Compressor and air conditioner having the same

Abstract

The present invention provides a compressor and an air conditioner having the same. The compressor includes a crankshaft, on which a plurality of eccentric portions are provided, the plurality of eccentric portions including a first eccentric portion and a second eccentric portion; a crankshaft balance block, the crankshaft balance block being connected to the end of the crankshaft, the first eccentric portion, the second eccentric portion, and the crankshaft balance block being arranged in sequence downward along the axis of the crankshaft; wherein the center distance between the crankshaft balance block and the first eccentric portion is L2, and the center distance between the crankshaft balance block and the second eccentric portion is L3, and 0.35≤L3 / L2≤0.75. This arrangement can effectively reduce deformation of the crankshaft during high-speed operation, reduce friction damage between the crankshaft and internal components of the compressor, and reduce vibration of the compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of air-conditioning equipment, and in particular to a compressor and an air conditioner having the same. Background Art

[0002] In the field of compressor technology, in order to maintain the dynamic balance of the shaft system, conventional balancing blocks are designed at both ends of the motor rotor. However, during the high-speed operation of the compressor, the centrifugal force of the balancing block will increase sharply, resulting in increased deflection of the crankshaft end, thereby causing abnormal problems such as motor bore scraping, bearing wear, and increased power consumption.

[0003] Prior art methods have used balancing weights on the lower stub shaft of the crankshaft to reduce the weight of the balancing weights required on the upper end of the motor rotor, thereby minimizing deformation of the eccentric crankshaft. However, adding balancing weights directly to the stub shaft of the crankshaft increases localized deformation of the stub shaft. Because the balancing weights are close to the secondary bearing and cylinder, this increases wear on the secondary bearing and exacerbates compressor vibration. Summary of the Invention

[0004] The main purpose of the present invention is to provide a compressor and an air conditioner having the same, so as to solve the problem of easy wear of the crankshaft in the prior art.

[0005] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, a compressor is provided, comprising: a crankshaft, on which a plurality of eccentric portions are arranged, the plurality of eccentric portions including a first eccentric portion and a second eccentric portion; a crankshaft balance block, the crankshaft balance block being connected to the end portion of the crankshaft, the first eccentric portion, the second eccentric portion and the crankshaft balance block being arranged in sequence downward along the axial direction of the crankshaft; wherein the center distance between the crankshaft balance block and the first eccentric portion is L2, the center distance between the crankshaft balance block and the second eccentric portion is L3, and 0.35≤L3 / L2≤0.75.

[0006] Furthermore, the crankshaft has a long shaft section and a short shaft section, the crankshaft balance block is connected to the short shaft section, the maximum eccentric distance between the crankshaft balance block and the crankshaft is R5, and the distance from the end of the short shaft section to the geometric center of the crankshaft balance block is L4, where 0.5≤R5 / L4≤0.8.

[0007] Furthermore, the crankshaft has a long shaft section and a short shaft section, the crankshaft balance block is connected to the short shaft section, and an oil suction pipe is provided on the end face of the short shaft section. The maximum eccentric distance between the crankshaft balance block and the crankshaft is R5, and the distance from the end of the oil suction pipe to the geometric center of the crankshaft balance block is L5, where 0.5≤R5 / L5≤0.8.

[0008] Furthermore, the compressor also includes: a rotor, the long shaft section of the crankshaft is connected to the rotor, and a rotor balancing block is provided on the end face of the rotor facing the short shaft section of the crankshaft, and the center of mass of the rotor balancing block is arranged relative to the center of mass of the crankshaft balancing block with a phase difference of 180°.

[0009] Furthermore, an external thread is provided on at least a portion of the outer peripheral surface of the short shaft section of the crankshaft.

[0010] Furthermore, the cross section of the short shaft section of the crankshaft is a D-shaped structure.

[0011] Furthermore, the first end of the crankshaft balance block is connected to the crankshaft, the second end of the crankshaft balance block is extended along the radial direction of the crankshaft, and the cross-section from the first end to the second end of the crankshaft balance block is gradually increased.

[0012] Furthermore, the short shaft section of the crankshaft is provided with a stop step, and the compressor also includes a nut, which is sleeved on the short shaft section, and the crankshaft balance block is located between the nut and the stop step.

[0013] Further, m1*R1=m4*R4=m2*R2*(L2-L3) / L1, wherein m1 is the mass of the rotor balancing block; m2 is the mass of the first eccentric part; m4 is the mass of the crankshaft balancing block; R1 is the eccentric distance between the rotor balancing block and the axis center of the crankshaft; R2 is the eccentric distance between the first eccentric part and the axis center of the crankshaft; R4 is the eccentric distance between the crankshaft balancing block and the axis center of the crankshaft; L1 is the center distance between the rotor balancing block and the crankshaft balancing block; L2 is the center distance between the first eccentric part and the crankshaft balancing block; L3 is the center distance between the second eccentric part and the crankshaft balancing block.

[0014] Furthermore, the first eccentric portion (11) and the second eccentric portion (12) have the same mass.

[0015] According to another aspect of the present invention, an air conditioner is provided, comprising a compressor, wherein the compressor is the above-mentioned compressor.

[0016] The technical solution of the present invention is applied to a crankshaft, wherein the center distance between the crankshaft balance weight and the first eccentric portion is L2, and the center distance between the crankshaft balance weight and the second eccentric portion is L3, and 0.35≤L3 / L2≤0.75. This arrangement effectively reduces crankshaft deformation during high-speed operation, reduces friction damage between the crankshaft and internal components of the compressor, and reduces compressor vibration. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The accompanying drawings, which constitute part of this application, are intended to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are intended to explain the present invention and do not constitute an undue limitation of the present invention. In the accompanying drawings:

[0018] Figure 1 It shows a structural schematic diagram of a first embodiment of a compressor according to the present invention;

[0019] Figure 2 It shows a structural schematic diagram of a second embodiment of a compressor according to the present invention;

[0020] Figure 3 shows a schematic structural diagram of a compressor according to a third embodiment of the present invention;

[0021] Figure 4 A schematic structural diagram of an embodiment of a crankshaft balancing block according to the present invention is shown;

[0022] Figure 5 A schematic structural diagram of an embodiment of a crankshaft according to the present invention is shown;

[0023] Figure 6 A comparison diagram of the contact stress of the auxiliary bearing of the compressor and the vibration effect of the compressor according to the present invention is shown.

[0024] The above drawings include the following reference numerals:

[0025] 10. Crankshaft; 11. First eccentric portion; 12. Second eccentric portion;

[0026] 20. Crankshaft balance block;

[0027] 30. Oil suction pipe;

[0028] 40. Rotor; 41. Rotor balancing weight;

[0029] 50. Nut. DETAILED DESCRIPTION

[0030] It should be noted that, in the absence of conflict, the embodiments and features of the embodiments in this application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0031] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0032] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way are interchangeable where appropriate, so that the embodiments of the present application described herein can, for example, be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0033] Now, exemplary embodiments according to the present application will be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in a variety of different forms and should not be interpreted as being limited to the embodiments described herein. It should be understood that these embodiments are provided to make the disclosure of this application thorough and complete, and to fully convey the concepts of these exemplary embodiments to those of ordinary skill in the art. In the accompanying drawings, for the sake of clarity, the thickness of layers and regions may be exaggerated, and the same reference numerals are used to represent the same devices, and thus their descriptions will be omitted.

[0034] Combine Figures 1 to 6 As shown, according to a specific embodiment of the present application, a compressor is provided.

[0035] Specifically, if Figures 1 to 2 As shown, the compressor includes a crankshaft 10 and a crankshaft balancer 20. The crankshaft 10 is provided with a plurality of eccentric portions. The plurality of eccentric portions include a first eccentric portion 11 and a second eccentric portion 12. The crankshaft balancer 20 is connected to the end of the crankshaft 10, and the first eccentric portion 11, the second eccentric portion 12, and the crankshaft balancer 20 are arranged in sequence downward along the axial direction of the crankshaft 10. The center distance between the crankshaft balancer 20 and the first eccentric portion 11 is L2, and the center distance between the crankshaft balancer 20 and the second eccentric portion 12 is L3, and 0.35≤L3 / L2≤0.75.

[0036] In this embodiment, a crankshaft balancing weight 20 is provided on the crankshaft, and the center distance between the crankshaft balancing weight 20 and the first eccentric portion 11 is L2, and the center distance between the crankshaft balancing weight 20 and the second eccentric portion 12 is L3, and 0.35≤L3 / L2≤0.75. This arrangement can effectively reduce deformation of the crankshaft during high-speed operation, reduce friction damage between the crankshaft and internal components of the compressor, and reduce vibration of the compressor.

[0037] The crankshaft 10 has a long section and a short section, with the crankshaft counterweight 20 connected to the short section. The maximum eccentric distance between the crankshaft counterweight 20 and the crankshaft 10 is R5, and the distance from the end of the short section to the geometric center of the crankshaft counterweight 20 is L4, where 0.5 ≤ R5 / L4 ≤ 0.8. This arrangement effectively reduces crankshaft disturbances and further improves crankshaft reliability.

[0038] According to another embodiment of the present application, Figure 3 As shown, the crankshaft 10 has a long section and a short section. The crankshaft balancer 20 is connected to the short section. An oil suction pipe 30 is provided on the end face of the short section. The maximum eccentric distance between the crankshaft balancer 20 and the crankshaft 10 is R5. The distance from the end of the oil suction pipe 30 to the geometric center of the crankshaft balancer 20 is L5, where 0.5 ≤ R5 / L5 ≤ 0.8. This arrangement effectively reduces crankshaft disturbances and improves crankshaft reliability.

[0039] The compressor further includes a rotor 40. The long section of the crankshaft 10 is connected to the rotor 40. A rotor balancing weight 41 is provided on the end surface of the rotor 40 facing the short section of the crankshaft 10. The center of mass of the rotor balancing weight 41 is positioned 180° out of phase with the center of mass of the crankshaft balancing weight 20. This arrangement reduces the stability of the compressor's internal components, thereby reducing compressor vibration.

[0040] like Figure 5 As shown, at least a portion of the outer circumference of the short shaft section of the crankshaft 10 is provided with external threads. This arrangement improves the stability and reliability of the installation of the crankshaft balance weight 20. The short shaft section of the crankshaft 10 has a D-shaped cross-section. That is, the sidewall of the crankshaft is provided with anti-cutting surfaces, which improves the installation accuracy of the crankshaft balance weight 20.

[0041] In order to further improve the installation stability of the crankshaft balancing weight 20, a stop step is provided on the short shaft section of the crankshaft 10. The nut 50 is sleeved on the short shaft section, and the crankshaft balancing weight 20 is located between the nut 50 and the stop step.

[0042] like Figure 4 As shown, the first end of the crankshaft balancing weight 20 is connected to the crankshaft 10, and the second end of the crankshaft balancing weight 20 extends in the radial direction of the crankshaft 10. The cross-section of the crankshaft balancing weight 20 gradually increases from the first end to the second end. This arrangement can improve the balancing effect of the crankshaft balancing weight 20, wherein the outer contour line of the crankshaft balancing weight 20 is arranged in a fan-shaped structure.

[0043] Further, m1*R1=m4*R4=m2*R2*(L2-L3) / L1, wherein m1 is the mass of the rotor balancing weight 41; m2 is the mass of the first eccentric portion 11, m4 is the mass of the crankshaft balancing weight 20, R1 is the eccentric distance between the rotor balancing weight 41 and the axis of the crankshaft 10, R2 is the eccentric distance between the first eccentric portion 11 and the axis of the crankshaft 10, R4 is the eccentric distance between the crankshaft balancing weight 20 and the axis of the crankshaft 10, L1 is the center distance between the rotor balancing weight 41 and the crankshaft balancing weight 20, L2 is the center distance between the first eccentric portion 11 and the crankshaft balancing weight 20, and L3 is the center distance between the second eccentric portion 12 and the crankshaft balancing weight 20. This arrangement can improve the stability and reliability of the entire compressor. In an embodiment, the mass of the first eccentric portion 11 and the second eccentric portion 12 are the same. Wherein, as Figure 2 As shown, m3 is the mass of the second eccentric portion 12 , and R3 is the eccentric distance between the second eccentric portion 12 and the axis center of the crankshaft 10 .

[0044] The compressor in the above embodiment can also be used in the technical field of air-conditioning equipment. That is, according to another aspect of the present invention, an air conditioner is provided, comprising a compressor, which is the compressor in the above embodiment.

[0045] Under high-frequency operating conditions, conventional balancing weight designs are not conducive to reducing deformation of the top of the crankshaft (the long shaft section), which can cause compressor vibration and reliability issues. Adding balancing weights to the short shaft of the crankshaft will increase local deformation of the short shaft, increase wear on the secondary bearing, and aggravate compressor vibration problems.

[0046] The balancing block installation structure proposed in the technical solution of the present application can not only reduce the deformation of the long shaft section of the crankshaft under high-speed operation conditions, but also solve the wear problems of the auxiliary bearing and the vibration problems of the compressor caused by the deformation of the short shaft section.

[0047] The balancing block installation method of the present application can greatly improve the reliability of the compressor shaft system under high-speed working conditions and reduce the vibration and noise of the compressor caused by the shaft system.

[0048] Figure 1This is a schematic diagram of the structure of the proposed solution. The compressor includes a crankshaft, a rotor, an oil suction pipe, a rotor balancing weight, and a crankshaft balancing weight. The crankshaft includes a long shaft section, a short shaft section, a first eccentric section, and a second eccentric section. The rotor balancing weight is placed on the lower end surface of the rotor, while the crankshaft balancing weight is placed below the second eccentric section of the crankshaft and fixed to the short shaft of the crankshaft. The rotor balancing weight is placed on the opposite side of the crankshaft balancing weight, with a phase difference of 180°, and the rotor balancing weight is located on the opposite side of the first eccentric section. For a two-cylinder compressor, the first and second eccentrics have the same mass. To ensure static and couple balance of the shaft system, the equation m1*R1=m4*R4=m2*R2*(L2-L3) / L1 should be met, where m1 and m4 are the masses of the rotor balancing mass and the crankshaft balancing mass, respectively, and m2 is the sum of the masses of the first eccentric and the roller. R1, R2, and R4 represent the eccentric distances between the centers of mass of the rotor balancing mass, the first eccentric, and the crankshaft balancing mass, respectively. L1, L2, and L3 represent the height distances between the centers of mass of the rotor balancing mass, the first eccentric, and the second eccentric, respectively, and the center of mass of the crankshaft balancing mass. However, the crankshaft balancing mass can cause significant deformation of the crankshaft stub shaft and is located close to the counterbearing and eccentric. This can exacerbate compressor vibration and increase the risk of counterbearing wear. Research has found that controlling the L3 / L2 ratio to meet the ratio 0.35≤L3 / L2≤0.75 can effectively address counterbearing wear and compressor vibration. Figure 6 The following curves show how the compressor counterbearing contact stress and vibration acceleration change with the L3 / L2 ratio. When L3 / L2 is less than 0.35, the localized load caused by the centrifugal force of the crankshaft counterweight significantly affects the counterbearing contact stress, leading to a significant increase in counterbearing wear. When L3 / L2 is greater than 0.75, the stub shaft length increases, the crankshaft counterweight's center of gravity shifts downward, and the centrifugal force-induced stub shaft deflection increases, compromising crankshaft stability and significantly exacerbating compressor vibration and noise.

[0049] During operation, the crankshaft balance block will be immersed in the refrigerant oil of the compressor. Due to the eccentric structure of the balance block, vortices will be generated on the surface of the oil pool. When the compressor speed increases, the depth of the vortex on the oil pool surface will increase, thereby affecting the oil suction of the oil suction pipe or the oil hole at the end of the crankshaft stub, resulting in a blocked oil circuit of the compressor and compressor reliability problems. According to research, in order to ensure the smooth flow of the oil circuit, it is necessary to ensure that: 0.5≤R5 / L4≤0.8. For structures with an oil suction pipe, L5 represents the distance from the end of the oil suction pipe to the center of the crankshaft balance block, such as Figure 1 、 Figure 3 As shown. For the structure without oil suction pipe, Figure 2 As shown in FIG, L4 represents the distance from the short shaft end of the crankshaft to the center of the crankshaft balance block. R5 represents the maximum eccentric distance of the crankshaft balance block.

[0050] Placing a rotor balancing block on the lower end face of the rotor and eliminating the balancing block on the upper end face of the rotor can minimize the deflection of the crankshaft top while ensuring the balance of the shaft system, thereby increasing the reliability of the compressor under high-speed conditions and reducing the vibration of the compressor.

[0051] In this solution, the rotor balancing weight can be fastened to the rotor by screws. As for the crankshaft balancing weight, its shape and fixing method are not limited. Figure 4 This diagram shows one type of balancing weight structure. The balancing weight can be fixed to the crankshaft stub by shrink fitting. The crankshaft stub is machined into a stepped shaft to provide axial positioning for the balancing weight. The tail of the stub is machined into a D-shape to provide circumferential positioning for the balancing weight, ensuring a 180° phase difference between the rotor balancing weight and the crankshaft balancing weight.

[0052] In the above scheme, the crankshaft balance block is fixed on the short shaft by shrink sleeve or by nut. The tail area of ​​the crankshaft short shaft is processed into external thread, and after the crankshaft balance block is installed, it is fixed by nut. Figure 5 shown.

[0053] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0054] In addition to the above, it should be noted that references to "one embodiment," "another embodiment," "an embodiment," and the like in this specification refer to specific features, structures, or characteristics described in conjunction with that embodiment as included in at least one embodiment generally described in this application. The appearance of the same expression in multiple places in the specification does not necessarily refer to the same embodiment. Furthermore, when a specific feature, structure, or characteristic is described in conjunction with any embodiment, it is intended that such feature, structure, or characteristic, when implemented in conjunction with other embodiments, also falls within the scope of the present invention.

[0055] In the above embodiments, the description of each embodiment has its own focus. For parts that are not described in detail in a certain embodiment, reference can be made to the relevant descriptions of other embodiments.

[0056] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention are intended to be within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that: include: A crankshaft (10), wherein the crankshaft (10) is provided with a plurality of eccentric portions, the plurality of eccentric portions including a first eccentric portion (11) and a second eccentric portion (12); a crankshaft balancing block (20), the crankshaft balancing block (20) being connected to an end portion of the crankshaft (10), the first eccentric portion (11), the second eccentric portion (12), and the crankshaft balancing block (20) being arranged in sequence downwardly along the axis direction of the crankshaft (10); The center distance between the crankshaft balancing weight (20) and the first eccentric portion (11) is L2, the center distance between the crankshaft balancing weight (20) and the second eccentric portion (12) is L3, and 0.35≤L3 / L2≤0.75; The crankshaft (10) has a long shaft section and a short shaft section, the crankshaft balancing block (20) is connected to the short shaft section, the maximum eccentric distance between the crankshaft balancing block (20) and the crankshaft (10) is R5, and the distance from the end of the short shaft section to the geometric center of the crankshaft balancing block (20) is L4, wherein 0.5≤R5 / L4≤0.

8.

2. The compressor according to claim 1, characterized in that An oil suction pipe (30) is provided on the end surface of the short shaft section, and the distance from the end of the oil suction pipe (30) to the geometric center of the crankshaft balance block (20) is L5, wherein 0.5≤R5 / L5≤0.

8.

3. The compressor according to claim 1, characterized in that The compressor further comprises: A rotor (40) is connected to the long shaft section of the crankshaft (10), and a rotor balancing block (41) is provided on the end surface of the rotor (40) facing the short shaft section of the crankshaft (10), wherein the center of mass of the rotor balancing block (41) is arranged opposite to the center of mass of the crankshaft balancing block (20) with a phase difference of 180 degrees.

4. The compressor according to claim 1, characterized in that At least a portion of the outer peripheral surface of the short shaft section of the crankshaft (10) is provided with an external thread.

5. The compressor according to claim 1, characterized in that The cross section of the short shaft section of the crankshaft (10) is in a D-shaped structure.

6. The compressor according to claim 1, characterized in that The first end of the crankshaft balancing block (20) is connected to the crankshaft (10), the second end of the crankshaft balancing block (20) is extended along the radial direction of the crankshaft (10), and the cross-section of the crankshaft balancing block (20) is gradually increased from the first end to the second end of the crankshaft balancing block (20).

7. The compressor according to claim 1, characterized in that The short shaft section of the crankshaft (10) is provided with a stop step. The compressor further comprises a nut (50), the nut (50) being sleeved on the short shaft section, and the crankshaft balance block (20) being located between the nut (50) and the stop step.

8. The compressor according to claim 3, characterized in that m1×R1=m4×R4=m2×R2×(L2-L3) / L1, where m1 is the mass of the rotor balancing block (41); m2 is the mass of the first eccentric portion (11); m4 is the mass of the crankshaft balance block (20); R1 is the eccentric distance between the rotor balancing weight (41) and the axis of the crankshaft (10); R2 is the eccentric distance between the first eccentric portion (11) and the axis of the crankshaft (10); R4 is the eccentric distance between the center of mass of the crankshaft balance block (20) and the axis of the crankshaft (10); L1 is the center distance between the rotor balancing block (41) and the crankshaft balancing block (20).

9. The compressor according to claim 1, characterized in that The first eccentric portion (11) and the second eccentric portion (12) have the same mass.

10. An air conditioner comprising a compressor, characterized in that: The compressor is the compressor according to any one of claims 1 to 9.

Images