Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment. The compressor comprises a shell, a motor assembly, a supporting assembly, a crankshaft and a spring. The supporting assembly comprises a motor bearing which is provided with a shaft hole. The crankshaft comprises an assembling part which is rotationally arranged in the shaft hole, the crankshaft is provided with an oil supply channel, the assembling part is provided with an oil outlet hole, and the two ends of the oil outlet hole communicate with the oil supply channel and the shaft hole correspondingly; the spring is arranged in the oil supply channel and located above the oil outlet hole. In the direction of the central axis of the crankshaft, the maximum distance between the upper end face of the crankshaft and the lower end of the spring is H1, the minimum distance between the center of an outlet of the oil outlet hole and the lower end of the spring is H2, and H2 / (H1 + H2) is larger than or equal to 0.1 and smaller than or equal to 0.5. By arranging the oil outlet hole and optimizing the distance between the spring and the oil outlet hole, more refrigerant oil is output to the shaft hole through the oil outlet hole, the lubricating performance between the crankshaft and the motor bearing is greatly improved, 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] For rotary compressors using high-thickness motors, the vibration of the rotor increases during the operation of the rotary compressor, affecting the coaxiality of the stator and rotor of the motor. For this reason, a double support structure is configured in the compressor, that is, the upper and lower ends of the crankshaft are supported by bearings, thereby reducing the flexural deformation of the upper end of the crankshaft and ensuring the coaxiality between the stator and rotor of the motor. In the related art, for the support structure located at the top, conventional sliding bearings are usually used to support the crankshaft. Conventional sliding bearings themselves are easily worn and have relatively poor reliability. In addition, the crankshaft does not supply enough oil to the sliding bearings, and the lubrication performance is poor, which affects 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, which can improve the lubrication performance between the crankshaft and the motor bearing and improve the reliability of the compressor.

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

[0005] According to the compressor of the first embodiment of the utility model, the housing includes a housing, a motor assembly, a support assembly, a crankshaft and a spring, wherein the housing has an inner cavity; the motor assembly is arranged in the inner cavity, the motor assembly includes a stator and a rotor, the stator is connected to the housing and is provided with an inner hole, and the rotor is rotatably arranged in the inner hole; the support assembly is installed in the inner cavity and is located above the motor assembly, the support assembly includes a motor bearing, and the motor bearing is provided with an axial hole; the crankshaft is fixedly connected to the rotor and protrudes upward from the rotor, the crankshaft includes an assembly portion located above the rotor, and the assembly portion The crankshaft is rotatably arranged in the shaft hole, and the crankshaft is provided with an oil supply passage, and the oil supply passage passes through the upper and lower ends of the crankshaft along the direction of the central axis of the crankshaft, and the assembly portion is provided with an oil outlet hole, and the two ends of the oil outlet hole are respectively connected to the oil supply passage and the shaft hole; the spring is arranged in the oil supply passage and is located above the oil outlet hole; wherein, along the direction of the central axis of the crankshaft, the maximum distance between the upper end surface of the crankshaft and the lower end of the spring is H1, and the minimum distance between the center of the outlet of the oil outlet hole and the lower end of the spring is H2, satisfying: 0.1≤H2 / (H1+H2)≤0.5.

[0006] The compressor according to the embodiment of the first aspect of the utility model has at least the following beneficial effects: by arranging an oil outlet hole on the assembly part of the crankshaft, and the two ends of the oil outlet hole are respectively connected with the oil supply channel and the shaft hole, on the one hand, the refrigerant oil in the oil supply channel can be directly output to the shaft hole through the oil outlet hole, so as to improve the lubrication performance between the crankshaft and the motor bearing; on the other hand, the spring arranged in the oil supply channel is located above the oil outlet hole, and the positional relationship between the spring and the oil outlet hole is limited to 0.1≤H2 / (H1+H2)≤0.5, so as to optimize the distance between the spring and the oil outlet hole. Combined with the oil blocking effect of the spring, more refrigerant oil can be output to the shaft hole through the oil outlet hole, and the vortex formed by the spring can be avoided from hindering the refrigerant oil from entering the oil outlet hole, thereby greatly improving the lubrication performance between the crankshaft and the motor bearing, and improving the reliability of the compressor.

[0007] According to some embodiments of the present invention, the inner diameter of the oil outlet hole is D, and the inner diameter D of the oil outlet hole and the minimum distance H2 between the center of the outlet of the oil outlet hole and the lower end of the spring satisfy: 0.21≤D / H2≤0.51.

[0008] According to some embodiments of the present invention, a central axis of the oil outlet hole is perpendicular to a central axis of the crankshaft.

[0009] According to some embodiments of the present invention, the oil outlet hole is arranged obliquely upward, and one end of the oil outlet hole away from the oil supply channel is higher than the other end.

[0010] According to some embodiments of the present utility model, the angle between the central axis of the oil outlet hole and the central axis of the crankshaft is θ, which satisfies: 60°≤θ<90°.

[0011] According to some embodiments of the utility model, the support assembly further includes a sleeve, which is installed in the shaft hole and sleeved on the assembly portion, and the end of the oil outlet hole away from the oil supply channel faces the inner circumferential wall of the sleeve.

[0012] According to some embodiments of the present invention, the oil supply channel includes a first channel and a second channel connected in sequence from top to bottom, the inner diameter of the second channel is smaller than the inner diameter of the first channel, and the spring is located at the connection between the first channel and the second channel.

[0013] According to some embodiments of the present invention, the maximum outer diameter of the spring is greater than the inner diameter of the second channel.

[0014] According to some embodiments of the present invention, the spring is configured to be conical in shape, and the small end of the spring is inserted into the second channel.

[0015] 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.

[0016] The refrigeration device according to the embodiment of the second aspect of the utility model has at least the following beneficial effects: when the refrigeration device is working, the compressor starts and compresses the refrigerant, and an oil outlet hole is provided on the assembly part of the crankshaft, and the two ends of the oil outlet hole are respectively connected with the oil supply channel and the shaft hole, so that the refrigerant oil in the oil supply channel can be directly output to the shaft hole through the oil outlet hole, so as to improve the lubrication performance between the crankshaft and the motor bearing, and the oil outlet effect of the oil outlet hole combined with the oil blocking effect of the spring can make more refrigerant oil be output to the shaft hole through the oil outlet hole, and can avoid the vortex formed by the spring hindering the refrigerant oil from entering the oil outlet hole, thereby greatly improving the lubrication performance between the crankshaft and the motor bearing, and improving the reliability of the compressor.

[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 This is a schematic diagram of the internal structure of the compressor in the embodiment of the utility model;

[0020] Figure 2 This is a schematic diagram of the installation of the assembly part of the first embodiment of the utility model;

[0021] Figure 3 This is a schematic diagram of the installation of the assembly part of the second embodiment of the utility model;

[0022] Figure 4 yes Figure 2 Enlarged view of point A in .

[0023] Reference numerals:

[0024] Shell 100; inner cavity 110; oil reservoir 111; exhaust pipe 120;

[0025] Motor assembly 200; stator 210; rotor 220;

[0026] Support assembly 300; motor bearing 310; shaft hole 311; support frame 320; shaft sleeve 330;

[0027] Crankshaft 400; assembly portion 410; oil outlet hole 411; oil supply channel 420; first channel 421; second channel 422; third channel 423; eccentric portion 430; step surface 440;

[0028] Spring 500; large end 510; small end 520;

[0029] Pump body assembly 600; cylinder 610; compression chamber 611; piston 620; first bearing 630; second bearing 640; partition 650; muffler 660;

[0030] Liquid reservoir 700. DETAILED DESCRIPTION

[0031] 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.

[0032] 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.

[0033] 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.

[0034] 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.

[0035] Reference Figure 1 As shown, the first embodiment of the utility model provides a compressor, which is applied to refrigeration equipment, and the compressor can compress the refrigerant to achieve the purpose of heat exchange through the refrigerant circulation. Specifically, the compressor includes a housing 100, a motor assembly 200, a support assembly 300, a crankshaft 400, a spring 500 and a pump body assembly 600.

[0036] The shell 100 is in the shape of a vertical column. An inner cavity 110 is formed inside the shell 100 . An oil storage tank 111 for storing refrigeration oil is reserved at the lower end of the inner cavity 110 . An exhaust pipe 120 is provided at the upper end of the shell 100 , and the exhaust pipe 120 is connected to the inner cavity 110 .

[0037] The motor assembly 200 is arranged in the inner cavity 110, and the motor assembly 200 includes a stator 210 and a rotor 220. The stator 210 is connected to the inner wall of the shell 100 and is provided with an inner hole. A plurality of reflux channels for the flow of refrigerant oil are also formed between the stator 210 and the inner wall of the shell 100. The reflux channels penetrate the two ends of the stator 210 in the vertical direction, and the plurality of reflux channels are arranged at intervals along the circumference of the stator 210. The stator 210 is mainly composed of an electromagnetic coil (winding) and an iron core. The rotor 220 is rotatably arranged in the inner hole of the stator 210. The rotor 220 is provided with a plurality of outlet channels for outputting a mixture of refrigerant and refrigerant oil. The outlet channels penetrate the two ends of the rotor 220 in the vertical direction, and the plurality of outlet channels are arranged at intervals along the circumference of the rotor 220.

[0038] By setting up a reflux channel, the refrigerant oil sprayed from the upper end of the crankshaft 400 to the inner wall of the shell 100 under the action of centrifugal force can flow to the outer surface of the cylinder 610 through the reflux channel, and then flow back to the oil storage tank 111, so that the refrigerant oil circulates to achieve lubrication and reduce the loss of refrigerant oil.

[0039] Reference Figure 1 As shown, the support assembly 300 is installed in the inner cavity 110 and is located above the motor assembly 200. The support assembly 300 includes a motor bearing 310 and a support frame 320. The outer wall of the support frame 320 and the inner wall of the shell 100 are fixedly connected by snapping, screwing or welding. The motor bearing 310 is detachably connected to the support frame 320 by fasteners and is located at the center of the support frame 320. An axial hole 311 is provided in the center of the motor bearing 310, and the support frame 320 is provided with a hollow structure for allowing refrigerant oil to flow through the support frame 320.

[0040] It can be understood that the rotor 220 is fixedly connected to the crankshaft 400 to drive the crankshaft 400 to rotate, and the crankshaft 400 is connected to the pump body assembly 600 to compress the refrigerant. Specifically, the pump body assembly 600 is located below the motor assembly 200, and the pump body assembly 600 includes a cylinder 610, a first bearing 630, a second bearing 640 and a piston 620. The cylinder 610 is fixedly installed in the inner cavity 110, and a compression chamber 611 is provided in the cylinder 610. The first bearing 630 and the second bearing 640 are respectively installed on both sides of the cylinder 610 to close the compression chamber 611. The first bearing 630 and the second bearing 640 are respectively installed on both sides of the cylinder 610 to close the compression chamber 611. The first bearing 630 and the second bearing 640 are respectively provided with gaps for connecting the compression chamber 611 and the inner chamber 110. The crankshaft 400 is sequentially passed through the first bearing 630, the cylinder 610 and the second bearing 640 and connected to the rotor 220. The crankshaft 400 is provided with an eccentric portion 430 at a position corresponding to the cylinder 610. The piston 620 is installed on the outer periphery of the eccentric portion 430 and accommodated in the compression chamber 611. The piston 620 can rotate eccentrically around the central axis of the crankshaft 400, thereby completing the suction, compression and exhaust processes of the refrigerant in the cylinder 610, and realizing the compression work of the refrigerant.

[0041] Among them, a liquid reservoir 700 is provided outside the shell 100, and the cylinder 610 is connected to the liquid reservoir 700 through a pipeline so that the compression chamber 611 can obtain the refrigerant in the liquid reservoir 700. There is one or two cylinders 610. When there are two cylinders 610, the two cylinders 610 are arranged at intervals in the vertical direction and a partition 650 for closing the compression chamber 611 is provided between the two cylinders 610. At this time, the eccentric part 430 and the piston 620 and the cylinder 610 are arranged one by one. By setting two cylinders 610, when the motor assembly 200 drives the crankshaft 400 to rotate, the crankshaft 400 simultaneously drives the pistons 620 in the two cylinders 610 to perform eccentric rotary motion through the two eccentric parts 430, thereby simultaneously performing the suction, compression and exhaust work of the refrigerant in the two cylinders 610, increasing the compression amount of the refrigerant, and improving the refrigeration capacity of the rotary compressor.

[0042] Reference Figure 1 As shown, the first bearing 630 and the second bearing 640 are connected to two opposite sides with mufflers 660, and the mufflers 660 on both sides are respectively covered on the first bearing 630 and the second bearing 640, and the mufflers 660 are provided with discharge ports for the refrigerant to flow out. The mufflers 660 can reduce noise while not interfering with the refrigerant exhaust.

[0043] Reference Figure 2 and Figure 3As shown, it can be understood that the upper end of the crankshaft 400 passes through the rotor 220 and forms an assembly portion 410, which is rotatably arranged in the shaft hole 311. In other words, the assembly portion 410 and the shaft hole 311 are clearance-matched to form a gap for the flow of refrigerant oil between the outer peripheral wall of the assembly portion 410 and the inner peripheral wall of the shaft hole 311. The crankshaft 400 is provided with an oil supply channel 420, which runs through the upper and lower ends of the crankshaft 400 along the central axis direction of the crankshaft 400 (i.e., the vertical direction), and the crankshaft 400 extends to the lower end of the cylinder 610, so that the oil supply channel 420 is connected with the oil reservoir 111. The inner wall of the lower end of the oil supply channel 420 is provided with a spiral oiling blade, and the rotation of the crankshaft 400 drives the oiling blade to rotate and transport the refrigerant oil in the oil reservoir 111 upward through the oil supply channel 420.

[0044] The assembly part 410 is provided with an oil outlet hole 411, and the two ends of the oil outlet hole 411 are respectively connected to the oil supply channel 420 and the shaft hole 311, that is, the oil outlet hole 411 passes through the side wall of the assembly part 410; the spring 500 is arranged in the oil supply channel 420 and is located above the oil outlet hole 411 and is provided with a through hole passing through the upper and lower ends along the central axis direction of the assembly part 410.

[0045] Reference Figure 1 and Figure 4 As shown, it can be understood that the oil supply channel 420 includes a first channel 421, a second channel 422 and a third channel 423 which are connected in sequence from top to bottom, the oiling blade is arranged in the third channel 423, the inner diameter of the second channel 422 is smaller than the inner diameter of the first channel 421, and the spring 500 is located at the connection between the first channel 421 and the second channel 422.

[0046] By setting the first channel 421 and the second channel 422, and the inner diameter of the second channel 422 is smaller than the inner diameter of the first channel 421, on the one hand, a step surface 440 can be formed at the connection between the first channel 421 and the second channel 422, and the step surface 440 can be a conical surface, an annular horizontal surface or an annular arc surface, and the structure of the step surface 440 is not specifically limited here. The spring 500 is installed at the connection between the first channel 421 and the second channel 422. At this time, the step surface 440 can play a positioning and supporting role for the spring 500, which is convenient for the positioning and installation of the spring 500. On the other hand, after the spring 500 buffers and decompresses the refrigeration oil, the refrigeration oil flows from the second channel 422 to the first channel 421. Since the inner diameter of the second channel 422 is smaller than the inner diameter of the first channel 421, the inner diameter of the refrigeration oil flow path increases. At this time, the refrigeration oil pressure is reduced and the flow rate is reduced, which can prevent the refrigeration oil from spraying out, thereby reducing the oil discharge amount and the oil discharge rate.

[0047] Reference Figure 2 and Figure 3As shown, it can be understood that, along the direction of the central axis of the crankshaft 400, the maximum distance between the upper end surface of the crankshaft 400 and the lower end of the spring 500 is H1, and the minimum distance between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500 is H2, satisfying: 0.1≤H2 / (H1+H2)≤0.5.

[0048] It should be noted that the cross section of the oil outlet hole 411 is circular, and the outlet of the oil outlet hole 411 is the opening of one end of the oil outlet hole 411 away from the oil supply channel 420 .

[0049] In some embodiments, the central axis of the oil outlet hole 411 is perpendicular to the central axis of the crankshaft 400. At this time, the height position of the center of the outlet of the oil outlet hole 411 is equal to the height position of the central axis of the oil outlet hole 411, and H2 is the distance between the central axis of the oil outlet hole 411 and the lower end of the spring 500.

[0050] In other embodiments, if the central axis of the oil outlet hole 411 is inclined relative to the central axis of the crankshaft 400, the center of the outlet of the oil outlet hole 411 is the intersection of the central axis of the oil outlet hole 411 and the extended surface of the outer peripheral wall of the assembly portion 410 at the outlet of the oil outlet hole 411.

[0051] The sum of the maximum distance H1 between the upper end surface of the crankshaft 400 and the lower end of the spring 500 and the minimum distance H2 between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500 can approximately represent the distance from the upper end surface of the crankshaft 400 to the outlet of the oil outlet hole 411, and the minimum distance H2 between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500 can approximately represent the distance between the outlet of the oil outlet hole 411 and the lower end of the spring 500.

[0052] Obviously, the ratio of the distance between the outlet of the oil outlet hole 411 and the lower end of the spring 500 to the distance from the upper end surface of the crankshaft 400 to the outlet of the oil outlet hole 411 can approximately represent the installation position of the spring 500 between the upper end surface of the crankshaft 400 and the outlet of the oil outlet hole 411. In other words, the closer the value of H2 / (H1+H2) is to 0, the closer the lower end of the spring 500 is to the oil outlet hole 411; the closer the value of H2 / (H1+H2) is to 1, the closer the lower end of the spring 500 is to the upper end of the crankshaft 400, and the farther it is from the oil outlet hole 411.

[0053] The ratio of the maximum distance H1 between the upper end surface of the crankshaft 400 and the lower end of the spring 500 to the outlet distance from the upper end surface of the crankshaft 400 to the oil outlet hole 411 is limited to above 0.1, ensuring that a certain distance is reserved between the lower end of the spring 500 and the oil outlet hole 411, avoiding the oil outlet hole 411 and the lower end of the spring 500 being too close, which would cause the refrigerant oil buffered by the spring 500 to collide with the refrigerant oil at the oil outlet hole 411 and form a vortex, thus affecting the oil outlet efficiency of the oil outlet hole 411.

[0054] The ratio of the maximum distance H1 between the upper end surface of the crankshaft 400 and the lower end of the spring 500 to the distance from the upper end surface of the crankshaft 400 to the outlet of the oil outlet hole 411 is limited to less than 0.5, that is, the distance from the lower end of the spring 500 to the center of the outlet of the oil outlet hole 411 does not exceed half of the distance from the upper end surface of the crankshaft 400 to the center of the outlet of the oil outlet hole 411. This can avoid the installation height of the spring 500 being too high along the central axial direction of the crankshaft 400 and the lower end of the spring 500 being away from the oil outlet hole 411, so that the spring 500 cannot quickly and effectively block the refrigerant oil above the oil outlet hole 411, and the refrigerant oil is decelerated and reduced in pressure, resulting in a decrease in the oil output of the oil outlet hole 411, affecting subsequent lubrication.

[0055] It can be understood that by providing an oil outlet hole 411 in the assembly portion 410 of the crankshaft 400, and the two ends of the oil outlet hole 411 are respectively connected to the oil supply channel 420 and the shaft hole 311, on the one hand, the refrigerant oil in the oil supply channel 420 can be directly output to the shaft hole 311 through the oil outlet hole 411 to improve the lubrication performance between the crankshaft 400 and the motor bearing 310, and on the other hand, the spring 500 provided in the oil supply channel 420 is located on the upper side of the oil outlet hole 411, and the spring 500 The positional relationship between the spring 500 and the oil outlet hole 411 is limited to 0.1≤H2 / (H1+H2)≤0.5. The distance between the spring 500 and the oil outlet hole 411 is optimized. Combined with the oil-blocking effect of the spring 500, more refrigerant oil can be output to the shaft hole 311 through the oil outlet hole 411, and the vortex formed by the spring 500 can be prevented from hindering the refrigerant oil from entering the oil outlet hole 411, thereby greatly improving the lubrication performance between the crankshaft 400 and the motor bearing 310 and improving the reliability of the compressor.

[0056] Reference Figure 2 and Figure 3 As shown, it can be understood that the inner diameter of the oil outlet hole 411 is D, and the inner diameter D of the oil outlet hole 411 and the minimum distance H2 between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500 satisfy: 0.21≤D / H2≤0.51.

[0057] Referring to the description of the outlet of the oil outlet hole 411 above, when the central axis of the oil outlet hole 411 is perpendicular to the central axis of the crankshaft 400, H2 is the distance between the central axis of the oil outlet hole 411 and the lower end of the spring 500. When the central axis of the oil outlet hole 411 is inclined relative to the central axis of the crankshaft 400, the center of the outlet of the oil outlet hole 411 is the intersection of the central axis of the oil outlet hole 411 and the extension surface of the outer peripheral wall of the assembly part 410 at the outlet of the oil outlet hole 411.

[0058] Along the central axis direction of the assembly part 410, the center of the outlet of the oil outlet hole 411 can approximately represent the opening position of the oil outlet hole 411 on the outer wall of the assembly part 410, so that the minimum distance H2 between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500 can approximately represent the distance between the outlet of the oil outlet hole 411 and the lower end of the spring 500.

[0059] The ratio of the inner diameter D of the oil outlet hole 411 to the minimum distance H2 between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500 is limited to above 0.21. On the one hand, it can avoid the problem that the inner diameter D of the oil outlet hole 411 is too small, the oil output of the oil outlet hole 411 is not high, and the oil output efficiency of the oil outlet hole 411 is reduced. On the other hand, it can avoid a series of problems such as design inconvenience and volume increase caused by the distance between the oil outlet hole 411 and the lower end of the spring 500 being too far and the length of the assembly part 410 along the central axis being too long, thereby improving the structural rationality of the assembly part 410.

[0060] The ratio of the inner diameter D of the oil outlet hole 411 to the minimum distance H2 between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500 is limited to less than 0.51 to prevent the oil outlet hole 411 from being too close to the lower end of the spring 500, which would cause the refrigerant oil buffered by the spring 500 to collide with the refrigerant oil at the oil outlet hole 411 and form a vortex, thus affecting the oil outlet efficiency of the oil outlet hole 411.

[0061] By reasonably limiting the ratio of the inner diameter D of the oil outlet hole 411 to the minimum distance H2 between the center of the outlet of the oil outlet hole 411 and the lower end of the spring 500, it is possible to ensure that the oil outlet hole 411 can discharge oil efficiently and stably and that the structure of the assembly part 410 is reasonable.

[0062] Reference Figure 2 As shown, it can be understood that the central axis of the oil outlet hole 411 is perpendicular to the central axis of the crankshaft 400 , that is, the oil outlet hole 411 is arranged in the horizontal direction and passes through the side wall of the assembly portion 410 .

[0063] The oil outlet hole 411 is arranged horizontally, which can facilitate the user to process and open the oil outlet hole 411 and reduce the manufacturing cost of the compressor.

[0064] Reference Figure 3 As shown, it can be understood that the oil outlet hole 411 is arranged to be inclined upward, and the end of the oil outlet hole 411 away from the oil supply channel 420 is higher than the other end, that is, along the vertical direction, the outlet of the oil outlet hole 411 is higher than the inlet, that is, along the radial direction of the assembly part 410, the end of the oil outlet hole 411 away from the central axis of the assembly part 410 is inclined upward.

[0065] When the crankshaft 400 rotates, the refrigerant oil flows vertically from bottom to top in the oil supply channel 420 under the action of the oiling blades. At this time, the refrigerant oil in the oil supply channel 420 has upward motion potential energy. The oil outlet hole 411 is arranged obliquely upward, so that the upward motion potential energy of the refrigerant oil can be reasonably utilized, the resistance of the refrigerant oil can be reduced, the flow rate of the refrigerant oil can be increased, the oil outlet efficiency of the oil outlet hole 411 can be improved, the lubrication capacity between the assembly part 410 and the motor bearing 310 can be enhanced, and the wear of the assembly part 410 and the motor bearing 310 can be reduced.

[0066] Continue to refer to Figure 3 As shown, it can be understood that the angle between the central axis of the oil outlet hole 411 arranged obliquely upward and the central axis of the vertical crankshaft 400 is θ, which satisfies: 60°≤θ<90°.

[0067] The angle between the central axis of the oil outlet hole 411 and the central axis of the crankshaft 400 is limited to more than 60° to avoid the oil outlet hole 411 from being tilted too much. When the refrigerant oil flows into the oil outlet hole 411, it is necessary to overcome the increased resistance caused by the work done by the larger gravity component, and ensure that the oil output of the oil outlet hole 411 is large enough.

[0068] Reference Figure 2 and Figure 3 As shown, it can be understood that the support assembly 300 also includes a sleeve 330, which is installed in the shaft hole 311 and sleeved on the assembly part 410. Specifically, the sleeve 330 is installed by a heat-sleeve method, that is, the motor bearing 310 is preheated before installation so that the lower end aperture of the motor bearing 310 is slightly larger than the aperture of the sleeve 330. Then, the sleeve 330 is quickly installed so that the sleeve 330 and the inner circumferential wall of the motor bearing 310 have an interference fit to ensure that the sleeve 330 is installed stably. The assembly part 410 and the sleeve 330 are clearance-fitted so that a gap for the flow of refrigerant oil is formed between the outer circumferential wall of the assembly part 410 and the inner circumferential wall of the sleeve 330, and the oil outlet hole 411 is away from the end of the oil supply channel 420 toward the inner circumferential wall of the sleeve 330.

[0069] By providing the sleeve 330, the wear resistance of the motor bearing 310 can be improved, thereby reducing the wear of the assembly part 410 and the motor bearing 310, reducing the working noise of the compressor, and extending the service life of the assembly part 410 and the motor bearing 310. The end of the oil outlet 411 away from the oil supply channel 420 is arranged toward the inner peripheral wall of the sleeve 330, ensuring that when the crankshaft 400 rotates, the refrigeration oil in the oil outlet 411 can be evenly sprayed onto the inner peripheral wall of the sleeve 330 to ensure lubrication.

[0070] In addition, before the assembly part 410 is installed, a friction-reducing coating may be provided on the outer peripheral wall of the assembly part 410 and / or the inner peripheral wall of the sleeve 330. The friction-reducing coating may be a polytetrafluoroethylene coating, a molybdenum disulfide coating, an aluminum silicon polyphenyl ester coating, a nickel-coated graphite coating, a nickel-chromium aluminum alloy coating or a babbitt alloy coating, etc. The above-mentioned types of friction-reducing coatings have low friction coefficients and high wear resistance and good lubricity, which can further optimize the lubrication process between the assembly part 410 and the motor bearing 310.

[0071] Reference Figure 4 As shown, it can be understood that the maximum outer diameter of the spring 500 is greater than the inner diameter of the second channel 422 .

[0072] The maximum outer diameter of the spring 500 is set to be larger than the inner diameter of the second channel 422, that is, the spring 500 and the first channel 421 are interference fit. After the spring 500 is installed, the outer peripheral wall of the spring 500 at the maximum outer diameter abuts against the inner peripheral wall of the first channel 421, which can effectively improve the installation stability of the spring 500 and avoid the spring 500 from loosening or even detaching from the oil supply channel 420 due to the impact of the refrigerant oil.

[0073] Continue to refer to Figure 4 As shown, it can be understood that the shape of the spring 500 is configured as a cone, the upper end of the conical spring 500 is the large end 510, and the lower end is the small end 520. The small end 520 of the spring 500 is inserted into the second channel 422. At this time, the outer diameter of the large end 510 of the spring 500 is the maximum outer diameter of the spring 500.

[0074] The spring 500 is configured to have a conical shape, and the small end 520 of the conical spring 500 is inserted into the second channel 422. At this time, the through hole that passes through the upper and lower ends of the spring 500 along the central axial direction of the crankshaft 400 is also conical, and the small end 520 of the conical through hole is located in the second channel 422, and the large end 510 is located in the first channel 421. When the refrigerant oil passes through the spring 500, the aperture of the through hole increases along the flow direction of the refrigerant oil, so that the oil pressure and flow rate of the refrigerant oil in the through hole are reduced, which effectively enhances the deceleration and pressure reduction effect of the spring 500, and when the spring 500 is assembled, the small end 520 of the spring 500 is inserted downward into the second channel 422, and the conical shape of the spring 500 can play a guiding and positioning role, which is convenient for the installation of the spring 500 and improves the assembly convenience of the spring 500.

[0075] The refrigeration equipment of the second embodiment of the utility model includes the compressor of the first embodiment of the utility model, and the refrigeration equipment includes air conditioners, refrigerators, freezers, water dispensers, etc. The compressor is the core power component of the refrigeration equipment and is mainly used to compress the refrigerant to achieve the purpose of heat exchange through the circulation of the refrigerant.

[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 having an inner cavity; A motor assembly is disposed in the inner cavity, the motor assembly comprises a stator and a rotor, the stator is connected to the housing and is provided with an inner hole, and the rotor is rotatably disposed in the inner hole; A support assembly is installed in the inner cavity and located above the motor assembly, wherein the support assembly includes a motor bearing, and the motor bearing is provided with an axial hole; A crankshaft, fixedly connected to the rotor and protruding upward from the rotor, the crankshaft comprising an assembly portion located above the rotor, the assembly portion being rotatably disposed on the shaft hole, the crankshaft being provided with an oil supply passage, the oil supply passage penetrating the upper and lower ends of the crankshaft along the direction of the central axis of the crankshaft, the assembly portion being provided with an oil outlet hole, the two ends of the oil outlet hole being respectively connected to the oil supply passage and the shaft hole; A spring, disposed in the oil supply passage and above the oil outlet hole; Among them, along the direction of the central axis of the crankshaft, the maximum distance between the upper end surface of the crankshaft and the lower end of the spring is H1, and the minimum distance between the center of the outlet of the oil outlet and the lower end of the spring is H2, satisfying: 0.1≤H2 / (H1+H2)≤0.

5.

2. The compressor according to claim 1, characterized in that: The inner diameter of the oil outlet hole is D, and the inner diameter D of the oil outlet hole and the minimum distance H2 between the center of the outlet of the oil outlet hole and the lower end of the spring satisfy: 0.21≤D / H2≤0.

51.

3. The compressor according to claim 1, characterized in that: The central axis of the oil outlet hole is perpendicular to the central axis of the crankshaft.

4. The compressor according to claim 1, characterized in that: The oil outlet hole is arranged obliquely upward, and one end of the oil outlet hole away from the oil supply channel is higher than the other end.

5. The compressor according to claim 4, characterized in that: The included angle between the central axis of the oil outlet hole and the central axis of the crankshaft is θ, which satisfies: 60°≤θ<90°.

6. The compressor according to any one of claims 1 to 5, characterized in that: The support assembly further includes a shaft sleeve, which is installed in the shaft hole and sleeved on the assembly portion, and the end of the oil outlet hole away from the oil supply channel faces the inner peripheral wall of the shaft sleeve.

7. The compressor according to claim 1, characterized in that: The oil supply channel comprises a first channel and a second channel which are connected in sequence from top to bottom, the inner diameter of the second channel is smaller than the inner diameter of the first channel, and the spring is located at the connection between the first channel and the second channel.

8. The compressor according to claim 7, characterized in that: The maximum outer diameter of the spring is greater than the inner diameter of the second passage.

9. The compressor according to claim 8, characterized in that: The outer shape of the spring is configured as a cone, and the small end of the spring is inserted into the second channel.

10. Refrigeration equipment, characterized in that Comprising a compressor as claimed in any one of claims 1 to 9.

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