Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment. The compressor comprises a shell, a motor assembly, a crankshaft, a spring and a supporting assembly. The crankshaft protrudes upwards to form a matching part; the supporting assembly comprises a motor bearing, and the motor bearing is provided with an assembling hole. The matching part is rotationally arranged in the assembling hole, the upper end face of the matching part is located below the plane where the upper end face of the motor bearing is located, a first oil storage cavity located above the upper end face of the matching part is formed in the assembling hole, and the maximum distance between the upper end face of the matching part and the lower end of the spring is H1 in the direction of the central axis, the minimum distance between the upper end face of the matching part and the upper end face of the motor bearing is H2, and H2 / H1 is larger than or equal to 0.04 and smaller than or equal to 0.5. The first oil storage cavity is defined between the upper end face of the matching part and the upper end face of the motor bearing, the oil blocking effect of the spring is combined, the lubricating performance can be guaranteed, the oil spitting rate can be reduced, and the reliability of the compressor can be improved.

Description

Technical Field

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

[0002] In order to ensure the running stability of the compressor, a double support structure is configured in the compressor, that is, the upper and lower parts of the crankshaft are supported by bearings. In the related art, in the matching structure between the crankshaft and the bearing matched with the upper end thereof, due to the unreasonable relative position relationship between the upper end of the crankshaft and the bearing in the direction of the central axis of the crankshaft, a large amount of refrigerant oil output from the upper end of the crankshaft will be sprayed into the cavity above the bearing in the compressor, resulting in a deterioration of the oil discharge rate and affecting 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 reduces the oil discharge rate while ensuring lubrication performance.

[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 comprises a housing, a motor assembly, a crankshaft, a spring and a support assembly, wherein the housing has an inner cavity; the motor assembly is arranged in the inner cavity, the motor assembly comprises a stator and a rotor, the stator is connected to the housing and is arranged around the outer periphery of the rotor; the crankshaft is fixedly connected to the rotor, the crankshaft is provided with an oil supply passage, the oil supply passage passes through both ends of the crankshaft along the direction of the central axis of the crankshaft, the crankshaft protrudes upward from the rotor and is formed with a matching portion; the spring is arranged in the oil supply passage and is located at the matching portion; the support assembly is installed in the inner cavity and is located above the motor assembly, the support assembly comprises a motor bearing, and the motor bearing is provided with an assembly hole; wherein the matching portion is rotatably arranged in the assembly hole, and the upper end surface of the matching portion is located below the plane where the upper end surface of the motor bearing is located, and a first oil storage cavity located above the upper end surface of the matching portion is formed in the assembly hole, and the maximum distance between the upper end surface of the matching portion and the lower end of the spring along the direction of the central axis is H 1 The minimum distance between the upper end surface of the mating portion and the upper end surface of the motor bearing is H 2 , satisfying: 0.04≤H 2 / H 1 ≤0.5.

[0006] The compressor according to the first embodiment of the utility model has at least the following beneficial effects: by making the upper end surface of the matching part of the crankshaft below the plane where the upper end surface of the motor bearing is located, a first oil storage cavity located above the upper end surface of the matching part is formed in the assembly hole. On the one hand, the first oil storage cavity can store a certain amount of refrigeration oil to ensure lubrication performance, and on the other hand, the minimum distance H between the upper end surface of the matching part and the upper end surface of the motor bearing is reduced. 2 The maximum distance H between the upper end surface of the mating part and the lower end of the spring 1 The ratio is limited to 0.04 to 0.5, and the position of the spring and the size of the first oil storage chamber are optimized. Combined with the oil blocking function of the spring, it can not only ensure the oil storage capacity of the first oil storage chamber to ensure the lubrication performance, but also reduce the flow velocity of the refrigerant oil output from the upper end of the oil supply channel, and reduce the amount of refrigerant oil sprayed to the upper space of the support assembly, thereby reducing the oil discharge rate, which is beneficial to improving the reliability of the compressor.

[0007] According to some embodiments of the utility model, the assembly hole includes a first hole segment, a second hole segment and a third hole segment which are connected in sequence from top to bottom, the matching portion is sequentially penetrated through the third hole segment and the second hole segment, and the upper end of the matching portion is accommodated in the first hole segment, the first oil storage chamber is formed in the first hole segment and is located on the upper end surface of the matching portion, a second oil storage chamber is defined between the inner circumferential wall of the first hole segment and the outer circumferential wall of the matching portion, and the second oil storage chamber is connected with the first oil storage chamber.

[0008] According to some embodiments of the present invention, the maximum outer diameter of the mating portion is D 1 , the inner diameter of the first hole section is D 2 , satisfying: 0.21≤(D 2 -D 1 ) / D 1 ≤0.45.

[0009] According to some embodiments of the present invention, the inner diameter of the second hole segment is smaller than the inner diameter of the first hole segment, and an oil passage is defined between the inner circumferential wall of the second hole segment and the outer circumferential wall of the mating portion, and the oil passage is connected to the second oil storage chamber.

[0010] According to some embodiments of the present invention, the maximum outer diameter of the mating portion is D 1 , the inner diameter of the second hole section is D 3 , satisfying: 0.2≤(D 3 -D 1 ) / D 1 ≤0.46.

[0011] According to some embodiments of the utility model, the oil supply channel includes a first channel and a second channel connected in sequence from top to bottom, the spring is located at the connection between the first channel and the second channel, and the inner diameter of the second channel is smaller than the inner diameter of the first channel.

[0012] 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.

[0013] 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.

[0014] According to some embodiments of the present invention, the support assembly further includes a sleeve, which is installed in the third hole section and sleeved on the matching portion.

[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 second embodiment 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 the upper end surface of the matching portion of the crankshaft is located below the plane where the upper end surface of the motor bearing is located, so that a first oil storage cavity located above the upper end surface of the matching portion is formed in the assembly hole. On the one hand, the first oil storage cavity can store a certain amount of refrigeration oil to ensure lubrication performance, and on the other hand, the minimum distance H between the upper end surface of the matching portion and the upper end surface of the motor bearing is set. 2 The maximum distance H between the upper end surface of the mating part and the lower end of the spring 1 The ratio is limited to 0.04 to 0.5, and the position of the spring and the size of the first oil storage chamber are optimized. Combined with the oil blocking function of the spring, it can not only ensure the oil storage capacity of the first oil storage chamber to ensure the lubrication performance, but also reduce the flow velocity of the refrigerant oil output from the upper end of the oil supply channel, and reduce the amount of refrigerant oil sprayed to the upper space of the support assembly, thereby reducing the oil discharge rate, which is beneficial to 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 It is a schematic diagram of the internal structure of the compressor in the embodiment of the utility model;

[0020] Figure 2It is a schematic diagram of the installation of the matching part in the embodiment of the utility model;

[0021] Figure 3 Figure 2 A in the enlarged view;

[0022] Figure 4 is a cross-sectional view of a motor bearing in an embodiment of the utility model;

[0023] Figure 5 The oil discharge rate and H in the embodiment of the utility model 2 / H 1 A line graph of the relationship between .

[0024] Reference numerals:

[0025] Shell 100; inner cavity 110; oil reservoir 111; exhaust pipe 120;

[0026] Motor assembly 200; stator 210; rotor 220;

[0027] Support assembly 300; motor bearing 310; assembly hole 311; first hole section 3111; second hole section 3112; third hole section 3113; fixing frame 320; sleeve 330; first oil storage chamber 340; second oil storage chamber 350; oil passage 360;

[0028] Crankshaft 400; mating portion 410; oil supply passage 420; first passage 421; second passage 422; third passage 423; eccentric portion 430; step surface 440;

[0029] Spring 500; large end 510; small end 520;

[0030] Pump body assembly 600; cylinder 610; compression chamber 611; piston 620; first bearing 630; second bearing 640; partition 650; muffler 660;

[0031] Liquid reservoir 700. DETAILED DESCRIPTION

[0032] 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.

[0033] 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.

[0034] 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.

[0035] 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.

[0036] 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.

[0037] 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 .

[0038] 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 circumferential 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 circumferential 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 the flow of 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.

[0039] 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, thereby realizing the recycling of the refrigerant oil and reducing the loss of refrigerant oil.

[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 on the outside of 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, the piston 620, and the cylinder 610 are arranged one by one.

[0042] By setting up 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 rotational motion through the two eccentric parts 430, so that the refrigerant is sucked in, compressed and exhausted in the two cylinders 610 at the same time, thereby increasing the compression amount of the refrigerant and improving the cooling capacity of the rotary compressor.

[0043] 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 affecting the discharge of the refrigerant.

[0044] Reference Figure 1 and Figure 2 As shown, it can be understood that the crankshaft 400 is provided with an oil supply passage 420, and the oil supply passage 420 passes through both ends of the crankshaft 400 along the central axis direction (i.e., the vertical direction) of the crankshaft 400, and the crankshaft 400 protrudes upward from the rotor 220 and is formed with a matching portion 410, and the spring 500 is arranged in the oil supply passage 420 and is located at the matching portion 410. Specifically, the oil supply passage 420 includes a first passage 421, a second passage 422, and a third passage 423 that are sequentially connected from top to bottom, and the oiling blade is arranged in the third passage 423, the inner diameter of the second passage 422 is smaller than the inner diameter of the first passage 421, and the connection between the first passage 421 and the second passage 422 is located at the matching portion 410 that passes through the rotor 220, and the spring 500 is installed at the connection between the first passage 421 and the second passage 422.

[0045] 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, the connection between the first channel 421 and the second channel 422 can form a step surface 440, and the step surface 440 can be a conical surface, an annular plane 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.

[0046] Reference Figure 3 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 .

[0047] 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 have an interference fit. After the spring 500 is installed, the outer wall of the spring 500 at the maximum outer diameter abuts the inner wall of the first channel 421, which can effectively improve the installation stability of the spring 500 and prevent the spring 500 from loosening or even detaching from the oil supply channel 420 due to the impact of the refrigerant oil.

[0048] Continue to refer to Figure 3As 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.

[0049] 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.

[0050] 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 fixing frame 320. The outer wall of the fixing frame 320 and the inner circumferential wall of the shell 100 are fixedly connected by means of clamping, screwing or welding. The motor bearing 310 is detachably connected to the fixing frame 320 by fasteners and is located at the center of the fixing frame 320. An assembly hole 311 is provided in the center of the motor bearing 310. The fixing frame 320 is provided with a hollow structure for allowing refrigerant oil to flow through the fixing frame 320. Specifically, the fixing frame 320 is a plate structure with an outer diameter smaller than the inner diameter of the inner cavity 110. A plurality of connecting parts are provided at intervals on the outer periphery of the fixing frame 320. The connecting parts are folded upward and connected to the inner circumferential wall of the inner cavity 110. A hollow structure for allowing refrigerant oil to flow through the fixing frame 320 is formed between two adjacent connecting parts.

[0051] Reference Figure 2 and Figure 3As shown, it can be understood that the mating part 410 is rotatably arranged in the assembly hole 311, and the upper end surface of the mating part 410 is located below the plane where the upper end surface of the motor bearing 310 is located, and a first oil storage chamber 340 is formed in the assembly hole 311 and is located above the upper end surface of the mating part 410. Specifically, the assembly hole 311 includes a first hole section 3111, a second hole section 3112 and a third hole section 3113 which are connected in sequence from top to bottom. The matching part 410 is sequentially inserted into the third hole section 3113 and the second hole section 3112 and the upper end of the matching part 410 is accommodated in the first hole section 3111, that is, along the vertical direction, the upper end surface of the matching part 410 is lower than the upper end surface of the motor bearing 310, so that the first hole section 3111 protrudes from the upper end surface of the matching part 410 along the central axis direction of the matching part 410, and the first hole section 3111 is located at the inner circumferential wall of the upper end surface of the matching part 410 and the plane where the upper end surface of the matching part 410 is located. The space capable of storing refrigerant oil, namely, the first oil storage chamber 340.

[0052] The mating portion 410 is installed in the assembly hole 311 to position and support the upper end of the crankshaft 400 passing through the rotor 220, which can reduce the flexural deformation of the upper end of the crankshaft 400 and ensure the coaxiality between the stator 210 and the rotor 220 of the motor.

[0053] By setting the first oil storage chamber 340, the first oil storage chamber 340 is located above the upper end surface of the matching part 410, that is, the first oil storage chamber 340 is located at the end of the refrigerant oil flow path in the oil supply channel 420. The first oil storage chamber 340 can store a certain amount of refrigerant oil, thereby ensuring the lubrication performance. At the same time, due to the rotation of the crankshaft 400, when the refrigerant oil is sprayed out from the upper end of the crankshaft 400, it is sprayed around the crankshaft 400 under the action of centrifugal force. At the same time, since the first oil storage chamber 340 is formed above the upper end surface of the crankshaft 400, the upper end surface of the crankshaft 400 has a wall surface surrounding the central axis of the crankshaft 400 (that is, the inner circumferential wall of the first oil storage chamber 340). The sprayed refrigerant oil is sprayed onto the inner circumferential wall of the first oil storage chamber 340 instead of being directly sprayed onto the upper space of the support assembly 300, thereby increasing the resistance and combining with the oil blocking effect of the spring 500 to reduce the spraying speed of the refrigerant oil, reduce the amount of refrigerant oil sprayed into the upper space of the support assembly 300, and reduce the oil discharge rate of the compressor.

[0054] Reference Figure 2 As shown, it can be understood that along the direction of the central axis, the maximum distance between the upper end surface of the matching portion 410 and the lower end of the spring 500 is H 1 The minimum distance between the upper end surface of the mating portion 410 and the upper end surface of the motor bearing 310 is H 2 , satisfying: 0.04≤H 2 / H 1 ≤0.5.

[0055] The maximum distance H between the upper end surface of the fitting portion 410 and the lower end of the spring 500 1 It can be roughly regarded as the installation height of the spring 500 from the first oil storage chamber 340, and the minimum distance H between the upper end surface of the matching portion 410 and the upper end surface of the motor bearing 310 2 That is, the depth of the first oil storage chamber 340 along the vertical direction. The ratio of the depth of the first oil storage chamber 340 and the installation height of the spring 500 is limited to above 0.04, ensuring that the first oil storage chamber 340 has a sufficient depth to store a certain amount of refrigerant oil to ensure lubrication performance, and ensuring that the first oil storage chamber 340 can store a sufficient amount of refrigerant oil to block the refrigerant oil flowing upward from the oil supply channel 420, preventing the refrigerant oil from directly rushing into the upper chamber and causing the oil discharge rate to deteriorate, while avoiding the first oil storage chamber 340 being too far away from the spring 500, resulting in problems such as difficulty in assembling the spring 500 and excessive length of the mating part 410.

[0056] The ratio of the depth of the first oil storage chamber 340 and the installation height of the spring 500 is limited to less than 0.5 to prevent the first oil storage chamber 340 from being too deep and causing too much refrigerant oil to accumulate in the first oil storage chamber 340, thereby affecting the circulation of the refrigerant oil and ensuring the smoothness of the entire circulation process of the refrigerant oil. At the same time, the first oil storage chamber 340 and the spring 500 are prevented from being too close to each other, causing the refrigerant oil sprayed out of the first oil storage chamber 340 through the first channel 421 to accumulate quickly, while the gap between the matching portion 410 and the second hole section 3112 cannot quickly drain the refrigerant oil accumulated in the first oil storage chamber 340, causing the refrigerant oil in the first oil storage chamber 340 to exceed the load-bearing upper limit, resulting in overflow of the refrigerant oil, and the refrigerant oil in the oil supply channel 420 quickly rushing out of the first oil storage chamber 340, causing the oil discharge rate to deteriorate.

[0057] Reference Figure 5 As shown, the oil discharge rate is less than or equal to 1.5% as the qualified standard. According to the line graph of the oil discharge rate changing with the ratio of the depth of the first oil storage cavity 340 and the installation height of the spring 500, it can be seen that when the ratio of the depth of the first oil storage cavity 340 and the installation height of the spring 500 is approximately 0.04 to 0.5, the oil discharge rate of the compressor is qualified, and when the ratio of the depth of the first oil storage cavity 340 and the installation height of the spring 500 is around 0.3, the oil discharge rate is the smallest, which is about 1.35%.

[0058] It can be understood that by making the upper end surface of the matching portion 410 of the crankshaft 400 located below the plane where the upper end surface of the motor bearing 310 is located, a first oil storage cavity 340 located above the upper end surface of the matching portion 410 is formed in the assembly hole 311, and the minimum distance H between the upper end surface of the matching portion 410 and the upper end surface of the motor bearing 310 is set to 2 The maximum distance H between the upper end surface of the mating portion 410 and the lower end of the spring 500 1The ratio is limited to 0.04 to 0.5, and the position of the spring 500 and the size of the first oil storage chamber 340 are optimized. Combined with the oil blocking function of the spring 500, it can not only ensure the oil storage capacity of the first oil storage chamber 340 to ensure the lubrication performance, but also reduce the flow velocity of the refrigerant oil output from the upper end of the oil supply channel 420, and reduce the amount of refrigerant oil sprayed into the upper space of the support assembly 300, thereby reducing the oil discharge rate, which is beneficial to improving the reliability of the compressor.

[0059] Reference Figure 2 As shown, it can be understood that the second oil storage chamber 350 is defined between the inner circumferential wall of the first hole section 3111 and the outer circumferential wall of the matching portion 410, that is, the maximum outer diameter of the matching portion 410 is smaller than the inner diameter of the first hole section 3111, so that an annular space capable of storing refrigerant oil is formed between the outer circumferential wall of the matching portion 410 and the inner circumferential wall of the first hole section 3111, that is, the second oil storage chamber 350. The second oil storage chamber 350 is communicated with the first oil storage chamber 340.

[0060] By setting up the second oil storage chamber 350, the second oil storage chamber 350 is located at the lower side of the first oil storage chamber 340 and is connected to the first oil storage chamber 340, so that the second oil storage chamber 350 can store a certain amount of refrigerant oil at the lower side of the first oil storage chamber 340, thereby increasing the oil storage amount in the motor bearing 310, thereby increasing the supply amount of refrigerant oil between the inner circumferential wall of the subsequent second hole section 3112 and the outer circumferential wall of the mating part 410, thereby ensuring the lubrication effect.

[0061] It should be noted that since the first oil storage chamber 340 is formed above the upper end surface of the motor bearing 310, and the second oil storage chamber 350 is formed between the inner circumferential wall of the first hole section 3111 and the outer circumferential wall of the mating portion 410, it is obvious that the inner circumferential wall of the first oil storage chamber 340 and the inner circumferential wall with a larger inner diameter of the second oil storage chamber 350 are both part of the inner circumferential wall of the first hole section 3111. Therefore, the inner circumferential wall of the first oil storage chamber 340 and the inner circumferential wall of the second oil storage chamber 350 are flush with each other, which facilitates the opening and processing of the assembly hole 311 and allows the refrigerant oil to flow smoothly at the connection between the first oil storage chamber 340 and the second oil storage chamber 350 to ensure lubrication.

[0062] Reference Figure 2 and Figure 4 As shown, it can be understood that the maximum outer diameter of the mating portion 410 is D 1 , the inner diameter of the first hole section 3111 is D 2 , satisfying: 0.21≤(D 2 -D 1 ) / D 1 ≤0.45.

[0063] The inner diameter D of the first hole section 3111 2 and the maximum outer diameter D of the mating portion 410 1The difference is the width dimension of the second oil storage chamber 350 along the radial direction of the assembly hole 311. The ratio of the width of the second oil storage chamber 350 to the maximum outer diameter of the matching portion 410 can be approximately regarded as the size ratio of the second oil storage chamber 350 and the matching portion 410. Since the inner circumferential wall of the first oil storage chamber 340 and the inner circumferential wall of the second oil storage chamber 350 are flush with each other, the ratio of the width of the second oil storage chamber 350 to the maximum outer diameter of the matching portion 410 is limited to more than 0.21, so as to avoid the second oil storage chamber 350 being too small in width and difficult to store a certain amount of refrigerant oil, resulting in the rapid loss of refrigerant oil through the second oil storage chamber 350, and reasonably expand the oil storage capacity of the first oil storage chamber 340 to enhance the oil blocking capacity of the first oil storage chamber 340.

[0064] The ratio of the width of the second oil storage chamber 350 to the maximum outer diameter of the mating part 410 is limited to less than 0.45. On the one hand, it can prevent the first oil storage chamber 340 and the second oil storage chamber 350 from having too large a radial width along the assembly hole 311 and too strong an oil storage capacity, which may cause too much refrigerant oil to accumulate in the motor bearing 310, affecting the circulation of the refrigerant oil and thus affecting the operation of the entire compressor. It ensures the smoothness of the entire circulation process of the refrigerant oil and at the same time prevents the width of the first oil storage chamber 340 from being too large, which may make it difficult to block the sprayed refrigerant oil. It ensures that most of the sprayed refrigerant oil will hit the inner wall of the first hole section 3111 and accumulate to form an oil pool, thereby ensuring the oil blocking capacity of the first oil storage chamber 340. On the other hand, it can prevent the inner diameter of the first hole section 3111 from being too large, which may reduce the wall thickness of the side wall of the motor bearing 310, resulting in reduced structural strength of the motor bearing 310.

[0065] By reasonably limiting the ratio of the width of the second oil storage chamber 350 to the maximum outer diameter of the mating part 410 and reasonably expanding the oil storage capacity of the first oil storage chamber 340, it can be ensured that the second oil storage chamber 350 has a certain oil discharge capacity without affecting the circulation of the refrigerant oil, and it can also be ensured that the motor bearing 310 has sufficient strength to support the mating part 410.

[0066] Reference Figure 2 As shown, it can be understood that the inner diameter of the second hole segment 3112 is smaller than the inner diameter of the first hole segment 3111, and an oil passage 360 ​​is defined between the inner circumferential wall of the second hole segment 3112 and the outer circumferential wall of the matching portion 410, and the oil passage 360 ​​is connected to the second oil storage chamber 350. In other words, the matching portion 410 and the second hole segment 3112 are loosely matched, and the gap between the matching portion 410 and the second hole segment 3112 forms an oil passage 360 ​​for the flow of refrigerant oil.

[0067] By setting up the oil passage 360, after the refrigerant oil is sprayed out of the oil supply channel 420 from the first channel 421, it passes through the first oil storage chamber 340 and the second oil storage chamber 350 in sequence, and under the action of gravity, flows from the second oil storage chamber 350 into the oil passage 360, providing lubrication between the matching part 410 and the inner circumferential wall of the second hole section 3112, reducing the wear of the matching part 410 and the motor bearing 310, and facilitating the recycling of the refrigerant oil.

[0068] Reference Figure 2 and Figure 4 As shown, it can be understood that the maximum outer diameter of the mating portion 410 is D 1 , the inner diameter of the second hole section 3112 is D 3 , satisfying: 0.2≤(D 3 -D 1 ) / D 1 ≤0.46.

[0069] The inner diameter D of the second hole section 3112 3 and the maximum outer diameter D of the mating portion 410 1 The difference is the radial width of the oil channel 360 along the assembly hole 311. The ratio of the width of the oil channel 360 to the maximum outer diameter of the mating part 410 is limited to above 0.2 to ensure that the oil channel 360 has sufficient oil outlet area and avoid problems such as the oil channel 360 being too small, the refrigerant oil flow efficiency being low, and insufficient lubrication.

[0070] The ratio of the width of the oil passage 360 ​​to the maximum outer diameter of the mating part 410 is limited to less than 0.46. On the one hand, it can prevent the width of the oil passage 360 ​​along the radial direction of the assembly hole 311 from being too large, and the inner circumference of the assembly hole 311 of the motor bearing 310 from being difficult to support the mating part 410, resulting in problems such as reduced stability of the mating part 410. It can also improve the fit between the motor bearing 310 and the crankshaft 400, and ensure stable installation of the mating part 410.

[0071] By reasonably limiting the ratio of the width of the oil passage 360 ​​to the maximum outer diameter of the matching portion 410, it is possible to ensure that the oil passage 360 ​​can smoothly discharge oil and that the motor bearing 310 and the crankshaft 400 have sufficient matching accuracy.

[0072] Reference Figure 1 and Figure 2As shown, it can be understood that the support assembly 300 also includes a sleeve 330, which is installed in the third hole section 3113 and sleeved on the matching portion 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. The sleeve 330 is then 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 matching portion 410 and the sleeve 330 are clearance-matched so that a gap for the flow of refrigerant oil is formed between the outer circumferential wall of the matching portion 410 and the inner circumferential wall of the sleeve 330, and the oil outlet hole is away from the end of the oil supply channel 420 toward the inner circumferential wall of the sleeve 330.

[0073] By providing the sleeve 330, the wear resistance of the motor bearing 310 can be improved, thereby reducing the wear of the matching part 410 and the motor bearing 310, reducing the working noise of the compressor, and extending the service life of the matching part 410 and the motor bearing 310. The end of the oil outlet hole 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 refrigerant oil in the oil outlet hole can be evenly sprayed onto the inner peripheral wall of the sleeve 330 to ensure lubrication.

[0074] It is understandable that a friction-reducing coating may be coated on the outer wall of the mating part 410 or the inner wall of the sleeve 330, or the outer wall of the mating part 410 and the inner wall of the sleeve 330 may be coated at the same time. 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 a low friction coefficient and high wear resistance, and have good lubricity, which can further optimize the lubrication between the mating part 410 and the motor bearing 310.

[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 disposed around the outer circumference of the rotor; A crankshaft, fixedly connected to the rotor, the crankshaft is provided with an oil supply passage, the oil supply passage passes through both ends of the crankshaft along the direction of the central axis of the crankshaft, the crankshaft protrudes upward from the rotor and is formed with a matching portion; a spring, disposed in the oil supply passage and located at the matching portion; 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 assembly hole; Wherein, the matching part is rotatably arranged in the assembly hole, and the upper end surface of the matching part is located below the plane where the upper end surface of the motor bearing is located, and a first oil storage cavity located above the upper end surface of the matching part is formed in the assembly hole, and along the direction of the central axis, the maximum distance between the upper end surface of the matching part and the lower end of the spring is H1, and the minimum distance between the upper end surface of the matching part and the upper end surface of the motor bearing is H2, satisfying: 0.04≤H2 / H1≤0.

5.

2. The compressor according to claim 1, characterized in that: The assembly hole includes a first hole segment, a second hole segment and a third hole segment which are connected in sequence from top to bottom, the matching portion is sequentially penetrated through the third hole segment and the second hole segment, and the upper end of the matching portion is accommodated in the first hole segment, the first oil storage cavity is formed in the first hole segment and is located on the upper end surface of the matching portion, a second oil storage cavity is defined between the inner circumferential wall of the first hole segment and the outer circumferential wall of the matching portion, and the second oil storage cavity is connected with the first oil storage cavity.

3. The compressor according to claim 2, characterized in that: The maximum outer diameter of the matching portion is D1, and the inner diameter of the first hole segment is D2, satisfying: 0.21≤(D2-D1) / D1≤0.

45.

4. The compressor according to claim 2, characterized in that: The inner diameter of the second hole segment is smaller than that of the first hole segment. An oil passage is defined between the inner peripheral wall of the second hole segment and the outer peripheral wall of the matching portion. The oil passage is communicated with the second oil storage cavity.

5. The compressor according to claim 4, characterized in that: The maximum outer diameter of the matching portion is D1, and the inner diameter of the second hole segment is D3, which satisfies: 0.2≤(D3-D1) / D1≤0.

46.

6. 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 spring is located at the connection between the first channel and the second channel, and the inner diameter of the second channel is smaller than the inner diameter of the first channel.

7. The compressor according to claim 6, characterized in that: The maximum outer diameter of the spring is greater than the inner diameter of the second passage.

8. The compressor according to claim 7, 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.

9. The compressor according to claim 2, characterized in that: The support assembly also includes a shaft sleeve, which is installed in the third hole section and sleeved on the matching portion.

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

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