Scroll compressor and oxygen generator
By installing an elastic ring between the crankshaft and cranks and the bearings in the scroll compressor, the friction is increased, which solves the problem of easy slippage of the bearings on the moving scroll and improves the durability and stability of the bearings.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- HUNAN MAIGU TECH CO LTD
- Filing Date
- 2025-06-06
- Publication Date
- 2026-04-21
AI Technical Summary
In scroll compressors, slippage can easily occur between the bearings on the moving scroll and the shaft, leading to problems such as high bearing operating temperature, accelerated wear, and reduced lifespan.
An elastic ring is installed between the crankshaft and the bearing to increase friction through elastic deformation and reduce the risk of slippage; an elastic ring is also installed between the crank and the bearing to enhance the anti-slip effect.
This effectively reduces the risk of slippage between the crankshaft and bearings, reduces wear and rust, and extends the service life of the bearings.
Smart Images
Figure CN224149778U_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of air compression technology, and in particular to scroll compressors and oxygen generators. Background Technology
[0002] An oxygen concentrator is a machine that produces oxygen. Its principle is based on air separation technology. First, air is compressed at high density, and then the different condensation points of the components in the air are used to separate the gas and liquid at a certain temperature. Further distillation is then carried out to obtain oxygen. Specifically, the adsorption properties of molecular sieves are used. Through physical principles, a large-displacement oil-free compressor is used to separate nitrogen and oxygen in the air, ultimately obtaining a high concentration of oxygen.
[0003] Oil-free compressors can be scroll compressors. The working principle of an oil-free scroll air compressor is to use the relative revolution of the moving and fixed scrolls to form a continuous change in the closed volume, thereby achieving the purpose of compressing gas. During the special eccentric motion of the compressor itself and under special working conditions such as high temperature and water vapor, slippage is likely to occur between the bearings on the moving scroll and the shaft, resulting in high bearing operating temperature, accelerated wear and rust between the shaft and the bearing, and greatly reducing the bearing life. Utility Model Content
[0004] This application provides a scroll compressor and an oxygen generator to reduce the risk of slippage between the bearings on the moving scroll and the shaft in the scroll compressor.
[0005] To solve the above-mentioned technical problems, the first technical solution provided in this application is: a scroll compressor, including a stationary scroll, a moving scroll, a first crankshaft bearing, a crankshaft, and a first elastic ring; one end of the moving scroll meshes with the stationary scroll; the outer ring of the first crankshaft bearing is connected to the end of the moving scroll away from the stationary scroll; one end of the crankshaft passes through the inner ring of the first crankshaft bearing; the first elastic ring is disposed between the first crankshaft bearing and the crankshaft.
[0006] According to one embodiment of this application, the scroll compressor further includes an end cover, a second crankshaft bearing, and a second elastic ring. The end cover is disposed on the side of the moving scroll away from the stationary scroll. The outer ring of the second crankshaft bearing is connected to the end cover. The inner ring of the second crankshaft bearing is sleeved on the other end of the crankshaft. The second elastic ring is disposed between the crankshaft and the second crankshaft bearing.
[0007] According to one embodiment of this application, there are at least two first elastic rings, which are arranged sequentially at intervals along the axial direction of the crankshaft; and / or, there are at least two second elastic rings, which are arranged sequentially at intervals along the axial direction of the crankshaft.
[0008] According to one embodiment of this application, the scroll compressor further includes a motor mount, which is disposed on the side of the moving scroll away from the stationary scroll, and the moving scroll is at least partially housed in the motor mount; a third crankshaft bearing, the outer ring of which is connected to the motor mount, and the inner ring of which is sleeved on the crankshaft, and the third crankshaft bearing is located between the first crankshaft bearing and the second crankshaft bearing along the axial direction of the crankshaft.
[0009] According to one embodiment of this application, the scroll compressor further includes a motor, which is connected to an end cover and a motor base, and is also connected to a crankshaft.
[0010] According to one embodiment of this application, the scroll compressor further includes a crank, with a moving scroll and a stationary scroll connected to its two ends respectively; the scroll compressor further includes a first crank bearing and a third elastic ring, the outer ring of the first crank bearing being connected to the moving scroll, the inner ring of the first crank bearing being sleeved on the end of the crank away from the stationary scroll, and the third elastic ring being disposed between the crank and the first crank bearing; and / or, the scroll compressor further includes a second crank bearing and a fourth elastic ring, the outer ring of the second crank bearing being connected to the stationary scroll, the inner ring of the first crank bearing being sleeved on the end of the crank away from the moving scroll, and the fourth elastic ring being disposed between the crank and the second crank bearing.
[0011] According to one embodiment of this application, the scroll compressor further includes a crank, a first crank bearing, a third elastic ring, a second crank bearing, and a fourth elastic ring; the outer ring of the first crank bearing is connected to the moving scroll, the inner ring of the first crank bearing is sleeved on the end of the crank away from the stationary scroll, and the third elastic ring is disposed between the crank and the first crank bearing; the outer ring of the second crank bearing is connected to the stationary scroll, the inner ring of the first crank bearing is sleeved on the end of the crank away from the moving scroll, and the fourth elastic ring is disposed between the crank and the second crank bearing; the number of first crank bearings is at least two, and the at least two first crank bearings are arranged sequentially along the axial direction of the crank; and / or, the number of second crank bearings is at least two, and the at least two second crank bearings are arranged sequentially along the axial direction of the crank; and / or, the number of third elastic rings is at least two, and the at least two third elastic rings are arranged alternately along the axial direction of the crank; and / or, the number of fourth elastic rings is at least two, and the at least two fourth elastic rings are arranged alternately along the axial direction of the crank.
[0012] According to one embodiment of this application, the scroll compressor further includes a crank, a first crank bearing, and a second crank bearing. The first crank bearing is connected to one end of the crank and the moving scroll, and the second crank bearing is connected to the other end of the crank and the stationary scroll. The scroll compressor further includes a first locking member, which is connected to the end of the crank away from the stationary scroll, and the end of the first crank bearing away from the stationary scroll abuts against the first locking member. And / or, the scroll compressor further includes a second locking member, which is connected to the end of the crank away from the moving scroll, and the end of the second crank bearing away from the moving scroll abuts against the second locking member.
[0013] According to one embodiment of this application, the scroll compressor further includes a third elastic ring disposed between the crank and the first crank bearing; and / or, the scroll compressor further includes a fourth elastic ring disposed between the crank and the second crank bearing.
[0014] To solve the above-mentioned technical problems, the second technical solution provided in this application is: an oxygen generator, including the scroll compressor of any of the above solutions.
[0015] The beneficial effects of this application are:
[0016] The scroll compressor and oxygen generator with the scroll compressor provided in this application have a crankshaft and a moving scroll that are rotatably coupled through a first crankshaft bearing. When the crankshaft rotates, the crankshaft drives the moving scroll to rotate around the rotation axis of the crankshaft to achieve gas compression. The elastic deformation of the first elastic ring sandwiched between the crankshaft and the first crankshaft bearing can reduce the risk of slippage between the inner surfaces of the inner ring of the crankshaft and the first crankshaft bearing. This reduces the risk of high operating temperature of the first crankshaft bearing, accelerated wear and rust between the crankshaft and the first crankshaft bearing, and reduced lifespan of the first crankshaft bearing caused by slippage. Attached Figure Description
[0017] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort, wherein:
[0018] Figure 1 This is an axial cross-sectional schematic diagram of the scroll compressor provided in this application;
[0019] Figure 2 yes Figure 1 Enlarged view of point A in the middle;
[0020] Figure 3 yes Figure 1 Schematic diagram of the bearings of the middle crankshaft and the first crankshaft;
[0021] Figure 4 yes Figure 1 Enlarged view of point B in the middle;
[0022] Figure 5 yes Figure 1 Enlarged view of point C in the middle;
[0023] Figure 6 yes Figure 5 A schematic diagram of the structure of the middle crank and the first crank bearing.
[0024] Explanation of reference numerals in the attached figures:
[0025] Scroll compressor 100
[0026] Static vortex disk 110
[0027] Heat sink fins 111
[0028] 120 moving scroll
[0029] Compression chamber 101
[0030] Crankshaft 131
[0031] Crankshaft eccentric section 1311
[0032] Crankshaft concentric section 1312
[0033] First crankshaft bearing 132
[0034] First elastic ring 1321
[0035] Second crankshaft bearing 133
[0036] Second elastic ring 1331
[0037] Third crankshaft bearing 134
[0038] Crank 141
[0039] Crank housing 1410
[0040] Crank eccentric section 1411
[0041] Crank concentric section 1412
[0042] First crank bearing 142
[0043] Third elastic ring 1421
[0044] Second crank bearing 143
[0045] Fourth elastic ring 1431
[0046] First locking component 144
[0047] Second locking component 145
[0048] Gasket 146
[0049] End cap 150
[0050] Motor mount 160
[0051] Motor 170
[0052] Stator assembly 171
[0053] Rotor assembly 172
[0054] First balancing block 181
[0055] Second balancing block 182 Detailed Implementation
[0056] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.
[0057] In this document, the term "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.
[0058] This application provides a scroll compressor, in one embodiment of which refers to... Figure 1 and Figure 2 , Figure 1 This is an axial sectional view of the scroll compressor provided in this application. Figure 2 yes Figure 1 The enlarged view at point A shows that the scroll compressor 100 includes a stationary scroll 110, a moving scroll 120, a first crankshaft bearing 132, a crankshaft 131, and a first elastic ring 1321. One end of the moving scroll 120 meshes with the stationary scroll 110; together they are combined. Figure 3 , Figure 3 yes Figure 1 A schematic diagram of the structure of the middle crankshaft and the first crankshaft bearing shows that the outer ring of the first crankshaft bearing 132 is connected to the end of the moving scroll 120 away from the stationary scroll 110, and one end of the crankshaft 131 passes through the inner ring of the first crankshaft bearing 132. The first elastic ring 1321 is located between the first crankshaft bearing 132 and the crankshaft 131.
[0059] The moving scroll 120 and the stationary scroll 110 are the main functional components of the scroll compressor 100. The moving scroll 120 meshes with the stationary scroll 110, forming a compression chamber 101. The rotation of the moving scroll 120 relative to the stationary scroll 110 causes a continuous change in the closed volume of the compression chamber 101, thereby compressing the low-pressure gas drawn into the compression chamber 101 into high-pressure gas and discharging it. Specifically, the stationary scroll 110 can be a groove structure opening towards the moving scroll 120, and stationary scroll teeth are provided inside the stationary scroll 110. The moving scroll 120 can be a plate-like structure, and moving scroll teeth are provided on the moving scroll 120. The stationary scroll 110 and the moving scroll 120 are connected by the staggered 180° meshing of the stationary and moving scroll teeth.
[0060] One end of the crankshaft 131 is connected to the moving scroll 120 via a first crankshaft bearing 132 to drive the rotation of the moving scroll 120 relative to the stationary scroll 110. Exemplarily, the crankshaft 131 can be driven to rotate by a drive component such as a motor, thereby driving the rotation of the moving scroll 120 relative to the stationary scroll 110. Specifically, the crankshaft 131 may include a concentric section 1312 and an eccentric section 1311. When the crankshaft 131 rotates, the rotation axis of the crankshaft 131 is parallel to the central axis of the eccentric section 1311, and the rotation axis of the crankshaft 131 coincides with the central axis of the concentric section 1312. That is, the crankshaft 131 rotates with the central axis of the concentric section 1312 as its rotation axis. Since the rotation axis of crankshaft 131 is parallel to the central axis of crankshaft eccentric section 1311, when crankshaft 131 rotates to drive moving scroll 120 to rotate, the rotation mode of moving scroll 120 relative to stationary scroll 110 is that moving scroll 120 revolves around the rotation axis of crankshaft 131.
[0061] The first crankshaft bearing 132 allows relative rotation between the crankshaft eccentric section 1311 and the moving scroll 120 (the crankshaft eccentric section 1311 rotates relative to the moving scroll 120 about the central axis of the moving scroll 120). This allows it to work with mechanisms such as the crank 141 described later to limit the rotation of the moving scroll 120 relative to its own central axis (also referred to as the rotation of the moving scroll 120), so that the moving scroll 120 only revolves around the crankshaft 131 without rotating on its own axis.
[0062] The crankshaft 131 and the inner surface of the bearing inner ring of the first crankshaft bearing 132 are typically fitted with a clearance fit. Therefore, slippage can easily occur between the inner surfaces of the crankshaft 131 and the inner ring of the first crankshaft bearing 132. A first elastic ring 1321 is disposed between the crankshaft 131 and the first crankshaft bearing 132. Specifically, the first elastic ring 1321 can be fitted onto the eccentric section 1311 of the crankshaft, and the first elastic ring 1321 is disposed between the eccentric section 1311 of the crankshaft and the inner ring of the first crankshaft bearing 132. An elastic ring 1321 is used to prevent slippage between the crankshaft 131 and the inner ring of the first crankshaft bearing 132. Specifically, when the first elastic ring 1321 is installed between the inner surfaces of the crankshaft 131 and the inner ring of the first crankshaft bearing 132, the first elastic ring 1321 will undergo elastic deformation, which can increase the friction between the inner surfaces of the crankshaft 131 and the inner ring of the first crankshaft bearing 132, thereby improving the anti-slip effect between the inner surfaces of the crankshaft 131 and the inner ring of the first crankshaft bearing 132.
[0063] The slippage between the crankshaft 131 and the inner surface of the bearing inner ring of the first crankshaft bearing 132 as described in this application means that the crankshaft 131 and the inner surface of the bearing inner ring of the first crankshaft bearing 132 slide along the circumference of the first crankshaft bearing 132.
[0064] As can be seen, in the scroll compressor 100 provided in this application, the crankshaft 131 and the moving scroll 120 are rotated together through the first crankshaft bearing 132. When the crankshaft 131 rotates, the crankshaft 131 drives the moving scroll 120 to rotate around the rotation axis of the crankshaft 131 to achieve gas compression. The elastic deformation of the first elastic ring 1321 sandwiched between the crankshaft 131 and the first crankshaft bearing 132 can reduce the risk of slippage between the inner surfaces of the inner rings of the crankshaft 131 and the first crankshaft bearing 132. This reduces the risk of high operating temperature of the first crankshaft bearing 132, accelerated wear and rust between the crank 141 and the first crankshaft bearing 132, and reduced lifespan of the first crankshaft bearing 132 due to slippage.
[0065] In some embodiments, please refer to Figure 4 , Figure 4 yes Figure 1 The enlarged view at point B shows that the scroll compressor 100 also includes an end cover 150, a second crankshaft bearing 133, and a second elastic ring 1331. The end cover 150 is located on the side of the moving scroll 120 away from the stationary scroll 110. The outer ring of the second crankshaft bearing 133 is connected to the end cover 150, and the inner ring of the second crankshaft bearing 133 is sleeved on the other end of the crankshaft 131. The second elastic ring 1331 is located between the crankshaft 131 and the second crankshaft bearing 133.
[0066] The end cap 150 is used to install the second crankshaft bearing 133. The end cap 150 can be fixedly installed relative to the stationary scroll plate 110. The second crankshaft bearing 133 allows relative rotation between the crankshaft 131 and the end cap 150, and also reduces the frictional resistance during relative rotation between the crankshaft 131 and the end cap 150. The second crankshaft bearing 133 can be a single bearing, and it can be located near the end of the crankshaft concentric section 1312 away from the crankshaft eccentric section 1311 to make the crankshaft 131 rotate more smoothly.
[0067] The crankshaft 131 and the inner surface of the inner ring of the second crankshaft bearing 133 are usually fitted with a clearance fit. Therefore, slippage is easy between the inner surfaces of the inner rings of the crankshaft 131 and the second crankshaft bearing 133. The second elastic ring 1331 is disposed between the crankshaft 131 and the second crankshaft bearing 133. Specifically, the second elastic ring 1331 can be sleeved on the concentric section 1312 of the crankshaft. The second elastic ring 1331 is disposed between the concentric section 1312 of the crankshaft and the inner surface of the inner ring of the second crankshaft bearing 133. This can increase the friction between the inner surfaces of the inner rings of the crankshaft 131 and the second crankshaft bearing 133, thereby improving the anti-slip effect between the inner surfaces of the inner rings of the crankshaft 131 and the second crankshaft bearing 133. This reduces the risk of high operating temperature of the second crankshaft bearing 133, accelerated wear and rust between the crankshaft 131 and the second crankshaft bearing 133, and reduced life of the second crankshaft bearing 133 due to slippage.
[0068] The slippage between the inner surface of the inner ring of the crankshaft 131 and the second crankshaft bearing 133 as described in this application means that the inner surface of the inner ring of the crankshaft 131 and the second crankshaft bearing 133 slides along the circumference of the first crankshaft bearing 132.
[0069] In some embodiments, there are at least two first elastic rings 1321, which are arranged at intervals along the axial direction of the crankshaft 131. In this embodiment, at least two first elastic rings 1321 are provided between the eccentric section 1311 of the crankshaft and the inner surface of the inner ring of the first crankshaft bearing 132, which can further increase the friction between the crankshaft 131 and the inner surface of the inner ring of the first crankshaft bearing 132, thereby further improving the anti-slip effect between them. Exemplarily, the number of first elastic rings 1321 between the eccentric section 1311 of the crankshaft and the inner surface of the inner ring of the first crankshaft bearing 132 can be two, three, or more. Figures 1 to 3 The diagram shows a case where there are two first elastic rings 1321 between the crankshaft eccentric section 1311 and the inner surface of the bearing inner ring of the first crankshaft bearing 132.
[0070] In some embodiments, there are at least two second elastic rings 1331, which are sequentially spaced apart along the axial direction of the crankshaft 131. In this embodiment, at least two second elastic rings 1331 are provided between the concentric section 1312 of the crankshaft and the inner surface of the inner ring of the second crankshaft bearing 133, which can further increase the friction between the crankshaft 131 and the inner surface of the inner ring of the second crankshaft bearing 133, thereby further improving the anti-slip effect between them. Exemplarily, the number of second elastic rings 1331 between the concentric section 1312 of the crankshaft and the inner surface of the inner ring of the second crankshaft bearing 133 can be two, three, or more. Figure 1 and Figure 3 The diagram shows a case where there are two second elastic rings 1331 between the concentric section 1312 of the crankshaft and the inner surface of the inner ring of the second crankshaft bearing 133.
[0071] In some embodiments, the scroll compressor 100 further includes a motor housing 160 and a third crankshaft bearing 134. The motor housing 160 is disposed on the side of the moving scroll 120 away from the stationary scroll 110, and the moving scroll 120 is at least partially housed in the motor housing 160. The outer ring of the third crankshaft bearing 134 is connected to the motor housing 160, and the inner ring of the third crankshaft bearing 134 is sleeved on the crankshaft 131. Along the axial direction of the crankshaft 131, the third crankshaft bearing 134 is located between the first crankshaft bearing 132 and the second crankshaft bearing 133.
[0072] The motor mount 160 can be a housing structure and is fixedly connected to the stationary scroll 110. The motor mount 160 is used to install the third crankshaft bearing 134 and together with the stationary scroll 110, it houses the moving scroll 120.
[0073] In this embodiment, a third crankshaft bearing 134 is added between the first crankshaft bearing 132 and the second crankshaft bearing 133, which can further improve the smoothness of the crankshaft 131 during rotation, thereby further improving the operating accuracy of the moving scroll 120.
[0074] In some embodiments, the crankshaft 131 and the inner ring of the third crankshaft bearing 134 are interference-fitted. This allows the third crankshaft bearing 134 to support the crankshaft 131 and also improves the operational stability of the crankshaft 131.
[0075] To achieve axial positioning when the crankshaft 131 is pressed into the third crankshaft bearing 134, the motor housing 160 and the crankshaft concentric section 1312 are both provided with mounting steps at the position where the third crankshaft bearing 134 is installed. The outer ring of the third crankshaft bearing 134 is locked in the mounting step of the motor housing 160, and the inner ring of the third crankshaft bearing 134 is locked in the mounting step of the crankshaft concentric section 1312.
[0076] In some embodiments, the scroll compressor 100 further includes a motor 170, which is connected to the end cover 150 and the motor mount 160, respectively, and is also connected to the crankshaft 131.
[0077] Generally, the motor 170 may include a stator assembly 171 and a rotor assembly 172. The stator assembly 171 is sleeved on the outside of the rotor assembly 172, and the crankshaft 131 (specifically, the crankshaft concentric section 1312 of the crankshaft 131) passes through the rotor assembly 172 and is fixedly connected to the rotor assembly 172. By supplying power to the stator coils of the stator assembly 171, the stator coils of the stator assembly 171 and the magnets of the rotor assembly 172 generate an electromagnetic effect, thereby causing the rotor assembly 172 to rotate relative to the stator assembly 171. When the rotor assembly 172 rotates, it synchronously drives the crankshaft 131 to rotate around the central axis of the crankshaft concentric section 1312.
[0078] The second crankshaft bearing 133 and the third crankshaft bearing 134 can be located on the axial sides of the rotor assembly 172 of the motor 170, respectively, and the end cover 150 and the motor base 160 are fixed to the two ends of the outer surface of the stator assembly 171, respectively.
[0079] In some embodiments, to improve the smoothness of crankshaft 131 rotation and reduce shaking or vibration during crankshaft 131 rotation, a first balance block 181 and a second balance block 182 are also provided on crankshaft 131. The first balance block 181 and the second balance block 182 can be detachably fastened to crankshaft 131 by means of, but not limited to, screws, bolts, snap-fits, etc. The first balance block 181 is located between the first crankshaft bearing 132 and the third crankshaft bearing 134, and the second balance block 182 is located between the rotor assembly 172 of motor 170 and the second crankshaft bearing 133. Since crankshaft 131 has an overall eccentric design, the weight of the first balance block 181 and the second balance block 182 provides counterweight, making crankshaft 131 rotate more smoothly.
[0080] In some embodiments, please refer to Figure 5 and Figure 6 , Figure 5 yes Figure 1 Enlarged view at point C in the middle. Figure 6 yes Figure 5 The schematic diagram of the structure of the middle crank and the first crank bearing shows that the scroll compressor 100 also includes a crank 141, with the two ends of the crank 141 connected to the moving scroll 120 and the stationary scroll 110 respectively; the scroll compressor 100 also includes a first crank bearing 142 and a third elastic ring 1421, the outer ring of the first crank bearing 142 is connected to the moving scroll 120, the inner ring of the first crank bearing 142 is sleeved on the end of the crank 141 away from the stationary scroll 110, and the third elastic ring 1421 is located between the crank 141 and the first crank bearing 142.
[0081] The crank 141 is used to limit the rotation of the moving volute 120. So when the moving volute 120 revolves around the rotation axis of the crankshaft 131, the moving volute 120 only revolves and does not rotate, so as to avoid interference between the moving volute teeth in the moving volute 120 and the stationary volute teeth in the stationary volute 110.
[0082] Generally speaking, crank 141 may include a concentric crank section 1412 and an eccentric crank section 1411. The central axis of the concentric crank section 1412 coincides with the rotation axis of crank 141, and the eccentric crank section 1411 is parallel to the rotation axis of crank 141. That is, crank 141 rotates with the central axis of the concentric crank section 1412 as the rotation axis.
[0083] Multiple cranks 141 can be spaced apart along the circumference of the compressor. For example, three can be evenly arranged along the circumference of the compressor to make the moving scroll 120 more stable under force and the revolution of the moving scroll 120 relative to the stationary scroll 110 more stable.
[0084] The first crank bearing 142 allows relative rotation between the eccentric crank section 1411 and the moving scroll 120. Since the eccentric crank section 1411 can rotate around the crankshaft 141's axis of rotation, when the crankshaft 131 rotates, causing the moving scroll 120 to revolve around the crankshaft 131's axis of rotation, the guidance of the eccentric crank section 1411's revolution around the crankshaft 141's axis of rotation ensures that the moving scroll 120 also follows the revolution path of the eccentric crank section 1411 around the crankshaft 131's axis of rotation, revolving only around the crankshaft 131 without rotating on its own axis. Furthermore, the first crank bearing 142 can reduce the frictional resistance during relative rotation between the eccentric crank section 1411 and the moving scroll 120.
[0085] The crank 141 and the inner ring of the first crank bearing 142 are typically fitted with a clearance fit, which makes slippage prone to occur between them. A third elastic ring 1421 is positioned between the crank 141 and the first crank bearing 142. Specifically, the third elastic ring 1421 can be fitted onto the eccentric section 1411 of the crank, and the third elastic ring 1421 is positioned between the eccentric section 1411 of the crank and the inner ring of the first crank bearing 142. On the inner surface, the third elastic ring 1421 prevents the crank 141 from slipping on the inner ring of the first crank bearing 142. Specifically, when the third elastic ring 1421 is installed between the crank 141 and the inner ring of the first crank bearing 142, the third elastic ring 1421 will undergo elastic deformation, which can increase the friction between the crank 141 and the inner ring of the first crank bearing 142, thereby improving the anti-slip effect of the crank 141 and the inner ring of the first crank bearing 142.
[0086] The slippage between the crank 141 and the inner ring of the first crank bearing 142 as described in this application means that the crank 141 and the inner ring of the first crank bearing 142 slide along the circumference of the first crank bearing 142.
[0087] To achieve axial positioning between the crank 141 and the moving scroll 120, the moving scroll 120 is provided with a mounting groove at the position where the first crank bearing 142 is installed, and the groove wall is provided with a mounting step. The crank eccentric section 1411 is also provided with a mounting step at the position where the first crank bearing 142 is installed. The first crank bearing 142 is received in the mounting groove of the moving scroll 120, and the outer ring of the first crank bearing 142 is locked in the mounting step of the mounting groove of the moving scroll 120, while the inner ring of the first crank bearing 142 is locked in the mounting step of the crank eccentric section 1411.
[0088] In some embodiments, the scroll compressor 100 further includes a crank 141, with the two ends of the crank 141 connected to a moving scroll 120 and a stationary scroll 110, respectively; the scroll compressor 100 further includes a second crank bearing 143 and a fourth elastic ring 1431, the outer ring of the second crank bearing 143 is connected to the stationary scroll 110, the inner ring of the second crank bearing 143 is sleeved on the end of the crank 141 away from the moving scroll 120, and the fourth elastic ring 1431 is disposed between the crank 141 and the second crank bearing 143.
[0089] The structure of crank 141 is the same as described in the above embodiment.
[0090] The second crank bearing 143 allows relative rotation between the concentric section 1412 of the crank and the stationary scroll 110, and also reduces frictional resistance during relative rotation between the concentric section 1412 of the crank and the stationary scroll 110.
[0091] The crank 141 and the second crank bearing 143 are usually fitted with a clearance fit, which makes them prone to slippage. The fourth elastic ring 1431 is disposed between the crank 141 and the second crank bearing 143. Specifically, the fourth elastic ring 1431 can be sleeved on the concentric section 1412 of the crank and is disposed between the concentric section 1412 of the crank and the inner surface of the inner ring of the second crank bearing 143. This increases the friction between the inner rings of the crank 141 and the second crank bearing 143, thereby improving the anti-slip effect between them. This reduces the risk of high operating temperature of the second crank bearing 143, accelerated wear and rust between the crank 141 and the second crank bearing 143, and reduced lifespan of the second crank bearing 143 caused by slippage.
[0092] The slippage between the crank 141 and the inner ring of the second crank bearing 143 as described in this application means that the crank 141 and the inner ring of the second crank bearing 143 slide circumferentially along the second crank bearing 143.
[0093] To achieve axial positioning of crank 141 relative to stationary scroll 110, both stationary scroll 110 and crank concentric section 1412 are provided with mounting steps at the positions where the second crank bearing 143 is installed. The outer ring of the second crank bearing 143 is locked in the mounting step of stationary scroll 110, and the inner ring of the second crank bearing 143 is locked in the mounting step of crank concentric section 1412.
[0094] In some embodiments, the crank 141 is located on the outer side of the compression chamber 101 in the radial direction of the compressor, thereby avoiding the meshing line between the stationary scroll 110 and the moving scroll 120.
[0095] In some embodiments, the motor mount 160 and the stationary scroll 110 together form a crank receiving cavity 1410, which is located on the outer side of the compression cavity 101 in the radial direction of the compressor, and the crank 141 is housed within the crank receiving cavity 1410. When multiple cranks 141 are arranged circumferentially along the compressor, the corresponding number of crank receiving cavities 1410 is also multiple.
[0096] In some embodiments, the number of first crank bearings 142 is at least two, and the at least two first crank bearings 142 are arranged sequentially along the axial direction of the crank 141. Since the crank 141 and the first crank bearings 142 experience a large centrifugal force during the rotation of the moving scroll 120, setting the number of first crank bearings 142 to at least two allows them to withstand larger loads. Exemplarily, the number of first crank bearings 142 can be two, or more. Figure 1 as well as Figures 5 to 6 The illustration shows a case where there are two first crank bearings 142. In other embodiments, the possibility of having only one first crank bearing 142 is also not excluded.
[0097] In some embodiments, the number of second crank bearings 143 is at least two, and the at least two second crank bearings 143 are arranged sequentially along the axial direction of the crank 141. Since the crank 141 experiences a large centrifugal force during the rotation of the moving scroll 120, setting the number of second crank bearings 143 to at least two allows for the bearing of larger loads. Exemplarily, the number of second crank bearings 143 can be two, or more. Figure 1 as well as Figure 6 The illustration shows a case where there are two second crank bearings 143. In other embodiments, the possibility of having only one second crank bearing 143 is also not excluded.
[0098] In some embodiments, the number of third elastic rings 1421 is at least two, and the at least two third elastic rings 1421 are arranged sequentially at intervals along the axial direction of the crank 141. In this embodiment, the arrangement of multiple third elastic rings 1421 between the crank 141 and the inner ring of the first crank bearing 142 can further increase the friction between the crank 141 and the inner ring of the first crank bearing 142, thereby further improving the anti-slip effect between the two. Exemplarily, the number of third elastic rings 1421 between the crank 141 and the inner ring of the first crank bearing 142 can be two, three, or more.
[0099] In some embodiments, the number of fourth elastic rings 1431 is at least two, and the at least two fourth elastic rings 1431 are arranged sequentially at intervals along the axial direction of the crank 141. In this embodiment, the arrangement of multiple fourth elastic rings 1431 between the crank 141 and the inner ring of the second crank bearing 143 can further increase the friction between the crank 141 and the inner ring of the second crank bearing 143, thereby further improving the anti-slip effect between the two. Exemplarily, the number of fourth elastic rings 1431 between the crank 141 and the inner ring of the second crank bearing 143 can be two, three, or more.
[0100] In some embodiments, the edge formed between the bearing inner ring end face and the bearing inner ring inner surface of at least one of the first crankshaft bearing 132, the second crankshaft bearing 133, the first crank bearing 142 and the second crank bearing 143 is chamfered.
[0101] The chamfering can be either a right angle or a rounded corner. The edge formed between the bearing inner ring end face and the bearing inner ring inner surface is chamfered to facilitate the insertion of each elastic ring. Preferably, the edge formed between the bearing inner ring end faces and the bearing inner ring inner surface of the first crankshaft bearing 132, the second crankshaft bearing 133, the first crankshaft bearing 142, and the second crankshaft bearing 143 is chamfered. That is, the edge formed between the bearing inner ring end face and the bearing inner ring inner surface of the first crankshaft bearing 132 is chamfered to facilitate the insertion of the first elastic ring 1321 between the bearing inner ring inner surface of the first crankshaft bearing 132 and the crankshaft eccentric section 1311; the edge formed between the bearing inner ring end face and the bearing inner ring inner surface of the second crankshaft bearing 133 is chamfered to facilitate the insertion of the second elastic ring 1331 between the bearing inner ring inner surface of the second crankshaft bearing 133 and the crankshaft concentric section 1312. The edge formed between the bearing inner ring end face and the inner surface of the bearing inner ring of the first crank bearing 142 is chamfered to facilitate the insertion of the third elastic ring 1421 between the inner surface of the bearing inner ring of the first crank bearing 142 and the eccentric section 1411 of the crank; the edge formed between the bearing inner ring end face and the inner surface of the bearing inner ring of the second crank bearing 143 is chamfered to facilitate the insertion of the fourth elastic ring 1431 between the inner surface of the bearing inner ring of the second crank bearing 143 and the concentric section 1412 of the crank.
[0102] In some embodiments, the scroll compressor 100 further includes a first locking member 144, which is connected to one end of the crank 141 away from the stationary scroll 110, and the end of the first crank bearing 142 away from the stationary scroll 110 abuts against the first locking member 144.
[0103] The first locking element 144 is used to prevent slippage between the crank 141 and the inner ring of the first crank bearing 142. The first locking element 144 can be a nut or other locking element, for example, a self-locking nut. One end of the crank 141 can be inserted through the nut, and the nut is screwed onto the crank 141. The end face of the nut presses against the end of the inner ring of the first crank bearing 142 that is away from the stationary scroll plate 110, thereby locking the crank 141 and the inner ring of the first crank bearing 142 and improving the anti-slip effect between the eccentric section 1411 of the crank and the inner ring of the first crank bearing 142.
[0104] In this application, the anti-slip between the crank 141 and the inner ring of the first crank bearing 142 can be achieved solely by the first locking member 144, solely by the third elastic ring 1421, or jointly by the first locking member 144 and the third elastic ring 1421.
[0105] In some embodiments, the scroll compressor 100 further includes a second locking member 145, which is connected to one end of the crank 141 away from the moving scroll 120, and the end of the second crank bearing 143 away from the moving scroll 120 abuts against the second locking member 145.
[0106] The second locking element 145 can be a locking bolt or a locking screw, for example, an internal hexagon head screw. Correspondingly, the end face of the concentric section 1412 of the crank is provided with a threaded locking groove, so the bolt (or screw) can be locked in the locking groove. At the same time, the nut of the bolt (or screw) presses against the end of the inner ring of the second crank bearing 143 that is away from the moving scroll 120, thereby achieving locking between the crank 141 and the inner ring of the second crank bearing 143, which can improve the anti-slip effect between the crank section 141 and the inner ring of the second crank bearing 143.
[0107] In this application, the anti-slip between the crank 141 and the inner ring of the second crank bearing 143 can be achieved solely by the second locking member 145, solely by the fourth elastic ring 1431, or jointly by the second locking member 145 and the fourth elastic ring 1431.
[0108] Furthermore, by setting the first locking member 144 and the second locking member 145, the stationary scroll 110 and the moving scroll 120 can be connected in the axial direction.
[0109] In some embodiments, along the axial direction of crank 141, a shim 146 is sandwiched between the concentric section 1412 of crank and the bearing inner ring end face of the first crank bearing 142, and crank 141 is supported on the bearing inner ring of the first crank bearing 142 by the shim 146.
[0110] In this embodiment, the shim 146 is used to prevent direct rigid contact between the crank 141 and the end face of the inner ring of the first crank bearing 142 when the crank 141 is supported on the end face of the inner ring of the first crank bearing 142. The shim 146 can be fitted onto the connection between the concentric section 1412 and the eccentric section 1411 of the crank.
[0111] In some embodiments, the stationary scroll 110 is provided with heat dissipation fins 111 on the side opposite to the compression chamber 101. In some embodiments, the moving scroll 120 is also provided with heat dissipation fins 111 on the side opposite to the compression chamber 101.
[0112] The heat dissipation fins 111 primarily serve a heat dissipation function. During the operation of the scroll compressor 100, the gas temperature rises as it compresses air into high-pressure gas. To reduce the internal temperature of the scroll compressor 100, heat dissipation fins 111 are provided on the surfaces of the stationary scroll 110 and the moving scroll 120 to dissipate the high temperature within the compression chamber 101. Additionally, a fan can be used in conjunction with the scroll compressor 100 during operation to further dissipate heat.
[0113] This application also provides an oxygen generator, which includes a scroll compressor, the specific structure of which is described in the above embodiments. Typically, the oxygen generator also includes a molecular sieve and a heat exchanger, the heat exchanger being connected between the scroll compressor and the molecular sieve.
[0114] In this type of oxygen generator, a scroll compressor is used to generate high-pressure air, which is then passed into a molecular sieve to produce high-concentration oxygen. This type of oxygen generator can also be called a molecular sieve oxygen generator.
[0115] Because the high-pressure air produced by the scroll compressor is at a high temperature, the temperature of the high-pressure air entering the molecular sieve during operation is also high. This reduces the performance of the molecular sieve and consequently affects the oxygen production efficiency of the oxygen generator. A heat exchanger is used to exchange heat with the high-pressure air produced by the scroll compressor, thereby reducing the temperature of the high-pressure air entering the molecular sieve.
[0116] The heat exchange device may include, but is not limited to, cooling pipes. Two molecular sieves may be provided, and the air discharged from the heat exchange device may alternately enter the two molecular sieves.
[0117] The working principle of this oxygen concentrator is roughly as follows: outside air enters the scroll compressor, which compresses the air. As the pressure increases, the temperature also increases. The high-temperature air then enters the heat exchange device for cooling. The cooled compressed air then enters the molecular sieve to produce oxygen. The produced oxygen can enter the gas storage tank and then be supplied to the user through the oxygen outlet (the oxygen production process of the molecular sieve oxygen concentrator is existing technology and will not be described in detail).
[0118] Since this oxygen generator adopts all the technical solutions of the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be repeated here.
[0119] The terms "first," "second," and "third" in this application are used for descriptive purposes only and should not be construed as indicating the number of technical features indicated. Therefore, a feature defined as "first," "second," or "third" may explicitly or implicitly include at least one of those features. All directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of this application are only used to explain the relative positional relationships and movement of the components in a specific orientation (as shown in the figures). If the specific orientation changes, the directional indications will also change accordingly. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.
[0120] The above description is merely an embodiment of this application and does not limit the patent scope of this application. Any equivalent structural or procedural transformations made using the content of this application's specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of this application.
Claims
1. A scroll compressor characterized by, include: Static vortex disk; A moving scroll plate, one end of which meshes with the stationary scroll plate; The first crankshaft bearing has its outer ring connected to the end of the moving scroll away from the stationary scroll. A crankshaft, one end of which passes through the inner ring of the first crankshaft bearing; A first elastic ring is disposed between the first crankshaft bearing and the crankshaft.
2. The scroll compressor according to claim 1, characterized in that, The scroll compressor further includes an end cover, a second crankshaft bearing, and a second elastic ring. The end cover is disposed on the side of the moving scroll away from the stationary scroll. The outer ring of the second crankshaft bearing is connected to the end cover. The inner ring of the second crankshaft bearing is sleeved on the other end of the crankshaft. The second elastic ring is disposed between the crankshaft and the second crankshaft bearing.
3. The scroll compressor according to claim 2, characterized in that, The first elastic ring comprises at least two rings, which are arranged at intervals along the axial direction of the crankshaft; and / or, The second elastic ring comprises at least two rings, which are arranged at intervals along the axial direction of the crankshaft.
4. The scroll compressor according to claim 2, characterized in that, The scroll compressor also includes: A motor mount is provided on the side of the moving scroll away from the stationary scroll, and the moving scroll is at least partially housed in the motor mount. The third crankshaft bearing has its outer ring connected to the motor housing and its inner ring fitted onto the crankshaft. Along the axial direction of the crankshaft, the third crankshaft bearing is located between the first crankshaft bearing and the second crankshaft bearing.
5. The scroll compressor according to claim 4, characterized in that, The scroll compressor also includes a motor, which is connected to the end cover and the motor mount, and is also connected to the crankshaft.
6. The scroll compressor according to any one of claims 1-5, characterized in that, The scroll compressor also includes a crank, with the two ends of the crank connected to the moving scroll and the stationary scroll, respectively. The scroll compressor further includes a first crank bearing and a third elastic ring. The outer ring of the first crank bearing is connected to the moving scroll, and the inner ring of the first crank bearing is fitted onto the end of the crank away from the stationary scroll. The third elastic ring is disposed between the crank and the first crank bearing; and / or, The scroll compressor further includes a second crank bearing and a fourth elastic ring. The outer ring of the second crank bearing is connected to the stationary scroll, and the inner ring of the second crank bearing is sleeved on the end of the crank away from the moving scroll. The fourth elastic ring is disposed between the crank and the second crank bearing.
7. The scroll compressor according to any one of claims 1-5, characterized in that, The scroll compressor also includes a crank, a first crank bearing, a third elastic ring, a second crank bearing, and a fourth elastic ring; The outer ring of the first crank bearing is connected to the moving scroll, the inner ring of the first crank bearing is sleeved on the end of the crank away from the stationary scroll, and the third elastic ring is disposed between the crank and the first crank bearing. The outer ring of the second crank bearing is connected to the stationary scroll plate, the inner ring of the first crank bearing is sleeved on the end of the crank away from the moving scroll plate, and the fourth elastic ring is disposed between the crank and the second crank bearing. The number of the first crank bearings is at least two, and the at least two first crank bearings are arranged sequentially along the axial direction of the crank; and / or, The number of the second crank bearing is at least two, and the at least two second crank bearings are arranged sequentially along the axial direction of the crank; and / or, The number of the third elastic rings is at least two, and the at least two third elastic rings are arranged at intervals along the axial direction of the crank; and / or, The number of the fourth elastic rings is at least two, and the at least two fourth elastic rings are arranged at intervals along the axial direction of the crank.
8. The scroll compressor according to any one of claims 1-5, characterized in that, The scroll compressor further includes a crank, a first crank bearing, and a second crank bearing. The first crank bearing is connected to one end of the crank and the moving scroll, and the second crank bearing is connected to the other end of the crank and the stationary scroll. The scroll compressor further includes a first locking member, which is connected to the end of the crank away from the stationary scroll, and the end of the first crank bearing away from the stationary scroll abuts against the first locking member; and / or, The scroll compressor further includes a second locking member, which is connected to the end of the crank away from the moving scroll, and the end of the second crank bearing away from the moving scroll abuts against the second locking member.
9. The scroll compressor according to claim 8, characterized in that, The scroll compressor further includes a third elastic ring, which is disposed between the crank and the first crank bearing; and / or The scroll compressor further includes a fourth elastic ring, which is disposed between the crank and the second crank bearing.
10. An oxygen generator, characterized by comprising: include: The scroll compressor as described in any one of claims 1-9.