Pool 120; on the other hand, the crankshaft 410 drives the oiling blade 420 to rotate, and the oiling blade 420 drives the refrigerant oil in the oil pool 120 to be transported upward through the oil supply channel 413, and the refrigerant oil is output from the upper end of the oil supply channel 413, and under the action of gravity, it flows back to the oil pool 120 from the reflux channel and the gaps between components, and the cycle is repeated in this way, so that the refrigerant oil can provide lubrication for the motor bearing 320 and the crankshaft 410, between the stator 210 and the rotor 220, between the first bearing 460 and the crankshaft 410, between the second bearing 470 and the crankshaft 410, and between the piston 432 and the crankshaft 410 to reduce wear.

[0053] Reference Figures 1 to 3As shown, it can be understood that the first shaft section 411 is also provided with an oil supply hole 414, which is located on one side of the oil supply channel 413 along the radial direction of the rotor 220, and both ends of the oil supply hole 414 are open, and one end of the oil supply hole 414 is connected to the oil supply channel 413, and the other end is connected to the shaft hole 321. Therefore, during the operation of the compressor, the refrigerant oil transported upward through the oil supply channel 413 can directly enter the shaft hole 321 through the oil supply hole 414, thereby increasing the oil supply to the matching point between the crankshaft 410 and the motor bearing 320, so as to improve the lubricity between the crankshaft 410 and the motor bearing 320, reduce the wear of the crankshaft 410 and the motor bearing 320, and improve the reliability of the compressor.

[0054] Reference Figure 2 and Figure 3 As shown, it can be understood that the cross section of the oil supply hole 414 is circular, and the inner diameter of the oil supply hole 414 is defined as D1. Along the direction of the central axis of the crankshaft 410, the distance between the center of the outlet of the oil supply hole 414 and the lower end surface of the crankshaft 410 is H1. The outlet of the oil supply hole 414 is the opening of the end of the oil supply hole 414 away from the oil supply channel 413. In this embodiment, the central axis of the oil supply hole 414 is perpendicular to the central axis of the crankshaft 410. At this time, the height position of the center of the outlet of the oil supply hole 414 is equal to the height position of the central axis of the oil supply hole 414, and H1 is the distance between the central axis of the oil supply hole 414 and the lower end surface of the crankshaft 410. H1 can reflect the height position of the oil supply hole 414.

[0055] In other embodiments, if the central axis of the oil supply hole 414 is inclined relative to the central axis of the crankshaft 410, the center of the outlet of the oil supply hole 414 is the intersection of the central axis of the oil supply hole 414 and the extended surface of the outer peripheral wall of the first shaft segment 411 at the outlet of the oil supply hole 414.

[0056] Reference Figure 2 and Figure 3As shown, it can be understood that the inner diameter D1 of the oil supply hole 414 and the distance H1 between the center of the outlet of the oil supply hole 414 and the lower end surface of the crankshaft 410 satisfy: 0.008≤D1 / H1≤0.012. Since the refrigeration oil is transported upward through the oil supply channel 413, the higher the position of the oil supply hole 414, the lower the oil pressure reaching the oil supply hole 414, and a larger hole diameter is required to meet the oil supply quantity requirement. That is, the inner diameter of the oil supply hole 414 is set according to the height of the oil supply hole 414. When D1 / H1<0.008, under the premise that the height position of the oil supply hole 414 is determined, the diameter of the oil supply hole 414 will be too small, and the oil supply to the matching part of the motor bearing 320 and the crankshaft 410 will be insufficient, and it is difficult to meet the lubrication requirements; when D1 / H1>0.012, under the premise that the height position of the oil supply hole 414 is determined, the diameter of the oil supply hole 414 will be too large, and the oil pressure of the refrigeration oil output to the matching part of the motor bearing 320 and the crankshaft 410 will be too low, affecting the flow and circulation of the refrigeration oil, which is not conducive to lubrication. Therefore, making 0.008≤D1 / H1≤0.012, for example, D1 / H1 value is 0.008, 0.009, 0.01, 0.011 or 0.012, etc., can increase the oil supply to the matching part of the motor bearing 320 and the crankshaft 410 and ensure that the oil pressure of the refrigeration oil meets the lubrication requirements, thereby further improving the lubrication performance between the motor bearing 320 and the crankshaft 410.

[0057] Understandably, Figures 6 to 9 In the curve diagram, the relative oil supply rate of the oil supply hole 414 is the ratio of the actual oil supply output to the motor bearing 320 through the oil supply hole 414 to the maximum oil supply under ideal conditions. It is easy to understand that the relative oil supply rate is less than or equal to 1.

[0058] Reference Figure 6 As shown, it can be understood that when 0.008≤D1 / H1≤0.012, the relative oil supply rate of the oil supply hole 414 is maintained at 0.5 or above, and the oil supply is sufficient, which is beneficial to improving lubrication performance and reducing wear.

[0059] In this way, by adding the oil supply hole 414, the oil supply to the fitting point of the motor bearing 320 and the crankshaft 410 can be increased, and at the same time, the oil pressure of the refrigeration oil can be ensured to meet the lubrication requirements. Even if the compressor runs at a low speed, the lubrication requirements of the fitting point of the motor bearing 320 and the crankshaft 410 can be met, thereby improving the lubrication performance between the motor bearing 320 and the crankshaft 410, reducing the wear of the motor bearing 320 and the crankshaft 410, and thus improving the reliability of the compressor.

[0060] Reference Figure 3As shown, it can be understood that in this embodiment, the central axis of the oil supply hole 414 is perpendicular to the central axis of the crankshaft 410. When processing the oil supply hole 414, it is sufficient to drill along the radial direction of the crankshaft 410, which is convenient for positioning the crankshaft 410, facilitating processing, and helping to improve processing efficiency.

[0061] Reference Figure 5 As shown, it can be understood that, since the refrigeration oil is transported upward through the oil supply channel 413, in other embodiments, the oil supply hole 414 is arranged obliquely upward, and the lower end opening of the oil supply hole 414 is connected to the oil supply channel 413, and the upper end opening is connected to the shaft hole 321, that is, the end of the oil supply hole 414 connected to the oil supply channel 413 is lower than the other end. Therefore, the angle between the flow direction of the refrigeration oil in the oil supply hole 414 and the flow direction of the refrigeration oil in the oil supply channel 413 can be reduced, thereby reducing the flow resistance of the refrigeration oil, which is conducive to increasing the oil supply amount and further improving the lubrication performance.

[0062] Reference Figure 3 As shown, it can be understood that in order to further reduce the wear of the motor bearing 320, the support assembly 300 also includes a sleeve 330, which is fixedly installed in the shaft hole 321 by a shrink sleeve method and is sleeved on the first shaft section 411 of the crankshaft 410. The first shaft section 411 and the sleeve 330 are rotatably matched, so that the wear of the motor bearing 320 caused by the crankshaft 410 is transferred to the sleeve 330, which can reduce the wear of the motor bearing 320. And the end of the oil supply hole 414 away from the oil supply channel 413 opens toward the inner peripheral wall of the sleeve 330, so that the refrigerant oil output through the oil supply hole 414 can directly flow to the inner peripheral wall of the sleeve 330, so as to improve the lubrication performance between the sleeve 330 and the crankshaft 410.

[0063] Reference Figure 2As shown, it can be understood that the oil supply channel 413 includes a first oil supply section 4131 and a second oil supply section 4132, the first oil supply section 4131 is located at the upper end of the second oil supply section 4132, and the first oil supply section 4131 and the second oil supply section 4132 are coaxially arranged and connected to each other, the oil supply hole 414 is connected to the first oil supply section 4131, and the lower end of the second oil supply section 4132 is connected to the oil pool 120. Among them, the maximum inner diameter of the first oil supply section 4131 is smaller than the maximum inner diameter of the second oil supply section 4132, and the inner diameter of the first oil supply section 4131 is equal at all places. It is easy to understand that the transition section at the connection between the first oil supply section 4131 and the second oil supply section 4132 (the inner diameter decreases from the maximum inner diameter of the second oil supply section 4132 to the maximum inner diameter of the first oil supply section 4131) belongs to a part of the second oil supply section 4132, and the inner diameter of the rest of the second oil supply section 4132 is equal at all places. The oiling blade 420 is arranged in the second oil supply section 4132, and the outer diameter of the oiling blade 420 is equal to the inner diameter of the second oil supply section 4132. Therefore, when the refrigerant oil is transported upward through the oil supply channel 413, since the maximum inner diameter of the first oil supply section 4131 is smaller than the maximum inner diameter of the second oil supply section 4132, when the refrigerant oil flows from the second oil supply section 4132 to the first oil supply section 4131, the flow area is reduced, the oil pressure is increased, and the flow rate is increased, which is conducive to the upward transportation of the refrigerant oil to ensure the oil supply pressure, thereby increasing the oil supply amount and oil pressure at the matching point of the motor bearing 320 and the crankshaft 410, thereby improving the lubrication performance.

[0064] Reference Figure 2 As shown, it can be understood that the inner diameter D1 of the oil supply hole 414 and the maximum inner diameter D2 of the first oil supply section 4131 satisfy: 0.3≤D1 / D2≤0.5. Similarly, under the premise that the maximum inner diameter of the first oil supply section 4131 is determined, when D1 / D2<0.3, the diameter of the oil supply hole 414 will be too small, and the oil supply to the matching part of the motor bearing 320 and the crankshaft 410 will be insufficient, and it is difficult to meet the lubrication requirements; when D1 / D2>0.5, the diameter of the oil supply hole 414 will be too large, and the oil pressure of the refrigeration oil output to the matching part of the motor bearing 320 and the crankshaft 410 will be too low, which will affect the flow and circulation of the refrigeration oil and is not conducive to lubrication. Therefore, setting 0.3≤D1 / D2≤0.5, for example, D1 / D2 value is 0.3, 0.35, 0.4, 0.45 or 0.5, etc., can increase the oil supply to the fitting point between the motor bearing 320 and the crankshaft 410 and ensure that the oil pressure of the refrigeration oil meets the lubrication requirements, thereby further improving the lubrication performance between the motor bearing 320 and the crankshaft 410.

[0065] Reference Figure 7 As shown, it can be understood that when 0.3≤D1 / D2≤0.5, the relative oil supply rate of the oil supply hole 414 is maintained at 0.8 or above, and the oil supply is sufficient, which is beneficial to improving lubrication performance and reducing wear.

[0066] Reference Figure 2 As shown, it can be understood that the maximum inner diameter of the first oil supply section 4131 is defined as D2, and the maximum inner diameter of the second oil supply section 4132 is defined as D3. It is easy to understand that D2<D3. At the same time, the maximum inner diameter D2 of the first oil supply section 4131 and the maximum inner diameter D3 of the second oil supply section 4132 satisfy: 0.5≤D2 / D3≤0.7. Generally speaking, the inner diameter of the second oil supply section 4132 (that is, the outer diameter of the oiling blade 420) is set according to the total oil supply amount. When D2 / D3<0.5, under the premise that the inner diameter of the second oil supply section 4132 is determined, the inner diameter of the first oil supply section 4131 is too small. Although the oil pressure of the refrigerant oil in the first oil supply section 4131 increases, the flow area of ​​the first oil supply section 4131 is too small, and the oil supply is insufficient to meet the lubrication requirements between the motor bearing 320 and the crankshaft 410, resulting in aggravated wear; when D2 / D3>0.7, under the premise that the inner diameter of the second oil supply section 4132 is determined, the inner diameter of the first oil supply section 4131 is too large, and the oil pressure is too small, which is not conducive to the upward transportation of the refrigerant oil, and will affect the oil supply to the fitting point of the motor bearing 320 and the crankshaft 410, resulting in poor lubrication and aggravated wear. Therefore, setting 0.5≤D2 / D3≤0.7, for example, D2 / D3 value is 0.5, 0.55, 0.6, 0.65 or 0.7, etc., can take into account the oil supply and oil pressure in the first oil supply section 4131, so as to increase the oil supply and oil pressure at the fitting point between the motor bearing 320 and the crankshaft 410, thereby improving the lubrication performance.

[0067] Reference Figure 8 As shown, it can be understood that when 0.5≤D2 / D3≤0.7, the relative oil supply rate of the oil supply hole 414 is maintained at 0.7 or above, and the oil supply is sufficient, which is beneficial to improving lubrication performance and reducing wear.

[0068] Reference Figure 1 and Figure 2 As shown, it can be understood that in order to further increase the oil pressure and increase the oil supply, along the direction of the central axis of the crankshaft 410, the upper end of the oiling blade 420 extends to the connection between the first oil supply section 4131 and the second oil supply section 4132, and the lower end of the oiling blade 420 extends to the lower end of the second oil supply section 4132 or protrudes downward from the crankshaft 410, that is, the oiling blade 420 completely occupies the second oil supply section 4132 in the direction of the central axis of the crankshaft 410, thereby making full use of the space of the second oil supply section 4132 and increasing the height of the oiling blade 420 in the direction of the central axis of the crankshaft 410, which is beneficial to increase the oil pressure and facilitate the upward transportation of the refrigerant oil to increase the oil supply, improve the lubrication performance, and reduce wear.

[0069] It is understood that in some embodiments, the liquid level of the refrigeration oil in the oil pool 120 is higher than the upper end of the oiling blade 420. Therefore, at this time, the entire oiling blade 420 is immersed in the refrigeration oil, and increasing the height of the oiling blade 420 in the direction of the central axis of the crankshaft 410 is also conducive to directly increasing the oil supply.

[0070] Reference Figure 1 and Figure 4 As shown, it can be understood that, in this embodiment, the lower end of the oiling blade 420 protrudes downward from the crankshaft 410, and the lower end of the oiling blade 420 extends into the oil pool 120. Therefore, the height of the oiling blade 420 in the direction of the central axis of the crankshaft 410 can be further increased, and the oil pressure and oil supply can be further increased, thereby improving the lubrication performance and reducing wear.

[0071] Reference Figure 4 and Figure 5 As shown, it can be understood that, along the direction of the central axis of the crankshaft 410, the distance between the center of the outlet of the oil supply hole 414 and the lower end of the first oil supply section 4131 is defined as H2, and the maximum height of the oiling blade 420 is H3. The maximum height H3 of the oiling blade 420 is the distance between the uppermost end and the lowermost end of the oiling blade 420. The explanation of the center of the outlet of the oil supply hole 414 in the definition of H2 can refer to the explanation of the center of the outlet of the oil supply hole 414 in the definition of H1, and will not be repeated here.

[0072] Reference Figure 2 As shown, it can be understood that the distance H2 between the center of the outlet of the oil supply hole 414 and the lower end of the first oil supply section 4131 and the maximum height H3 of the oiling blade 420 satisfy: 1.5≤H2 / H3≤1.7. Generally speaking, the height position of the oil supply hole 414 is determined, that is, the value of H2+H3 is determined. When H2 / H3<1.5, the maximum height of the oiling blade 420 will be too large, the upward oil supply will increase, and the upward oil supply will be much larger than the refrigeration oil return flow. During the operation of the compressor, the liquid level of the refrigeration oil in the oil pool 120 will gradually drop, affecting the normal circulation of the refrigeration oil. After a long operation time, the lubrication performance will deteriorate and the wear will be aggravated; when H2 / H3>1.7, the maximum height of the oiling blade 420 will be too small, the oil supply will be insufficient, and the oil pressure will be low, the lubrication performance will deteriorate, and the wear will be aggravated. Therefore, setting 1.5≤H2 / H3≤1.7, for example, H2 / H3 value is 1.5, 1.55, 1.6, 1.65 or 1.7, etc., can increase the oil supply to the fitting point between the motor bearing 320 and the crankshaft 410 and increase the oil pressure, and ensure the normal circulation of the refrigerant oil, prevent the refrigerant oil level from continuously dropping and deteriorating, thereby improving the lubrication performance and reducing wear.

[0073] Reference Figure 2 and Figure 4As shown, it can be understood that, along the direction of the central axis of the crankshaft 410, the distance between the lower end face of the crankshaft 410 and the lower end of the oiling blade 420 is defined as H4, that is, H4 is the protruding height of the oiling blade 420 relative to the lower end face of the crankshaft 410, which satisfies: 0.15≤H4 / H3≤0.25. Under the premise that the installation position of the upper end of the oiling blade 420 and the maximum height H3 are determined, when H4 / H3<0.15, the protruding height of the oiling blade 420 relative to the lower end face of the crankshaft 410 is too small, the oil supply is insufficient, and the lubrication performance is affected; when H4 / H3>0.25, the protruding height of the oiling blade 420 relative to the lower end face of the crankshaft 410 is too large, which will cause the oiling blade 420 to interfere with the bottom wall of the shell 100, and the structure is unreasonable, affecting the normal operation of the compressor. Therefore, setting 0.15≤H4 / H3≤0.25, for example, H4 / H3 value is 0.15, 0.2 or 0.25, etc., can increase the oil supply to the fitting point between the motor bearing 320 and the crankshaft 410, and at the same time make the assembly relationship between the oiling blade 420 and the housing 100 reasonable, avoid interference between the oiling blade 420 and the housing 100, and ensure the normal operation of the compressor.

[0074] Reference Fig. 9 As shown, it can be understood that when 0.15≤H4 / H3≤0.25, the relative oil supply rate of the oil supply hole 414 is maintained at 0.85 or above, and the oil supply is sufficient, which is beneficial to improving lubrication performance and reducing wear.

[0075] The refrigeration device of the second embodiment of the utility model includes the compressor of the first embodiment of the utility model, which will not be described in detail here.

[0076] Since the refrigeration equipment adopts all the technical solutions of the compressor of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment.

[0077] 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 compressor, characterized in that include: A housing is provided with an inner cavity and an oil pool, wherein the oil pool is located at the bottom of the inner cavity; A motor assembly, comprising a stator and a rotor disposed in the inner cavity, wherein the stator is connected to the housing and is disposed around the outer circumference of the rotor; A support assembly is located above the motor assembly, the support assembly includes a bracket and a motor bearing arranged in the inner cavity, the bracket is connected to the housing, and the motor bearing is installed on the bracket and is provided with an axial hole; A crankshaft, comprising a first shaft section and a second shaft section connected to each other, wherein the second shaft section is fixedly connected to the rotor, the first shaft section is located above the rotor and penetrates the shaft hole, the crankshaft is provided with an oil supply passage, the oil supply passage penetrates both ends of the crankshaft along the direction of the central axis of the crankshaft, and the oil supply passage is communicated with the oil pool; Among them, the first shaft section is provided with an oil supply hole, one end of the oil supply hole is connected to the oil supply channel, and the other end is connected to the shaft hole, the inner diameter of the oil supply hole is D1, and along the direction of the central axis of the crankshaft, the distance between the center of the outlet of the oil supply hole and the lower end surface of the crankshaft is H1, satisfying: 0.008≤D1 / H1≤0.

012.

2. The compressor according to claim 1, characterized in that: The oil supply passage comprises a first oil supply section and a second oil supply section which are interconnected. The oil supply hole is connected to the first oil supply section. The second oil supply section is located at an end of the first oil supply section away from the oil supply hole and is connected to the oil pool. The maximum inner diameter of the first oil supply section is D2, and the maximum inner diameter of the second oil supply section is D3, satisfying: D2<D3.

3. The compressor according to claim 2, characterized in that: The inner diameter D1 of the oil supply hole and the maximum inner diameter D2 of the first oil supply section satisfy: 0.3≤D1 / D2≤0.

5.

4. The compressor according to claim 2, characterized in that: The maximum inner diameter D2 of the first oil supply section and the maximum inner diameter D3 of the second oil supply section satisfy: 0.5≤D2 / D3≤0.

7.

5. The compressor according to claim 2, characterized in that: The compressor further comprises an oiling vane, which is installed in the second oil supply section and protrudes downward from the lower end surface of the crankshaft, and the lower end of the oiling vane extends into the oil pool.

6. The compressor according to claim 5, characterized in that: Along the direction of the central axis of the crankshaft, the upper end of the oiling blade extends to the connection between the first oil supply section and the second oil supply section.

7. The compressor according to claim 5 or 6, characterized in that: Along the central axis of the crankshaft, the distance between the center of the outlet of the oil supply hole and the lower end of the first oil supply section is H2, and the maximum height of the oiling blade is H3, satisfying: 1.5≤H2 / H3≤1.

7.

8. The compressor according to claim 5 or 6, characterized in that: Along the direction of the central axis of the crankshaft, the maximum height of the oiling blade is H3, and the distance between the lower end surface of the crankshaft and the lower end of the oiling blade is H4, satisfying: 0.15≤H4 / H3≤0.

25.

9. The compressor according to claim 1, characterized in that: The central axis of the oil supply hole is perpendicular to the central axis of the crankshaft; Alternatively, the oil supply hole is arranged obliquely upward, and one end of the oil supply hole connected to the oil supply passage is lower than the other end.

10. The compressor according to claim 1 or 9, characterized in that: The support assembly further comprises a shaft sleeve, which is installed in the shaft hole, and one end of the oil supply hole which is away from the oil supply channel faces the inner peripheral wall of the shaft sleeve.

11. Refrigeration equipment, characterized in that Comprising a compressor as claimed in any one of claims 1 to 10.

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