Vertical compressor

Abstract

The utility model discloses a vertical compressor. The vertical compressor comprises a main body part and a shell part. Wherein the main body part comprises a pump body assembly and a motor, and the motor is in driving connection with the pump body assembly; the shell component comprises a shell and a plurality of bottom feet, the main body component is arranged in the shell, the bottom feet are arranged on the periphery, close to the bottom, of the shell at intervals, the projections of the bottom feet are located on the periphery of the projection of the shell in the height direction of the shell, and the first-order inherent frequency omega of the bottom feet in the height direction of the shell meets the relational expression that omega is larger than or equal to 1400 Hz and smaller than or equal to 1700 Hz. The vertical compressor at least can solve the problems that in the prior art, the bottom foot surface area of a vertical compressor is large, resonance is prone to occurring between the bottom foot surface area and main working components of the compressor, and therefore large vibration noise is generated.

Description

TECHNICAL FIELD

[0001] The utility model relates to refrigeration equipment technical field, specifically, stand type compressor. BACKGROUND

[0002] The compressor is the core component of the refrigeration equipment, and usually comprises a closed shell, a pump body assembly, a motor, a gas-liquid separator, a suction pipe and a discharge pipe.

[0003] In the prior art, the main working components of the compressor are enclosed in the shell, and the feet are connected to the lower part of the compressor shell by welding to form an integral body, thereby supporting the compressor. When the compressor is working, the vibration and noise generated by the internal working components will be transmitted or radiated to the outside through the feet. At present, the internal vibration and noise excitation of the compressor is complex, and there are specific excitations in different frequency bands. The natural frequency of the feet is often distributed in a specific frequency band, which causes the feet to easily resonate with the main working components of the compressor. In addition, the thickness of the feet of the compressor is relatively thin and the surface area is large, that is, it has a large noise radiation area, thereby generating a large vibration noise. SUMMARY

[0004] The main purpose of the utility model is to provide a stand type compressor, which at least solves the problem that the surface area of the feet of the stand type compressor in the prior art is large and easily resonates with the main working components of the compressor, thereby generating a large vibration noise.

[0005] According to one aspect of the utility model, a stand type compressor is provided, comprising:

[0006] A main body component comprising a pump body assembly and a motor, the motor being drivingly connected to the pump body assembly;

[0007] A shell component comprising a shell and a plurality of feet, the main body component being arranged in the shell, the shell being provided with a plurality of feet at an outer periphery near the bottom, and in the height direction of the shell, the projection of the feet is located at the outer periphery of the projection of the shell, and the first order natural frequency ω of the feet in the height direction of the shell satisfies the relationship: 1400Hz≤ω≤1700Hz.

[0008] Further, the total surface area S of each foot satisfies the relationship: 2200mm 2 ≤S≤3000mm 2 .

[0009] Further, the feet comprise a mounting section and an extension section connected to the mounting section, the mounting section being connected to the outer peripheral surface of the shell, and the extension section extending in a direction away from the shell.

[0010] Further, a relationship 0.3≤H / L≤0.5 is satisfied between the height H of the mounting section and the length L of the epitaxial section.

[0011] Further, the mounting section includes a first side close to the housing, and a bump is arranged on the first side, and the mounting section is welded to the housing through the bump.

[0012] Further, the epitaxial section is in a strip shape, and a width W of the epitaxial section satisfies a relationship 26mm≤W≤34mm.

[0013] A thickness T of the epitaxial section satisfies a relationship 2.2mm≤T≤3.3mm.

[0014] A length L of the epitaxial section satisfies a relationship 34mm≤L≤36mm.

[0015] Further, a circular mounting hole is arranged on the epitaxial section, and a radius R of the circular mounting hole satisfies a relationship 9mm≤R≤12mm.

[0016] Further, a relationship 0.7≤W / L≤1.1 is satisfied between the width W of the epitaxial section and the length L of the epitaxial section.

[0017] Further, a relationship 0.07≤T / W≤0.13 is satisfied between the thickness T of the epitaxial section and the width W of the epitaxial section.

[0018] Further, a relationship 0.2≤R / L≤0.4 is satisfied between the radius R of the circular mounting hole and the length L of the epitaxial section.

[0019] In the utility model, the vertical compressor includes a main body component and a shell component. Among them, the main body component is the core component of the compressor, through the common action of the pump body assembly and the motor, the series process of gas suction, compression and discharge is realized. In the application, the shell component includes a shell and a plurality of feet, the main body component is arranged in the shell, and a plurality of feet are arranged at the outer periphery of the shell near the bottom, the plurality of feet can ensure the stability of the equipment, reduce vibration and facilitate installation and fixation. Specifically, in the height direction of the shell, the projection of the foot is located at the outer periphery of the projection of the shell, so as to improve the overall performance of the vertical compressor, including stability, safety and maintenance convenience. And in the application, the first order natural frequency ω of the foot in the height direction of the shell satisfies the relationship: 1400Hz≤ω≤1700Hz. Among them, the first order natural frequency refers to the frequency of free vibration of the system without external excitation, and the first order natural frequency is the frequency of the most basic and easiest vibration mode of the foot of the compressor. Generally, the working frequency of the compressor and its components is small, but in the actual working process, the moving parts (such as piston, crankshaft, etc.) of the compressor will excite the pump body assembly to produce vibration of a certain frequency band, and in some cases, it is in the 2000Hz frequency band. In the application, the first order natural frequency of the foot of the vertical compressor is set in the range of 1400Hz-1700Hz, the foot can avoid the excitation frequency of the compressor in this frequency band to a certain extent, so as to reduce the resonance, optimize the noise performance of the compressor, reduce the overall noise of the air conditioner and other equipment, and improve the market competitiveness of the product. BRIEF DESCRIPTION OF DRAWINGS

[0020] The drawings described herein are used to provide further understanding of the utility model, constitute a part of the utility model, the illustrative embodiment of the utility model and its explanation are used to explain the utility model, and do not constitute improper limitation to the utility model. In the drawings:

[0021] Figure 1 The schematic diagram of the vertical compressor disclosed by the embodiment of the utility model is shown in the figure;

[0022] Figure 2 The structure schematic diagram of the foot of the vertical compressor disclosed by the embodiment of the utility model is shown in the figure;

[0023] Figure 3 The schematic diagram of the related size of the foot of the vertical compressor disclosed by the embodiment of the utility model is shown in the figure;

[0024] Figure 4 The top view of the extension section of the foot of the vertical compressor disclosed by the embodiment of the utility model is shown in the figure.

[0025] Among them, the above drawings include the following figure marks:

[0026] 10, housing part; 11, housing; 12, foot; 121, mounting section; 1211, protrusion; 122, extension section; 1221, circular mounting hole. DETAILED DESCRIPTION

[0027] It should be noted that the embodiments and features in the embodiments of the present application can be combined with each other without conflict. The present application will be described in detail below with reference to the drawings and in combination with the embodiments.

[0028] It should be noted that the terms used herein are only intended to describe specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form unless the context clearly indicates otherwise, and it should also be understood that the terms "comprise" and / or "include" as used herein indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0029] Unless specifically stated otherwise, the relative arrangements of components and steps, numerical expressions, and numerical values set forth in the various embodiments described herein are not meant to limit the scope of the present application. At the same time, it should be understood that the dimensions of the various parts shown in the drawings are not drawn to scale for the sake of convenience of description. Techniques, methods, and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered as part of the authorized description where appropriate. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary, and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference numbers and letters represent similar items in the following drawings, and therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0030] As mentioned in the background, in the prior art, the internal vibration noise excitation of the compressor is complex, and there are specific excitations in different frequency bands. The natural frequency of the foot is often distributed in a specific frequency band, which causes the foot to easily resonate with the main working components of the compressor. In addition, the thickness of the foot of the compressor is relatively thin and the surface area is large, i.e. it has a large noise radiation area, thereby generating a large vibration noise. Therefore, the present application provides a vertical compressor, the foot of which has the characteristics of specific natural frequency, small noise radiation area, less material usage, and small contact area with the housing, and the foot natural frequency span is large, which facilitates the control of the natural frequency of the foot by combining the size parameters to achieve noise design. The vertical compressor of the present application will be described in detail below with reference to the drawings.

[0031] Referring to Figures 1 to 4As shown, the application provides a vertical compressor. The vertical compressor comprises a main body component and a shell component 10.

[0032] In the application, the main body component (not shown in the figure) comprises a pump body assembly (not shown in the figure) and a motor (not shown in the figure), and the motor is drivingly connected with the pump body assembly; the shell component 10 comprises a shell 11 and a plurality of feet 12, the main body component is arranged in the shell 11, the shell 11 is provided with a plurality of feet 12 at intervals on the outer periphery close to the bottom, and in the height direction of the shell 11, the projection of the foot 12 is located on the outer periphery of the projection of the shell 11, and the first order natural frequency ω of the foot 12 in the height direction of the shell 11 satisfies the relationship: 1400Hz≤ω≤1700Hz.

[0033] In the application, the vertical compressor comprises a main body component and a shell component 10. Among them, the main body component is the core component of the compressor, through the joint action of the pump body assembly and the motor, it realizes the series process of gas suction, compression and discharge. In the application, the shell component 10 comprises a shell 11 and a plurality of feet 12, the main body component is arranged in the shell 11, and a plurality of feet 12 are arranged at intervals on the outer periphery close to the bottom of the shell 11, which can ensure the stability of the equipment, reduce vibration and facilitate installation and fixation. Specifically, in the height direction of the shell 11, the projection of the foot 12 is located on the outer periphery of the projection of the shell 11, which can improve the overall performance of the vertical compressor, including stability, safety and maintenance convenience. And in the application, the first order natural frequency ω of the foot 12 in the height direction of the shell 11 satisfies the relationship: 1400Hz≤ω≤1700Hz. Among them, the first order natural frequency refers to the frequency of free vibration of the system without external excitation, and the first order natural frequency is the frequency of the most basic and easiest vibration mode of the foot 12 of the compressor. Generally, the working frequency of the compressor and its components is small, but in the actual working process, the moving parts of the compressor (such as piston, crankshaft, etc.) will excite the pump body assembly to produce vibration of a certain frequency band, and in some cases, it is in the 2000Hz frequency band. In the application, the first order natural frequency of the foot 12 of the vertical compressor is set in the range of 1400Hz-1700Hz, the foot 12 can avoid the excitation frequency of the compressor in this frequency band to a certain extent, so as to reduce the resonance, optimize the noise performance of the compressor, reduce the overall noise of the air conditioning equipment, and improve the market competitiveness of the product.

[0034] Specifically, in the present application, in the height direction of the shell 11, the projection of the foot 12 is located at the outer periphery of the projection of the shell 11, so that the foot 12 supports the compressor, which helps to reduce the risk of equipment overturning caused by external force, thereby improving the stability of the equipment; the foot 12 also provides a loose operating space, which is conducive to the installation and maintenance of the installation and maintenance personnel; the foot 12 also helps to reduce the influence of heat conduction and is conducive to optimizing vibration and noise absorption effect.

[0035] Exemplarily, in the present application, the number of feet 12 can be 3, 4, 5, etc., and the specific number is not limited in the present application. In actual production process, the appropriate number of feet 12 can be selected according to the size and installation requirements of the vertical compressor. Figure 1 The case where four feet 12 are provided is shown. In addition, in the present application, the first-order natural frequency can be 1400Hz, 1500Hz, 1600Hz, 1700Hz, etc. In the present application, the specific value is not limited, as long as the first-order natural frequency of the foot 12 is within this range.

[0036] As shown in Figures 1 to 3 , the total surface area S of each foot 12 satisfies the relationship: 2200mm 2 ≤S≤3000mm 2 In the present application, the first-order natural frequency is related to the mass, stiffness, shape and size, material properties of the foot 12, and the connection between the foot 12 and the shell 11. In the present application, the first-order natural frequency of the foot 12 is mainly adjusted by controlling the size of the foot 12. When the total surface area of one foot 12 on the compressor is within 2200mm 2 -3000mm 2 , the first-order natural frequency ω of the foot 12 can be ensured within the range of 1400Hz-1700Hz, thereby reducing the resonance between the foot 12 and the main working parts of the vertical compressor, and further reducing the vibration and noise of the vertical compressor, prolonging the service life of the vertical compressor. In addition, setting the surface area of each foot 12 within the range of 2200mm 2 -3000mm 2 also helps to ensure the stability of the vertical compressor installation; evenly disperses the pressure to avoid excessive local pressure causing damage or deformation of the foot 12, etc. Of course, in other embodiments of the present application, the range of the surface area of a single foot 12 can be changed in the actual application process according to the specific model and purpose of the compressor.

[0037] Further, as shown in Figure 2 and Figure 3As shown, the foot 12 includes a mounting section 121 connected with the outer circumferential surface of the shell 11 and an extension section 122 connected with the mounting section 121 and extending away from the shell 11. In the mounting section 121, the width of the mounting section 121 gradually increases from top to bottom, i.e., the mounting section 121 is narrow at the top and wide at the bottom. Such arrangement improves the overall stability of the device, improves the damping performance, meets the manufacturing requirements, facilitates the installation of the foot 12, and the like. In the present application, the mounting section 121 is connected with the outer circumferential surface of the shell 11 to ensure the stability of the device, reduce vibration, and facilitate installation and fixation. Specifically, in the present application, the extension section 122 is integrally formed with the mounting section 121, the extension section 122 extends away from the shell 11 and is connected with the mounting section 121 perpendicularly. The perpendicular connection helps to increase the overall structural stability of the foot 12, and can also optimize the force transmission path, so that the force transmitted from the vertical compressor to the foot 12 and then to the device foundation or the ground is as direct and evenly distributed as possible, and the support effectiveness of the foot 12 is improved, thereby reducing vibration. In addition, the perpendicular arrangement also facilitates the installation of the vertical compressor in the device such as the air conditioner cabinet, and the like. In addition, the corners of the extension section 122 are provided with rounded corners, which can reduce the risk of scratching during transportation.

[0038] Referring to Figure 3 As shown, the height H of the mounting section 121 and the length L of the extension section 122 satisfy the relationship: 0.3≤H / L≤0.5. Exemplarily, the value of H / L can be 0.3, 0.35, 0.4, 0.45, 0.5, and the like. When the ratio of the height H of the mounting section 121 to the length L of the extension section 122 is within the range of 0.3-0.5, it is beneficial to optimize the support performance of the foot 12, improve the rigidity and stability of the overall structure, and also improve the damping performance: when H / L is between 0.3-0.5, the foot 12 can effectively absorb and disperse the vibration energy generated by the operation of the compressor, reduce the amount of vibration transmitted to the ground or other support structure, thereby reducing noise and protecting the device from vibration damage. Such arrangement can also avoid stress concentration in a certain part, reduce the risk of fatigue damage, and prolong the service life of the device. In addition, it is also beneficial to reduce the materials required during the production of the foot 12, reduce the production cost, and the mass of the foot 12, thereby improving the first order natural frequency of the foot 12.

[0039] As Figure 2As shown, the mounting segment 121 includes a first side close to the shell 11, and the first side is provided with the protrusions 1211, and the mounting segment 121 is welded to the shell 11 through the protrusions 1211. Specifically, the first side of the mounting segment 121 is provided with an arc shape matched with the shell 11, and the arc shape design is more conducive to uniformly distributing mechanical stress caused by factors such as vibration, thermal expansion or external load; and the arc shape design can provide better structural support, so that the mounting segment 121 and the shell 11 are more firmly combined, etc. And the first side of the mounting segment 121 is provided with the protrusions 1211, wherein the number of the protrusions 1211 can be 1, 2, 3, 4, etc. Figure 2 and Figure 3 The case where the number of the protrusions 1211 is 3 is shown in FIG. 12. In the present application, the specific number of the protrusions 1211 is not limited, and the number of the protrusions 1211 can be designed according to actual production needs. In the present application, the protrusions 1211 are provided to facilitate the welding positioning of the foot 12, and the welding is more firm. In addition, the excitation generated by the main part of the vertical compressor is transmitted to the foot 12 through the mounting segment 121, so as to cause the foot 12 to vibrate, and the foot 12 is connected to the shell 11 of the compressor through the protrusions 1211, and there is a smaller vibration transmission path, so that the vibration reduction effect can be achieved. Specifically, in the present application, the mounting segment 121 and the shell 11 can be fixedly connected by means of fusion welding, pressure welding, brazing, etc.

[0040] Further, the protrusions 1211 on the mounting segment 121 are arranged according to the actual shape of the mounting segment 121 to ensure that the mounting segment 121 can be fixedly connected with the shell 11 of the compressor. In this application, along the height direction of the mounting segment 121 from top to bottom, the distance D1 between the protrusion 1211 closest to the top of the mounting segment 121 and the top of the mounting segment 121 and the height H of the mounting segment 121 satisfy the relationship: 0.3≤D1 / H≤0.4; the distance D2 between the protrusion 1211 closest to the bottom of the mounting segment 121 and the bottom of the mounting segment 121 and the height H of the mounting segment 121 satisfy the relationship: 0.2≤D2 / H≤0.3. Exemplarily, the value of D1 / H can be 0.3, 0.35, 0.4, etc.; the value of D2 / H can be 0.2, 0.25, 0.3, etc. When the values of D1 / H and D2 / H both satisfy the corresponding requirements, it can be ensured that the mounting segment 121 has a large enough connection area to resist the load moment. In addition, when the values of D1 / H and D2 / H are both within the above-mentioned range, the stress distribution can be optimized, the stress on the welding area and its periphery is more uniform, the stress concentration phenomenon is reduced, thereby reducing the risk of cracking caused by fatigue or overload. In this way, the rigidity of the structure can also be improved, and the appropriate position of the protrusion 1211 can enhance the connection strength between the foot 12 and the shell 11, thereby improving the rigidity and stability of the entire structure; the welding quality can also be improved, which ensures that the heat distribution during the welding process is more uniform, which is helpful to form a high-quality weld, reduce the occurrence of welding defects, etc., thereby effectively prolonging the service life of the equipment.

[0041] Again referring to Figure 3 and Figure 4 It is shown that the extension segment 122 is in a strip shape. The width W of the extension segment 122 satisfies the relationship: 26mm≤W≤34mm; exemplarily, the value of the width W of the extension segment 122 can be 26mm, 27mm, 30mm, 31mm, 34mm, etc. The thickness T of the extension segment 122 satisfies the relationship: 2.2mm≤T≤3.3mm, exemplarily, the value of the thickness T of the extension segment 122 can be 2.2mm, 2.5mm, 2.7mm, 3.1mm and 3.3mm, etc., and the thickness T of the extension segment 122 will affect the quality distribution and rigidity of the foot 12. In addition, the length L of the extension segment 122 satisfies the relationship: 34mm≤L≤36mm, exemplarily, the value of the length L of the extension segment 122 can be 34mm, 34.5mm, 35mm, 35.5mm and 36mm, etc.

[0042] In the present application, the first order natural frequency and the surface area of the foot 12 are mainly adjusted by controlling the length, width, thickness of the epitaxial segment 122 and the radius of the circular mounting hole 1221 provided on the epitaxial segment 122. Specifically, the length, width and thickness of the epitaxial segment 122 all affect the rigidity and mass distribution of the foot 12. Among them, the first order natural frequency of the foot 12 is proportional to the rigidity of the structure and inversely proportional to the mass. Specifically, when the width and thickness of the epitaxial segment 122 remain unchanged, increasing its length will cause its mass to increase, thereby causing the first order natural frequency of the foot 12 to decrease; when the length and thickness of the epitaxial segment 122 remain unchanged, increasing its width will increase the mass of the foot 12, while also enhancing the lateral rigidity of the foot 12. Among them, the increase in mass will cause the first order natural frequency of the foot 12 to decrease, while the increase in rigidity will increase the first order natural frequency of the foot 12, but the actual specific effect depends on the relative change between mass and rigidity. When the length and width of the epitaxial segment 122 remain unchanged, increasing its thickness will increase the rigidity of the foot 12, especially the bending rigidity, thereby causing the first order natural frequency of the foot 12 to increase; but as the thickness increases, it will affect the stability and dynamic response characteristics of the entire device. In the present application, the width, thickness and length of the epitaxial segment 122 are not specifically limited, and appropriate values are selected according to actual needs during production. When the width, thickness and length of the epitaxial segment 122 are all within the above-mentioned limited range, the first order natural frequency of the foot 12 can be effectively controlled, avoiding resonance with the main working parts of the compressor, while also enabling the foot 12 to meet the requirements of mechanical strength, stability and vibration reduction.

[0043] Referring again to Figure 3 As shown, the circular mounting hole 1221 is provided at the center position of the epitaxial segment 122. The radius R of the circular mounting hole 1221 satisfies the relationship: 9mm≤R≤12mm. Exemplarily, the value of R can be 9mm, 10mm, 11mm and 12mm, etc., which is not specifically limited in the present application and can be selected according to actual needs. Providing the circular mounting hole 1221 on the epitaxial segment 122 not only facilitates stable installation of the device, but also provides installation flexibility, simplifies the installation process, enhances the safety and stability of the device, and also provides a guarantee for long-term reliable operation of the device. In addition, providing the circular mounting hole 1221 on the epitaxial segment 122 can also reduce the surface area of the foot 12, so that the vibration noise radiation area is small when the vertical compressor is working, reducing the noise; providing the circular mounting hole 1221 also reduces the mass of the foot 12, which is conducive to improving the first order natural frequency of the foot 12. However, in actual design, the radius of the circular mounting hole 1221 needs to be reasonably designed to ensure safe and stable operation of the device.

[0044] Further, the bottom of the extension section 122 is also provided with a damping rubber layer having a certain thickness, which can make the foot 12 and the air conditioner and other equipment connected through flexibility, effectively absorb and buffer the vibration generated during the operation of the equipment, and has good damping effect; the damping rubber layer can also tolerate the slight displacement of the foundation due to unevenness or thermal expansion and cold contraction to some extent; the damping rubber layer can also improve the stable operation of the equipment and prolong the service life of the equipment. In addition, in the present application, the foot 12 is made of carbon steel, mainly because carbon steel has the advantages of high strength, good toughness, high cost-effectiveness, good processing performance and good dimensional stability, etc. Using carbon steel to prepare the foot 12 of the compressor can not only ensure the safe and reliable operation of the equipment, but also reduce the production cost and is also beneficial to processing. In the present application, the elastic modulus of the carbon steel is between 190GPa and 210GPa, so that the vibration can be effectively absorbed, the resonance risk can be reduced, and the compressor and related equipment can be protected while ensuring sufficient supporting strength and stability.

[0045] Further, the width W of the extension section 122 and the length L of the extension section 122 satisfy the relationship: 0.7≤W / L≤1.1. Exemplarily, the value of W / L can be 0.7, 0.8, 0.9, 1.0, 1.1, etc. When the value is within the above range, the design of the foot 12 can be optimized to achieve the best stability and damping effect. Specifically, when the width W of the extension section 122 and the length L of the extension section have a proper ratio, it is beneficial to improve the first-order natural frequency of the foot 12 to avoid resonance between the compressor and the foot 12, thereby improving the stability, load distribution and reducing local stress concentration of the entire equipment; it also improves the damping performance, absorbs and relieves the vibration generated during the operation of the equipment, protects the equipment from damage and reduces noise propagation; it also optimizes the space utilization, and when the ratio is within the above range, the installation space of the vertical compressor in the air conditioner and other equipment can be saved.

[0046] Further, the thickness T of the extension section 122 and the width W of the extension section 122 satisfy the relationship: 0.07≤T / W≤0.13. Exemplarily, the value of T / W can be 0.07, 0.09, 0.11, 0.13, etc. When the ratio of the thickness T and the width W of the extension section 122 is within the above range, the foot 12 can have sufficient rigidity to resist deformation, thereby improving the first-order natural frequency of the foot 12, reducing the resonance risk, prolonging the service life of the equipment and ensuring the long-term stable operation of the equipment; it also makes the foot 12 better isolate the vibration from the main working parts of the compressor, reduces the possibility of these vibrations being transmitted to the base of the air conditioner and other equipment and the ground, etc.

[0047] In the present application, the relationship between the radius R of the circular mounting hole 1221 and the length L of the epitaxial segment 122 satisfies the relationship: 0.2≤R / L≤0.4. Exemplarily, the value of R / L can be 0.2, 0.25, 0.3, 0.4, etc. When the ratio between the radius of the circular mounting hole 1221 on the epitaxial segment 122 and the length L of the epitaxial segment 122 is within the above range, it can be ensured that the compressor can be stably fixed on its base or support structure. If the value of R / L is greater than 0.4, it may cause the bolt to loosen, resulting in unstable operation of the equipment; if R / L is less than 0.2, it may increase the difficulty of installation. When R / L is within the above range, stress concentration problems caused by vibration can be reduced, which helps to improve the fatigue resistance of the entire foot 12 and prolong the service life of the equipment; it can also ensure that the connecting members such as bolts provide sufficient fastening force while not excessively restricting the foot 12, allowing the foot 12 to have a certain elastic deformation to absorb vibration. In addition, when R / L is within the above range, it is beneficial to simplify the installation process and adapt to certain manufacturing tolerances, without affecting the final installation quality and use performance.

[0048] In order to verify the influence of the size ratio of the epitaxial segment 122 of the foot 12 in the present application on the first-order natural frequency of the foot 12, the present application provides the following specific examples and comparative examples:

[0049] Example 1

[0050] In the present embodiment, the length of the epitaxial segment 122 is 34 mm, the width is 32 mm, the thickness is 3 mm, and the radius of the circular mounting hole 1221 is 10 mm. The surface area of the foot 12 is measured to be 2730 mm 2 , and the first-order natural frequency of the foot 12 is measured to be 1691 Hz.

[0051] Example 2

[0052] The size of the epitaxial segment 122 in Example 2 is basically the same as that in Example 1, except that in the present embodiment, the width of the epitaxial segment 122 is 26 mm. The surface area of the foot 12 is measured to be 2223 mm 2 , and the first-order natural frequency of the foot 12 is measured to be 1682 Hz.

[0053] Example 3

[0054] The size of the epitaxial segment 122 in Example 3 is basically the same as that in Example 1, except that in the present embodiment, the width of the epitaxial segment 122 is 34 mm. The surface area of the foot 12 is measured to be 2858 mm 2 , and the first-order natural frequency of the foot 12 is measured to be 1635 Hz.

[0055] Example 4

[0056] The dimensions of the epitaxial section 122 in Example 4 were substantially the same as in Example 1, except that in this example the length of the epitaxial section 122 was 36 mm. The surface area of the foot 12 was measured to be 2920 mm 2 The first order natural frequency of the foot 12 was measured to be 1466 Hz.

[0057] Example 5

[0058] The dimensions of the epitaxial section 122 in Example 5 were substantially the same as in Example 1, except that in this example the thickness of the epitaxial section 122 was 2.5 mm. The surface area of the foot 12 was measured to be 2665 mm 2 The first order natural frequency of the foot 12 was measured to be 1425 Hz.

[0059] Example 6

[0060] The dimensions of the epitaxial section 122 in Example 6 were substantially the same as in Example 1, except that in this example the radius of the circular mounting hole 1221 of the epitaxial section 122 was 9 mm. The surface area of the foot 12 was measured to be 2880 mm 2 The first order natural frequency of the foot 12 was measured to be 1700 Hz.

[0061] Example 7

[0062] The dimensions of the epitaxial section 122 in Example 7 were substantially the same as in Example 1, except that in this example the radius of the circular mounting hole 1221 of the epitaxial section 122 was 12 mm. The surface area of the foot 12 was measured to be 2491 mm 2 The first order natural frequency of the foot 12 was measured to be 1650 Hz.

[0063] Comparative Example 1

[0064] In this example, the length of the epitaxial section 122 was 28 mm, the width was 24 mm, the thickness was 2 mm, and the radius of the circular mounting hole 1221 was 7 mm. The surface area of the foot 12 was measured to be 3762 mm 2 The first order natural frequency of the foot 12 was measured to be 824 Hz.

[0065] Comparative Example 2

[0066] In this example, the length of the epitaxial section 122 was 40 mm, the width was 36 mm, the thickness was 3.5 mm, and the radius of the circular mounting hole 1221 was 13 mm. The surface area of the foot 12 was measured to be 3969 mm 2 The first order natural frequency of the foot 12 was measured to be 1199 Hz.

[0067] Comparative Example 3

[0068] The dimensions of the epitaxial section 122 in Comparative Example 3 were substantially the same as in Example 1, except that in this example the width of the epitaxial section 122 was 35 mm. The surface area of the footing 12 was measured to be 2802 mm 2 The first order natural frequency of the footing 12 was measured to be 1721 Hz.

[0069] Comparative Example 4

[0070] The dimensions of the epitaxial section 122 in Comparative Example 4 were substantially the same as in Example 1, except that in this example the width of the epitaxial section 122 was 25 mm. The surface area of the footing 12 was measured to be 2082 mm 2 The first order natural frequency of the footing 12 was measured to be 1619 Hz.

[0071] Comparative Example 5

[0072] The dimensions of the epitaxial section 122 in Comparative Example 5 were substantially the same as in Example 1, except that in this example the length of the epitaxial section 122 was 38 mm. The surface area of the footing 12 was measured to be 3010 mm 2 The first order natural frequency of the footing 12 was measured to be 1289 Hz.

[0073] Comparative Example 6

[0074] The dimensions of the epitaxial section 122 in Comparative Example 6 were substantially the same as in Example 1, except that in this example the length of the epitaxial section 122 was 30 mm. The surface area of the footing 12 was measured to be 2450 mm 2 The first order natural frequency of the footing 12 was measured to be 2412 Hz.

[0075] Comparative Example 7

[0076] The dimensions of the epitaxial section 122 in Comparative Example 7 were substantially the same as in Example 1, except that in this example the thickness of the epitaxial section 122 was 2 mm. The surface area of the footing 12 was measured to be 2612 mm 2 The first order natural frequency of the footing 12 was measured to be 1115 Hz.

[0077] Comparative Example 8

[0078] The dimensions of the epitaxial section 122 in Comparative Example 8 were substantially the same as in Example 1, except that in this example the thickness of the epitaxial section 122 was 3.5 mm. The surface area of the footing 12 was measured to be 2813 mm 2 The first order natural frequency of the footing 12 was measured to be 1972 Hz.

[0079] Comparative Example 9

[0080] The size of the epitaxial segment 122 in Comparative Example 9 is substantially the same as that in Example 1, except that the radius of the circular mounting hole 1221 of the epitaxial segment 122 is 7 mm in this example. The surface area of the footing 12 is measured to be 3044 mm 2 The first order natural frequency of the footing 12 is measured to be 1721 Hz.

[0081] Comparative Example 10

[0082] The size of the epitaxial segment 122 in Comparative Example 10 is substantially the same as that in Example 1, except that the radius of the circular mounting hole 1221 of the epitaxial segment 122 is 13 mm in this example. The surface area of the footing 12 is measured to be 2403 mm 2 The first order natural frequency of the footing 12 is measured to be 1622 Hz.

[0083] Table 1

[0084]

[0085] According to Table 1: By comparing Example 1, Example 2, Example 3, Comparative Example 3 and Comparative Example 4, it can be seen that when the length and thickness of the epitaxial segment 122 of the footing 12 and the radius of the circular mounting hole 1221 provided on the epitaxial segment 122 remain unchanged, as the size of the width gradually increases, the first order natural frequency of the footing 12 first increases and then decreases. And when the other sizes of the epitaxial segment 122 of the footing 12 remain unchanged, when the width is less than 26 mm, the first order natural frequency of the footing 12 meets the requirements, but the surface area of the footing 12 is less than 2200 mm 2 , which does not meet the requirements, so it does not meet the requirements of the present application; when the width of the epitaxial segment 122 is greater than 34 mm, the first order natural frequency of the footing 12 is greater than 1700 Hz, and the surface area is within the required range, also does not meet the requirements of the present application. But when the width of the epitaxial segment 122 is within 26 mm-34 mm, both the first order natural frequency of the footing 12 and the surface area of the footing 12 meet the requirements of the present application, and the resonance situation can be avoided.

[0086] As can be seen from Comparative Example 1, Example 4, Comparative Example 5 and Comparative Example 6, when the other dimensions of the epitaxial segment 122 remain unchanged, the first-order natural frequency of the foot 12 gradually decreases as the length dimension of the epitaxial segment 122 increases. When the length dimension of the epitaxial segment 122 is less than 34 mm, the first-order natural frequency of the foot 12 is greater than 1700 Hz, which does not meet the requirements of the present application; when the length dimension of the epitaxial segment 122 is greater than 36 mm, the first-order natural frequency of the foot 12 is less than 1400 Hz, which does not meet the requirements of the present application. However, when the length of the epitaxial segment 122 is within 34 mm-36 mm, both the first-order natural frequency of the foot 12 and the surface area of the foot 12 meet the requirements of the present application, and the resonance condition can be avoided.

[0087] As can be seen from Comparative Example 1, Example 5, Comparative Example 7 and Comparative Example 8, when the other dimensions of the epitaxial segment 122 of the foot 12 remain unchanged, the surface area of the foot 12 gradually increases and the first-order natural frequency of the foot 12 also gradually increases as the thickness dimension of the epitaxial segment 122 increases. However, when the thickness of the epitaxial segment 122 is less than 2.2 mm, the first-order natural frequency of the foot 12 is less than 1400 Hz, which does not meet the requirements of the present application; when the thickness is greater than 3.3 mm, the first-order natural frequency of the foot 12 is greater than 1700 Hz, which also does not meet the requirements of the present application. When the thickness of the epitaxial segment 122 is within 2.2 mm-3.3 mm, both the first-order natural frequency of the foot 12 and the surface area of the foot 12 meet the requirements of the present application, and the resonance condition can be avoided.

[0088] As can be seen from Comparative Example 1, Example 6, Example 7 and Comparative Example 9, when the radius R of the circular mounting hole 1221 on the epitaxial segment 122 in the present application is within 9 mm-12 mm, both the first-order natural frequency of the foot 12 and the surface area of the foot 12 meet the requirements of the present application, and the resonance condition can be avoided. However, when the size of the circular mounting hole 1221 on the epitaxial segment 122 is not within the above range, both the surface area and the first-order natural frequency of the foot 12 are out of the range required by the present application, and therefore the resonance condition may occur and the stability of the equipment may be reduced.

[0089] As can be seen from Comparative Example 1 to Example 8 and Comparative Example 1, when the length, width, thickness and radius of the circular mounting hole 1221 of the epitaxial segment 122 are all less than the minimum value of the size requirement of each index, the first-order natural frequency of the foot 12 is much less than 1400 Hz, and the resonance condition is likely to occur when the main working parts of the compressor vibrate.

[0090] As can be seen from Comparative Example 1 to Example 8 and Comparative Example 2, when the length L, the width W, the thickness T of the extension segment 122 and the radius R of the circular mounting hole 1221 are all greater than the maximum value of the required size of each index, the first-order natural frequency ω of the foot 12 is also less than 1400 Hz.

[0091] Specifically, the above-mentioned situation occurs mainly because the size of the extension segment 122 affects the first-order natural frequency of the foot 12. Specifically, the length, width and thickness of the extension segment 122 all affect the rigidity and mass distribution of the foot 12. Mainly, it will affect the rigidity of the foot 12 and may change the mass distribution, so that the position of the center of gravity changes. Since the first-order natural frequency of the foot 12 is proportional to the rigidity of the structure and inversely proportional to the mass. Specifically, when the width and thickness of the extension segment 122 remain unchanged, increasing its length will cause its mass to increase, thereby causing the first-order natural frequency of the foot 12 to decrease; when the length and thickness of the extension segment 122 remain unchanged, increasing its width will increase the mass of the foot 12, while also enhancing the lateral rigidity of the foot 12. Among them, the increase in mass will cause the first-order natural frequency of the foot 12 to decrease, while the increase in rigidity will increase the first-order natural frequency of the foot 12, but the actual specific effect depends on the relative change between mass and rigidity. When the length and width of the extension segment 122 remain unchanged, increasing its thickness will increase the rigidity of the foot 12, especially the bending rigidity, thereby causing the first-order natural frequency of the foot 12 to increase; but with the increase of the thickness, it will affect the stability and dynamic response characteristics of the entire device. It is worth noting that in the present application, when the radius of the circular mounting hole 1221 on the foot 12 is 13 mm, the first-order natural frequency of the foot 12 and the surface area of the foot 12 all meet the requirements of the present application, but the size of the circular mounting hole 1221 on this type of foot 12 is too large, which may bring a series of negative effects. Specifically, when the radius of the circular mounting hole 1221 is too large, there is a gap between the fastener (such as a bolt) and the circular mounting hole 1221, causing the fastening to be insecure, thereby affecting the stability of the device; in addition, the excessively large circular mounting hole 1221 will also weaken the structural rigidity of the foot 12, reduce the effective cross-sectional area of the extension segment 122, and make the foot 12 more prone to deformation or damage. Due to the problems of structural rigidity and insecurity, it may also cause the device to be easily displaced or tilted, thereby causing property loss and causing personal injury, and increasing the operation and maintenance cost of the device. Therefore, when designing, in addition to considering that the foot 12 has a natural frequency and surface area that meet the requirements, the installation and operation reliability of the device also need to be further considered.

[0092] In addition, when the size of each index of the extension segment 122 is reduced at the same time, the total surface area S and the mass m of the foot 12 will be reduced, and since the mass is reduced, the rigidity k of the foot 12 will be reduced, according to the formula It can be known that the effect of the increase of the natural frequency ω caused by the mass reduction can be offset by the decrease of the rigidity of the foot 12, and finally the first-order natural frequency of the foot 12 is actually reduced. Similarly, it can be known that if the size of each index of the extension section 122 is increased, the mass of the foot 12 will be increased, and the natural frequency will be reduced according to the formula of the natural frequency. Although increasing the size of each index can increase the mass and the rigidity of the foot 12, thereby improving the rigidity, in actual engineering applications, simply increasing the mass without optimizing the structure design often makes it difficult to significantly improve the rigidity, so the natural frequency of the foot 12 tends to be reduced, and thus the above experimental effect occurs.

[0093] In summary, the size of each index of the extension section 122 needs to be within the range specified in the present application, so as to ensure that the first-order natural frequency of the foot 12 is within the range of 1400Hz-1700Hz, so that the first-order natural frequency of the foot 12 can be improved, and resonance caused by the excitation frequency of the foot 12 and the vertical compressor can be avoided, thereby improving the operation stability of the equipment and prolonging the service life of the equipment.

[0094] It can be known from the above embodiments that the vertical compressor of the present application can also achieve the following technical effects:

[0095] (1) The utility model discloses a foot structure size ratio is designed to control the foot to have a fixed frequency (i.e.

[0096] 1400Hz-1700Hz), and the surface area is within the range of 2200mm 2 -3000mm 2 , so as to avoid the large vibration noise caused by the resonance of the foot of the vertical compressor.

[0097] (2) The utility model discloses a foot size structure size ratio is designed to control the foot to have a higher fixed frequency and smaller vibration noise radiation area, thereby reducing the production cost and avoiding resonance.

[0098] For purposes of the description hereinafter, spatial relative terms, such as "above", "below", "upper", "lower", and the like, can be used to describe the relative position of one element or feature to another as illustrated in the figures. It will be understood that the spatial relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientations depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "up" other elements or features would then be oriented "below" or "down" the other elements or features. Thus, the exemplary term "above" can encompass both an orientation of above and below. The device can be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly. Well, the spatial relative terms used herein are for ease of description only and do not limit the protective scope of the present application.

[0099] In addition, it should be noted that the use of "first", "second", and the like words to qualify parts, only for the convenience of the corresponding parts are distinguished, such as no other declaration, the above words have no special meaning, therefore can not be understood as the limitation of the protective scope of the present application.

[0100] The above is only the preferred embodiment of the present application, and is not intended to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. within the spirit and principle of the present application shall be included in the protective scope of the present application.

Claims

1. A vertical compressor, characterized by, The utility model relates to a pump, comprising: a main body component, the main body component includes pump body assembly and motor, the motor is connected with the pump body assembly drive; a shell component (10), the shell component (10) includes shell (11) and a plurality of foot (12), the main body component is arranged in the shell (11), the shell (11) is close to the bottom and is spaced apart with a plurality of foot (12) on the outer periphery, and in the height direction of the shell (11), the projection of the foot (12) is located on the projection of the shell (11) periphery, the first order inherent frequency omega of the foot (12) in the height direction of the shell (11) satisfies the relationship formula: 1400Hz <= omega <= 1700Hz.

2. The vertical compressor according to claim 1, characterized in that, The total surface area S of each of the feet (12) satisfies the relationship: 2200 mm 2 ≤ S ≤ 3000 mm 2 .

3. The vertical compressor according to claim 1, characterized in that, The foot (12) includes mounting section (121) and the extension section (122) connected with the mounting section (121), the mounting section (121) is connected with the outer peripheral surface of the shell (11), and the extension section (122) extends in the direction away from the shell (11).

4. The vertical compressor according to claim 3, characterized in that, The height H of the mounting section (121) and the length L of the extension section (122) satisfy the relationship formula: 0.3 <= H / L <= 0.

5.

5. The vertical compressor according to claim 3, characterized in that, The mounting section (121) includes the first side close to the shell (11), and a convex point (1211) is arranged on the first side, and the mounting section (121) is welded on the shell (11) through the convex point (1211).

6. The vertical compressor according to claim 3, characterized in that, The extension section (122) is long strip shape, and the width W of the extension section (122) satisfies the relationship formula: 26mm <= W <= 34mm; The thickness T of the extension section (122) satisfies the relationship formula: 2.2mm <= T <= 3.3mm; The length L of the extension section (122) satisfies the relationship formula: 34mm <= L <= 36mm.

7. The vertical compressor according to claim 6, characterized in that, The extension section (122) is provided with a circular mounting hole (1221), and the radius R of the circular mounting hole (1221) satisfies the relationship formula: 9mm <= R <= 12mm.

8. The vertical compressor according to claim 6, characterized in that, The width W of the extension section (122) and the length L of the extension section (122) satisfy the relationship formula: 0.7 <= W / L <= 1.

1.

9. The vertical compressor according to claim 6, characterized in that, The thickness T of the extension section (122) and the width W of the extension section (122) satisfy the relationship formula: 0.07 <= T / W <= 0.

13.

10. The vertical compressor according to claim 7, characterized in that, The radius R of the circular mounting hole (1221) and the length L of the extension section (122) satisfy the relationship formula: 0.2 <= R / L <= 0.4.

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