Compressor pump body and compressor
By setting a thinning zone and optimizing the design on the compressor bearing, the problem of the heavy upper bearing was solved, realizing lightweight and energy-saving manufacturing of the compressor, and reducing manufacturing costs and transportation expenses.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-09-02
- Publication Date
- 2026-03-10
AI Technical Summary
The existing compressors have a bulky upper bearing structure, which leads to waste of raw materials and increased logistics and transportation costs, making it difficult to achieve lightweight design and green energy-saving manufacturing.
Thinning zones are set on the first and second bearings of the compressor to ensure that the thickness is no more than 7.9mm. Combined with the design of annular flanges and chamfered surfaces, material consumption is reduced while maintaining structural strength.
By designing a thinning zone, the weight of the bearing is reduced, saving raw material consumption, lowering manufacturing costs and transportation expenses, and achieving lightweight and green energy-saving manufacturing of the compressor.
Smart Images
Figure CN121630739A_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application relates to the technical field of compression devices, in particular to a compressor pump body and a compressor. BACKGROUND
[0002] The upper bearing and the lower bearing are arranged on the cylinder in the rotary compressor, and the upper bearing and the lower bearing are used for supporting the crankshaft, and the upper bearing is further provided with an exhaust hole for discharging the compressed gas in the cylinder. At present, the structure of the upper bearing is single and bulky, and the excessive weight of the upper bearing will cause waste of raw materials for manufacturing the compressor and increase the logistics transportation cost of the compressor, which is not conducive to the lightweight design and green energy-saving manufacturing of the compressor product. SUMMARY
[0003] The main purpose of the present application is to provide a compressor pump body and a compressor to solve the problem that the excessive weight of the upper bearing in the compressor will cause waste of raw materials for manufacturing the compressor and increase the logistics transportation cost of the compressor.
[0004] According to one aspect of the present application, a compressor pump body is provided, comprising:
[0005] a crankshaft;
[0006] a compression mechanism, the compression mechanism comprising a cylinder and a bearing assembly, the cylinder being sleeved on one end of the crankshaft, the bearing assembly comprising a first bearing and a second bearing, the first bearing and the second bearing being sleeved on the crankshaft and being connected to opposite sides of the cylinder along the axial direction of the crankshaft, respectively, the first bearing being provided with an exhaust valve connecting seat and a thinning area, the exhaust valve connecting seat being located in the thinning area;
[0007] wherein, along the axial direction of the crankshaft, the first bearing has a first thickness at the thinning area, and the first thickness is not greater than 7.9mm.
[0008] Further, the first bearing comprises:
[0009] a disc body connected with the cylinder, the disc body comprising a first surface away from the cylinder;
[0010] a shaft handle protruding from the first surface, the shaft handle being provided with a first connecting hole, the first connecting hole penetrating through the disc body along the axial direction of the crankshaft, the crankshaft being arranged in the first connecting hole, and the thinning area being located on the disc body and arranged around the outer periphery of the shaft handle.
[0011] Further, the disc body has an annular flange protruding from the first surface and located at the outer periphery of the thinning area away from the shaft handle, a first chamfered surface is arranged on the side of the annular flange close to the shaft handle, and the distance between the first chamfered surface and the outer peripheral surface of the disc body gradually decreases in the radial direction of the crankshaft, and the minimum distance between the first chamfered surface and the outer peripheral surface of the disc body is greater than 0 mm and not greater than 1.5 mm.
[0012] Further, the maximum distance between the first chamfered surface and the outer peripheral surface of the disc body is not greater than 5.1 mm.
[0013] Further, in the axial direction of the crankshaft, the height of the outer peripheral surface of the disc body is K, and the ratio between K and the first thickness is not less than 1.01 and not greater than 2.
[0014] Further, the shaft handle comprises at least two connecting sections, the outer diameters of the at least two connecting sections are different and sequentially decrease in the direction away from the disc body, and the outer diameters of the at least two connecting sections gradually decrease in the direction away from the disc body.
[0015] Further, the connecting section comprises:
[0016] a first connecting section, the first connecting section is located on the side of the shaft handle close to the disc body, and the included angle between the outer peripheral surface of the first connecting section and the axis of the crankshaft is not less than 1° and not greater than 9°.
[0017] Further, the connecting section further comprises:
[0018] a second connecting section, the second connecting section is located on the side of the first connecting section away from the disc body, and the included angle between the outer peripheral surface of the second connecting section and the axis of the crankshaft is greater than 0° and not greater than 1.5°.
[0019] Further, the connecting section further comprises:
[0020] a third connecting section, the third connecting section is located on the side of the second connecting section away from the first connecting section, and the included angle between the outer peripheral surface of the third connecting section and the axis of the crankshaft is greater than 0° and not greater than 1.5°.
[0021] Further, a second chamfered surface is arranged between the shaft handle and the thinning area, and the included angle between the second chamfered surface and the thinning area is not less than 15° and not greater than 45°.
[0022] In another aspect, the application also provides a compressor comprising the compressor pump body.
[0023] In this application, at least one of the first and second bearings of the compressor pump body is provided with a thinning zone. Along the axial direction of the crankshaft, at least one of the first and second bearings has a first thickness at the thinning zone, which is no greater than 7.9 mm. This application reduces the weight of at least one of the first and second bearings by providing a thinning zone on at least one of the first and second bearings and ensuring that the first thickness of the corresponding bearing in the thinning zone is no greater than 7.9 mm. This saves on the raw material consumption required for manufacturing at least one of the first and second bearings, significantly reducing the manufacturing cost and logistics expenses of compressors using this compressor pump body. It achieves lightweight design and green energy-saving manufacturing of compressor products, possessing significant socio-economic value. Attached Figure Description
[0024] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings:
[0025] Figure 1 This is a schematic diagram of the structure of a compressor provided in one embodiment of this application;
[0026] Figure 2 This is a schematic diagram of the structure of the first bearing;
[0027] Figure 3 This is the front view of the first bearing;
[0028] Figure 4 for Figure 3 AA section view of the first bearing.
[0029] The above figures include the following reference numerals:
[0030] 10. Housing; 20. Motor; 21. Stator; 22. Rotor; 30. Compressor pump body; 31. Crankshaft; 32. Cylinder; 33. First bearing; 331. Disc; 311. First surface; 312. Thinning zone; 313. Annular flange; 314. First chamfered surface; 315. Clearance hole; 316. Exhaust valve connecting seat; 332. Shaft handle; 321. First connecting hole; 322. First connecting section; 323. Second connecting section; 324. Third connecting section; 325. Second chamfered surface; 34. Second bearing; 35. Muffler. Detailed Implementation
[0031] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.
[0032] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.
[0033] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.
[0034] A rotary compressor is a commonly used compression device in refrigeration and air conditioning systems. A rotary compressor includes a housing 10 and, within the housing 10, a motor 20 and a compressor pump body 30. The compressor pump body 30 mainly includes a crankshaft 31, a cylinder 32, and a first bearing 33 and a second bearing 34 connected to opposite sides of the cylinder 32 to support the crankshaft 31. The first bearing 33 is the upper bearing or main bearing, and the second bearing 34 is the lower bearing or auxiliary bearing. The upper bearing is located on the side of the cylinder 32 closest to the motor 20. Besides its supporting function, the upper bearing is also responsible for exhaust; therefore, it is usually equipped with an exhaust valve seat, a muffler 35, etc. The lower bearing mainly supports the distal end of the crankshaft 31 extending from the cylinder 32. The upper and lower bearings work together to prevent the rotating crankshaft 31 from twisting or shifting, improving the rotational accuracy and stability of the crankshaft 31. The motor 20 is used to drive the crankshaft 31 to rotate. The crankshaft 31 has an eccentric part, which is connected to the piston in the cylinder 32 through a connecting rod to drive the piston to rotate and compress the refrigerant gas entering the cylinder 32.
[0035] As precision equipment, compressors, in the context of market demands for increased precision, still face relatively high manufacturing and transportation costs. Therefore, there is still room for improvement in compressor structure. Through in-depth research, the inventors of this invention have discovered that the upper bearing in current compressors has a simple and bulky structure. The significant weight of the upper bearing leads to wasted raw materials in compressor manufacturing and increases logistics costs, hindering lightweight design and energy-efficient manufacturing. Therefore, aside from necessary bolt holes and standard thickness dimensions, the structure of the upper bearing in existing compressors still has room for improvement.
[0036] This invention aims to achieve a lightweight design for the lower bearing while maintaining the original mechanical properties of the upper bearing. This reduces the consumption of raw materials for manufacturing the lower bearing, thus addressing the problem of excessive weight in the upper bearing causing waste of raw materials and increased logistics costs in the compressor. To this end, the first embodiment of this invention provides a compressor pump body 30, please refer to [link to previous text]. Figures 1 to 4 The compressor pump body 30 includes a crankshaft 31 and a compression mechanism. The compression mechanism includes a cylinder 32 and a bearing assembly. The cylinder 32 is sleeved on one end of the crankshaft 31 so that the crankshaft 31 can drive the piston in the cylinder 32 to rotate under the drive of the motor 20 to compress the refrigerant gas. The bearing assembly of the compressor pump body 30 includes a first bearing 33 and a second bearing 34. The first bearing 33 and the second bearing 34 are sleeved on the crankshaft 31 and respectively connected to opposite sides of the cylinder 32 along the axial direction of the crankshaft 31.
[0037] The first bearing 33 is provided with an exhaust valve connecting seat 316 and a thinning zone 312. The exhaust valve connecting seat 316 is located within the thinning zone 312. The exhaust valve connecting seat 316 has a recessed structure, and an exhaust port is provided near the bottom of the cylinder 32 for discharging compressed gas from the cylinder 32. Along the axial direction of the crankshaft 31, the first bearing 33 has a first thickness at the thinning zone 312. It should be noted that the first thickness is the thickness of the first bearing 33 at the position in the thinning zone offset from the exhaust valve connecting seat 316 (i.e., the first thickness does not include the thickness of the first bearing 33 at the exhaust valve connecting seat 316). The first thickness is not greater than 7.9 mm (the first thickness is as follows). Figure 4(The thickness is indicated by H in the text). Since the first thickness of at least one of the first bearings 33 and 34 at the thinning region 312 is no greater than 7.9 mm, the weight of at least one of the first bearings 33 and 34 can be reduced, thus saving the amount of raw materials required to manufacture the first bearings 33 and 34. When the first bearing 33 is installed in the compressor housing 10, its outer peripheral wall needs to be connected to the inner peripheral surface of the housing 10, and the volume of the first bearing 33 is usually larger than that of the second bearing 34. Therefore, providing a thinning region 312 on the first bearing 33 can save more bearing raw material consumption and ensure the stability of the first bearing 33 and the second bearing 34 in supporting the crankshaft 31. As shown in Table 1, Table 1 shows the weight of the first bearing 33 in this embodiment when the first thickness at the thinning region 312 is at different sizes. The first bearing 33 with a first thickness greater than 7.9 mm is equivalent to an unthinned bearing structure currently available on the market.
[0038] First bearing 33 type First thickness H / mm Weight / gram First bearing a1 9.0 522 First bearing a2 8.5 474 First bearing a3 8.0 450 First bearing a4 7.9 432 First bearing a5 7.0 383 First bearing a6 6.5 355 First bearing a7 6.0 328
[0039] Table 1
[0040] As shown in Table 1, the weights of bearings a1, a2, and a3 with a first thickness greater than 7.9 mm are significantly greater than the weights of bearings a4 to a7. Furthermore, the smaller the first thickness, the more significant the weight reduction effect of the thinning zone 312 on the first bearing 33. Compared to bearings with a first thickness greater than 7.9 mm, bearings with a first thickness of no more than 7.9 mm have a thickness reduced to 75% to 90% of their original size, resulting in a weight reduction of 1% to 39%. For example, if the thickness of the thinning zone of the first bearing 33 in this embodiment is 9 mm, and the first thickness of the first bearing 33 in this embodiment is 6 mm, the weight of the first bearing 33 is reduced by 39% relative to the weight of the existing bearing product.
[0041] In this embodiment, the first thickness of the first bearing 33 in the thinning region 312 is not less than 6.0 mm, thereby ensuring that the first bearing 33 achieves effective weight reduction without reducing its structural strength due to insufficient first thickness.
[0042] Specifically, in this embodiment, the first thickness includes one of the following: 6.0mm, 6.1mm, 6.2mm, 6.3mm, 6.4mm, 6.5mm, 6.6mm, 6.7mm, 6.8mm, 6.9mm, 7.0mm, 7.1mm, 7.2mm, 7.3mm, 7.4mm, 7.5mm, 7.6mm, 7.7mm, 7.8mm, and 7.9mm. In this embodiment, the first thickness of the first bearing 33 falls within the aforementioned range, resulting in a weight less than that of conventional first bearings 33 without compromising structural strength.
[0043] As can be seen, in this embodiment, at least one of the first bearing 33 and the second bearing 34 of the compressor pump body 30 is provided with a thinning region 312. Along the axial direction of the crankshaft 31, at least one of the first bearing 33 and the second bearing 34 has a first thickness at the thinning region 312, which is no greater than 7.9 mm. This application provides a thinning region 312 on at least one of the first bearing 33 and the second bearing 34, and reduces the weight of at least one of the first bearing 33 and the second bearing 34 by ensuring that the first thickness of the corresponding bearing in the thinning region 312 is no greater than 7.9 mm. This saves on the consumption of raw materials required for manufacturing at least one of the first bearing 33 and the second bearing 34, significantly reducing the manufacturing cost and logistics costs of the compressor using this compressor pump body 30, achieving lightweight design and green energy-saving manufacturing of the compressor product, and possessing good socio-economic value.
[0044] In this embodiment, there can be one or more thinning regions 312. When there are multiple thinning regions 312, they can be set in different areas of the first bearing 33. For example, if the first bearing 33 includes a disc body 331 and a shaft 332, one or more thinning regions 312 can be set on the disc body 331 to reduce the weight of the first bearing 33. The disc body 331 of the first bearing 33 is connected to the cylinder 32, and the disc body 331 includes a first surface 311 facing away from the cylinder 32. The shaft 332 protrudes from the first surface 311, and a first connecting hole 321 is provided in the shaft 332. The first connecting hole 321 passes through the disc body 331 along the axial direction of the crankshaft 31, and the crankshaft 31 passes through the first connecting hole 321 so that the crankshaft 31 can rotate stably under the support of the shaft 332. The thinning zone 312 is located on the disc body 331 and surrounds the outer periphery of the shaft 332, forming a thin annular thinning zone 312 on the disc body 331. The annular thinning zone 312 is not only easy to manufacture, but also, due to its wider coverage on the disc body 331, has a more significant weight reduction effect on the first bearing 33, saving more manufacturing raw materials and reducing the manufacturing and transportation costs of the compressor with the first bearing 33. The disc body 331 also has multiple second connecting holes 314 arranged axially along the crankshaft 31, spaced apart circumferentially in the thinning zone 312. The disc body 331 is fixedly connected to the cylinder 32 by fasteners (such as bolts and studs) passing through the multiple second connecting holes 314.
[0045] In this embodiment, the disc 331 of the first bearing 33 has an annular flange 313, which protrudes from the first surface 311 and is located on the outer periphery of the thinning region 312 away from the shaft 332. When the first bearing 33 is connected to the cylinder 32 and installed into the compressor housing 10, the annular flange 313 can increase the connection area between the first bearing 33 and the inner wall of the housing 10, making the compressor pump body 30 more stable and reliable when operating in the housing 10. To reduce the weight of the first bearing 33, the annular flange 313 in this embodiment has a first chamfered surface 131 on the side near the shaft 332. Along the radial direction of the crankshaft 31, the minimum distance between the first chamfered surface 131 and the outer peripheral surface of the disc 331 (e.g., ...) is... Figure 4The spacing dimension indicated by the symbol L1 is greater than 0 mm and not greater than 1.5 mm. In other words, this embodiment reduces the weight of the first bearing 33 by using the thinning zone 312, and also narrows the radial width of the annular flange 313 along the crankshaft 31 by ensuring that the minimum distance between the first chamfered surface 131 on the annular flange 313 and the outer peripheral surface of the disc 331 is not greater than 1.5 mm. This not only does not reduce the structural strength of the disc 331 of the first bearing 33, but also makes the first bearing 33 lighter, saving more manufacturing raw materials, reducing the production cost of the first bearing 33, and consequently reducing the production and transportation costs of the compressor containing the first bearing 33.
[0046] Furthermore, in this embodiment, the minimum distance L1 between the first chamfered surface 131 and the outer peripheral surface of the disc 331 is greater than 0 mm and not greater than 1.5 mm. This not only reduces the weight of the first bearing 33, but also, since L1 has a certain width, after the annular flange 313 is formed on the disc 331, the annular flange 313 usually has some burrs. The size of L1 being within the above-mentioned range also facilitates the removal of burrs on the annular flange 313 by machining, thereby improving the product quality of the first bearing 33. Specifically, in this embodiment, the size of the minimum distance L1 between the first chamfered surface 131 and the outer peripheral surface of the disc 331 includes one of the following: 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1.0 mm, 1.1 mm, 1.2 mm, 1.3 mm, 1.4 mm, and 1.5 mm.
[0047] In some optional embodiments of the present invention, the first chamfer surface 131 can be either a planar chamfer surface or an arc-shaped chamfer surface. When the first chamfer surface 131 is a planar chamfer surface, if the first chamfer surface 131 is parallel to the axis of the crankshaft 31, then the longitudinal section of the annular flange 313 along the axial direction of the crankshaft 31 is a rectangular surface structure, and the width of the rectangular surface along the radial direction of the crankshaft 31 is greater than 0 mm and not greater than 1.5 mm. In this case, the annular flange 313 has a narrower flange structure, which can reduce the weight of the first bearing 33. Preferably, in this embodiment, the first chamfer surface 131 is set as an inclined surface so that the side of the annular flange 313 near the cylinder 32 is thicker, so that the annular flange 313 is narrower and lighter while having better strength.
[0048] Typically, the disc body 331 is also provided with multiple clearance holes 315, which are used to connect the space of the first bearing 33 near the cylinder 32 with the space of the first bearing 33 away from the cylinder 32. Along the circumference of the crankshaft 31, the multiple clearance holes 315 are spaced apart between the annular flange 313 and the thinning region 312. To prevent the angle of inclination of the first chamfered surface 131 relative to the outer circumferential surface of the disc body 331 from being too large and reducing the weight reduction effect, in this embodiment, the first chamfered surface 131 is located between the clearance hole 315 on the radial side of the crankshaft 31 away from the thinning region 312 and the outer circumferential surface of the disc body 331. The disc body 331 is also provided with an exhaust port, located in the thinning region 312, which is used to communicate with the compression chamber of the cylinder 32 to discharge the compressed gas from the exhaust port provided on the housing 10.
[0049] The maximum distance between the first chamfered surface 131 and the outer peripheral surface of the disc body 331 is no greater than 5.1 mm. This maximum distance is the thickness of the bottom of the annular flange 313 near the cylinder 32 along the radial direction of the crankshaft 31, i.e. Figure 4 The symbol L2 indicates the spacing dimension. In this embodiment, by ensuring that L2 is no greater than 5.1 mm, the weight of the first bearing 33 is reduced without compromising the structural strength of the annular flange 313. Specifically, the size of L2 includes one of the following: 5.1 mm, 5.06 mm, 5.04 mm, 5.02 mm, 4.8 mm, 4.8 mm, 4.7 mm, 4.5 mm, 4.3 mm, 4.1 mm, 4.0 mm, 3.8 mm, 3.5 mm, 3.3 mm, 3.2 mm, 3.0 mm, 2.9 mm, 2.8 mm, 2.6 mm, 2.4 mm, 2.3 mm, 2.0 mm, 1.8 mm, 1.5 mm, 1.4 mm, 1.3 mm, 1.2 mm, 1.1 mm, and 1.0 mm.
[0050] Along the axial direction of crankshaft 31, the height of the outer circumferential surface of disk 331 is K (e.g., Figure 4As shown), the ratio between K and the first thickness is not less than 1.01 and not greater than 2. That is, this embodiment achieves overall thinning and weight reduction of the disk body 331 by limiting the ratio between the height K of the outer peripheral surface of the disk body 331 and the first thickness to not less than 1.01 and not greater than 2, without reducing the structural strength of the first bearing 33. Specific ratios of K to the first thickness may include 1.01, 1.02, 1.04, 1.06, 1.08, 1.1, 1.12, 1.14, 1.16, 1.17, 1.18, 1.19, 1.2, 1.21, 1.23, 1.25, 1.27, 1.28, 1.3, 1.31, 1.32, 1.34, 1.35, 1.37, 1.39, 1.4, 1.41, 1.43, 1.45, 1... One of the following: 0.48, 1.49, 1.5, 1.52, 1.54, 1.56, 1.58, 1.6, 1.61, 1.63, 1.65, 1.67, 1.69, 1.7, 1.72, 1.74, 1.76, 1.78, 1.79, 1.8, 1.81, 1.83, 1.85, 1.87, 1.89, 1.9, 1.91, 1.93, 1.94, 1.96, 1.98, 2.0, etc.
[0051] Table 2 below shows the weight of the first bearing 33 when the height K of the outer circumferential surface of the disc 331 of the first bearing 33 is in different ranges.
[0052]
[0053] Table 2
[0054] As can be seen from Table 2, when the ratio between the height K and the first thickness (i.e., k / H) is not greater than 2, the smaller the k / H of the first bearing 33 in the first bearing b1 and the first bearing b7, the smaller its weight, and the weight reduction effect is significant. Conversely, if the k / H of the first bearing 33 is greater than 2, its weight will be larger, which is not conducive to the lightweighting of the first bearing 33 and the energy-saving manufacturing of the compressor.
[0055] This embodiment reduces the weight of the first bearing 33 while further improving its overall structural strength to ensure stable and reliable support for the crankshaft 31. In this embodiment, the shaft shank 332 of the first bearing 33 includes at least two connecting sections with different outer diameters that decrease sequentially away from the disc body 331; that is, the outer diameter of the connecting section closer to the disc body 331 is larger than that of the connecting section farther from the disc body 331. Furthermore, the outer diameter of at least two connecting sections gradually decreases away from the disc body 331. In other words, in this embodiment, at least two connecting sections of the shaft shank 332 retain a draft angle (the draft angle is the angle between the tangential direction of the side where the workpiece intersects the mold parting surface and the normal direction of the mold parting surface, artificially set to allow the workpiece to better detach from the mold), making at least two connecting sections conical in shape. Thus, this embodiment achieves weight reduction through the thinning zone 312 and the narrowing of the annular flange 313, while simultaneously enhancing the structural strength of the corresponding connecting sections. After the weight of the first bearing 33 is reduced, the connecting sections of the shaft 332 can still provide stable support for the crankshaft 31, ensuring the stability of the crankshaft 31 during rotation.
[0056] The connecting section of the shaft 332 includes a first connecting section 322, which is located on the side of the shaft 332 closest to the disc 331. The angle between the outer peripheral surface of the first connecting section 322 and the axis of the crankshaft 31 (hereinafter referred to as the first angle for ease of description) is not less than 1° and not greater than 9°. Specifically, the angle between the outer peripheral surface of the first connecting section 322 and the axis of the crankshaft 31 may include one of the following: 1°, 2°, 3°, 4°, 5°, 6°, 7°, 8°, or 9°. When the angle between the outer peripheral surface of the first connecting section 322 and the axis of the crankshaft 31 is within the above-mentioned angle range, not only is the structural strength of the first connecting section 322 ensured, but the weight reduction effect of the first bearing 33 in this embodiment is not reduced due to the first angle of the first connecting section 322. Through numerous experiments conducted by the inventors of this invention, it has been found that if the angle between the outer peripheral surface of the first connecting segment 322 and the axis of the crankshaft 31 is less than 1°, the overall structural strength of the first bearing 33 will be reduced. If the angle between the outer peripheral surface of the first connecting segment 322 and the axis of the crankshaft 31 is greater than 9°, the weight of the first bearing 33 will increase due to the presence of the draft angle, thus reducing the weight reduction effect of this embodiment on the first bearing 33.
[0057] When the first included angle of the first connecting section 322 is not less than 1° and not greater than 9°, the outer diameter of the first connecting section 322 along the axial direction of the crankshaft 31 on the side closer to the disc 331 is larger than the outer diameter on the side farther from the disc 331. Along the radial direction of the crankshaft 31, the side of the first connecting section 322 with the larger outer diameter (i.e., the bottom of the first connecting section 322 on the side closer to the disc 331) has a second thickness (e.g., ...). Figure 4As shown in d1). The second thickness of the first connecting segment 322 is not less than 5.6 mm and not greater than 6.6 mm. When the second thickness is within the aforementioned range, not only can the first bearing 33 improve its structural strength through the first included angle of the first connecting segment 322, but the presence of the first included angle will not reduce the weight reduction effect of the thinning area 312 and the narrow annular flange 313 on the first bearing 33. The second thickness may specifically include one of the following: 5.6 mm, 5.7 mm, 5.8 mm, 5.9 mm, 6.0 mm, 6.1 mm, 6.2 mm, 6.3 mm, 6.4 mm, 6.5 mm, or 6.6 mm.
[0058] In this embodiment, the connecting segment further includes a second connecting segment 323. The second connecting segment 323 is located on the side of the first connecting segment 322 away from the disc body 331. The angle between the outer peripheral surface of the second connecting segment 323 and the axis of the crankshaft 31 (hereinafter referred to as the second angle) is greater than 0° and not greater than 1.5°. The angle between the outer peripheral surface of the second connecting segment 323 and the axis of the crankshaft 31 may specifically include one of 0.5°, 1°, 1.1°, 1.2°, 1.3°, 1.4°, and 1.5°. Similarly, when the second angle of the second connecting segment 323 is within the above-mentioned angle range, not only can the structural strength of the second connecting segment 323 be ensured, but the weight reduction effect of the first bearing 33 in this embodiment will not be reduced due to the second angle of the second connecting segment 323.
[0059] When the second included angle of the second connecting segment 323 is greater than 0° and not greater than 1.5°, the outer diameter of the second connecting segment 323 along the axial direction of the crankshaft 31 closer to the first connecting segment 322 is larger than the outer diameter of the side farther from the first connecting segment 322. Along the radial direction of the crankshaft 31, the side of the second connecting segment 323 with the larger outer diameter (i.e., the bottom of the second connecting segment 323 closer to the first connecting segment 322) has a third thickness (e.g., ...). Figure 4 (as shown in d2). The third thickness is not less than 3.2 mm and not more than 4.2 mm. When the third thickness is within the aforementioned range, it not only allows the first bearing 33 to improve its structural strength through the second included angle of the second connecting section 323, but also ensures that the presence of the second included angle does not reduce the weight reduction effect of the thinning region 312 and the narrow annular flange 313 on the first bearing 33. Specifically, the third thickness may include one of the following: 3.2 mm, 3.3 mm, 3.4 mm, 3.5 mm, 3.6 mm, 3.7 mm, 3.8 mm, 3.9 mm, 4.0 mm, 4.1 mm, or 4.2 mm.
[0060] In this embodiment, the connecting segment further includes a third connecting segment 324. The third connecting segment 324 is located on the side of the second connecting segment 323 away from the first connecting segment 322. The angle between the outer peripheral surface of the third connecting segment 324 and the axis of the crankshaft 31 (hereinafter referred to as the third angle) is greater than 0° and not greater than 1.5°. The angle between the outer peripheral surface of the third connecting segment 324 and the axis of the crankshaft 31 may specifically include one of 0.5°, 1°, 1.1°, 1.2°, 1.3°, 1.4°, and 1.5°. Similarly, when the third angle of the third connecting segment 324 is within the above-mentioned angle range, not only can the structural strength of the third connecting segment 324 be ensured, but the weight reduction effect of the first bearing 33 in this embodiment will not be reduced due to the third angle on the third connecting segment 324.
[0061] When the third included angle of the third connecting section 324 is greater than 0° and not greater than 1.5°, the outer diameter of the third connecting section 324 along the axial direction of the crankshaft 31 is larger on the side closer to the second connecting section 323 than on the side farther from the second connecting section 323. Along the radial direction of the crankshaft 31, the side of the third connecting section 324 with the larger outer diameter (i.e., the bottom of the third connecting section 324 closer to the second connecting section 323) has a fourth thickness (e.g., ...). Figure 4 (as shown in d3). The fourth thickness is not less than 1.5 mm and not more than 2.5 mm. When the fourth thickness is within the aforementioned range, it not only allows the first bearing 33 to improve its structural strength through the third included angle of the third connecting section 324, but also ensures that the presence of the third included angle does not reduce the weight reduction effect of the thinning area 312 and the narrow annular flange 313 on the first bearing 33. The fourth thickness may specifically include one of the following: 1.5 mm, 1.6 mm, 1.7 mm, 1.8 mm, 1.9 mm, 2.0 mm, 2.1 mm, 2.2 mm, 2.3 mm, 2.4 mm, or 2.5 mm.
[0062] Furthermore, in order to further improve the overall structural strength of the first bearing 33 while reducing its weight, this embodiment provides a second chamfered surface 325 between the shaft shank 332 and the thinning region 312. The included angle between the second chamfered surface 325 and the thinning region 312 (e.g., Figure 4 The angle (indicated by the symbol α) is not less than 15° and not greater than 45°. The included angle α between the second chamfered surface 325 and the axis of the crankshaft 31 can specifically include one of the following: 15°, 16°, 18°, 20°, 21°, 23°, 25°, 26°, 28°, 30°, 31°, 32°, 35°, 36°, 38°, 40°, 41°, 42°, 43°, 44°, or 45°. When α is within the above angle range, it not only does not affect the weight reduction of the first bearing 33 in this embodiment, but also improves the overall structural strength of the first bearing 33, reducing the compressor's production and transportation costs without reducing the compressor's operating performance.
[0063] The second embodiment of the present invention also provides a compressor, which includes the compressor pump body 30 mentioned in the first embodiment of the present invention. The compressor further includes a housing 10 and a motor 20, which is installed within the housing 10. The motor 20 includes a stator 21 and a rotor 22. The rotor 22 is rotatably disposed within the stator 21 and is connected to the end of the crankshaft 31 away from the cylinder 32 of the compressor pump body 30 to drive the crankshaft 31 to rotate. The compressor pump body 30 is disposed within the housing 10 and connected to the inner peripheral wall of the housing 10. The compressor pump body 30 also includes a second bearing 34 and a muffler 35. The first bearing 33 of the compressor pump body 30 is connected to the side of the cylinder 32 near the motor 20 and is connected to the inner peripheral wall of the housing 10. The second bearing 34 is connected to the side of the cylinder 32 away from the motor 20. The muffler 35 is disposed on the side of the first bearing 33 away from the cylinder 32. For details on the structure of the first bearing 33 of the compressor pump body 30, please refer to the content provided in the first embodiment of the present invention; it will not be repeated here.
[0064] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.
[0065] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.
[0066] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.
Claims
1. A compressor pump body characterized by, The application relates to a crankshaft (31) and a compression mechanism. The compression mechanism comprises a cylinder (32) and a bearing assembly, the cylinder (32) is sleeved on one end of the crankshaft (31), the bearing assembly comprises a first bearing (33) and a second bearing (34), the first bearing (33) and the second bearing (34) are sleeved on the crankshaft (31) and are connected to opposite sides of the cylinder (32) along the axial direction of the crankshaft (31), the first bearing (33) is provided with an exhaust valve connecting seat (316) and a thinning area (312), and the exhaust valve connecting seat (316) is located in the thinning area (312). The first bearing (33) has a first thickness at the thinning area (312) along the axial direction of the crankshaft (31), and the first thickness is not greater than 7.9 mm. The first bearing (33) comprises:
2. The compressor pump body of claim 1, wherein, a disc body (331) connected to the cylinder (32), the disc body (331) comprises a first surface (311) facing away from the cylinder (32); a shaft handle (332) protruding from the first surface (311), the shaft handle (332) is provided with a first connecting hole (321), the first connecting hole (321) penetrates the disc body (331) along the axial direction of the crankshaft (31), the crankshaft (31) penetrates the first connecting hole (321), and the thinning area (312) is located on the disc body (331) and is annularly arranged on the outer periphery of the shaft handle (332). The disc body (331) has an annular flange (313) protruding from the first surface (311) and located away from the outer periphery of the shaft handle (332) at the thinning area (312), a first chamfer surface (131) is arranged on the side of the annular flange (313) close to the shaft handle (332), along the radial direction of the crankshaft (31), the distance between the first chamfer surface (131) and the outer peripheral surface of the disc body (331) gradually decreases in the direction away from the cylinder (32), and the minimum distance between the first chamfer surface (131) and the outer peripheral surface of the disc body (331) is greater than 0 mm and not greater than 1.5 mm.
3. The compressor pump body of claim 2, wherein, The maximum distance between the first chamfer surface (131) and the outer peripheral surface of the disc body (331) is not greater than 5.1 mm.
4. The compressor pump body of claim 3, wherein, Along the axial direction of the crankshaft (31), the height of the outer peripheral surface of the disc body (331) is K, the ratio between K and the first thickness is not less than 1.01 and not greater than 2.
5. The compressor pump body of claim 2, wherein, The shaft handle (332) comprises at least two connecting sections, the outer diameters of the at least two connecting sections are different and sequentially decrease in the direction away from the disc body (331), and the outer diameters of the at least two connecting sections gradually decrease in the direction away from the disc body (331).
6. The compressor pump body of any one of claims 2 to 5, wherein, The connecting section comprises:
7. The compressor pump body of claim 6, wherein, A first connecting section (322) is located on a side of the shaft handle (332) close to the disc body (331), and an included angle between an outer circumferential surface of the first connecting section (322) and an axis of the crankshaft (31) is not less than 1° and not more than 9°.
8. The compressor pump body of claim 7, wherein, The connecting section further comprises: A second connecting section (323) is located on a side of the first connecting section (322) away from the disc body (331), and an included angle between an outer circumferential surface of the second connecting section (323) and the axis of the crankshaft (31) is greater than 0° and not more than 1.5°.
9. The compressor pump body of claim 8, wherein, The connecting section further comprises: A third connecting section (324) is located on a side of the second connecting section (323) away from the first connecting section (322), and an included angle between an outer circumferential surface of the third connecting section (324) and the axis of the crankshaft (31) is greater than 0° and not more than 1.5°.
10. The compressor pump body of claim 6, wherein, A second chamfered surface (325) is arranged between the shaft handle (332) and the thinning area (312), and an included angle between the second chamfered surface (325) and the thinning area (312) is not less than 15° and not more than 45°.
11. A compressor characterized by, The compressor comprises the compressor pump body (30) according to any one of claims 1 to 10.