Screw compressor and refrigerating system
By setting first and second silencing reaction chambers in the screw compressor, sound wave reflection and interference are enhanced, solving the noise and vibration problems caused by pressure pulsation, and achieving a wider range of silencing effects and compressor stability.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- CARRIER CORP
- Filing Date
- 2024-11-12
- Publication Date
- 2026-05-12
AI Technical Summary
In existing screw compressors, pressure pulsations from the economizer cause noise and vibration, especially in high-temperature and high-pressure applications, and existing silencing chamber designs are not effective in reducing high-frequency pressure pulsations.
The screw compressor is equipped with a built-in first silencing reaction chamber and a second silencing reaction chamber surrounding the outer wall of the economizer pipeline. By designing reasonable dimensions and structure, sound wave reflection and interference are enhanced, the silencing frequency range is widened, and pressure pulsation transmission loss is reduced.
It effectively reduces compressor operating noise and vibration, widens the silencing frequency range, and improves the compressor's operating stability and service life.
Smart Images
Figure CN122014607A_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of refrigeration / cooling equipment technology, specifically to a screw compressor and a refrigeration system having the screw compressor. Background Technology
[0002] Screw compressors typically use economizers to improve the capacity and COP of air conditioning units. However, pulsation propagation from the economizer port often affects the operation of the screw compressor and causes pipe vibration, generating noise. Existing technology usually incorporates a silencing chamber at the economizer port, where the economizer piping connects to the compression chamber, to reduce pressure pulsations transmitted to the economizer piping and downstream. This chamber is typically designed with a degree of frequency selectivity. The design considers the compressor speed and structural parameters, targeting the expected main operating frequency range of the compressor for the chamber design.
[0003] When such compressors are used in high-temperature and high-pressure designs such as heat pumps, the pressure pulsation will be enhanced to a certain extent. The cavity design usually needs to have better noise reduction performance, such as higher pressure pulsation transmission loss and a wider effective operating frequency range.
[0004] Therefore, how to effectively reduce pressure pulsation from the economizer pipeline without making major design changes is a problem that needs to be solved. Summary of the Invention
[0005] This application aims to provide a screw compressor that at least solves or alleviates some of the problems existing in the prior art.
[0006] This application provides a screw compressor, comprising: a compressor housing with a built-in compression cavity; an economizer connected to the compressor housing via an economizer pipeline; a first silencer reaction cavity disposed within the compressor housing and having an economizer compression cavity port connected to the compression cavity; one end of the economizer pipeline being connected to the first silencer reaction cavity and the other end being connected to the economizer; wherein, a second silencer reaction cavity is further comprising connected to the economizer pipeline and surrounding and protruding from the outer wall of the economizer pipeline.
[0007] In the optional technical solution, the diameter D2 of the second silencing reaction chamber is at least larger than the diameter D1 of the pipe at the end where the economizer pipe connects to the first silencing reaction chamber.
[0008] In the optional technical solution, the distance d between the second silencing reaction chamber and the first silencing reaction chamber is ≥10mm.
[0009] In the optional technical solution, the height H of the second silencing reaction chamber in the direction of the economic tube path satisfies the formula condition H-D1≥5mm.
[0010] In the optional technical solution, the length L of the second silencing reaction chamber in the direction of the economizer pipeline extension satisfies the formula condition L≥10mm.
[0011] In an optional technical solution, the screw compressor also includes an orifice plate disposed at the connection between the second silencer reaction chamber and the economizer pipeline.
[0012] In an optional technical solution, the screw compressor also includes: sound-absorbing material filling the second silencing reaction chamber.
[0013] This application also provides a refrigeration system having any of the screw compressors provided in this application. Attached Figure Description
[0014] Figure 1 This is a schematic diagram of a refrigeration system with a screw compressor provided in one embodiment of this application.
[0015] Figure 2 This is a partial structural diagram of a screw compressor provided in one embodiment of this application.
[0016] Figure 3 This is a partially enlarged schematic diagram of a screw compressor provided in one embodiment of this application.
[0017] Figure 4 This is a comparison chart of the transmission loss calculated for the silencing cavity design of the screw compressor provided in one embodiment of this application and the transmission loss curve obtained by traditional calculation using only the first silencing reaction cavity.
[0018] Figure 5 This is a schematic diagram of the economizer piping provided in the second embodiment of this application.
[0019] Figure 6 This is a schematic diagram of the economizer piping provided in the third embodiment of this application.
[0020] Figure 7 This is a schematic diagram of the specific structure of the orifice plate used in the economizer pipeline provided in the third embodiment of this application.
[0021] Figure 8 This is a schematic diagram of the economizer pipeline provided in the fourth embodiment of this application.
[0022] Reference numerals: 1. Screw compressor; 101. Compressor housing; 102. First silencer reaction chamber; 1021. Economizer compression chamber port; 103. Economizer pipeline; 104. Second silencer reaction chamber; 2. Refrigeration system; 201. Condenser; 202. Economizer primary side; 2021. Economizer primary side outlet; 2022. Economizer secondary side; 2023. First expansion valve; 203. Second expansion valve; 204. Evaporator; 205. Orifice plate; 1041. Sound-absorbing material; 1042. Detailed Implementation
[0023] It should be noted that the following will use examples to illustrate the working principle, characteristics and advantages of the screw compressor according to this application. However, it should be understood that all descriptions are given for illustrative purposes only and should not be construed as limiting this application in any way.
[0024] Furthermore, for any single technical feature described or implied in the embodiments mentioned herein, or any single technical feature shown or implied in the various figures, this application still allows for any combination or deletion of these technical features (or their equivalents) without any technical obstacle, thereby obtaining more other embodiments of this application that may not be directly mentioned herein.
[0025] <First Implementation Method>
[0026] Figure 1 This is a schematic diagram of the structure of a refrigeration system 2 with a screw compressor 1 provided in one embodiment of this application. Figure 1 As shown, after the refrigerant is compressed into a high-temperature, high-pressure refrigerant gas in the screw compressor 1, it is transported to the condenser 201 via the refrigerant pipeline. In the condenser 201, the high-temperature, high-pressure refrigerant gas exchanges heat with an external medium, such as water or air, causing its temperature to decrease and condense into a medium-temperature, high-pressure refrigerant gas-liquid mixture or refrigerant liquid. This liquid is then transported from the outlet of the condenser 201 to the primary side 2021 of the economizer via the refrigerant pipeline. A portion of the refrigerant at the primary side outlet 2022 of the economizer flows to the first expansion valve 203, where it is depressurized and expanded before flowing into the evaporator 205. Another portion expands into refrigerant gas through the second expansion valve 204 and enters the secondary side 2023 of the economizer. It exchanges heat with the refrigerant flowing through the primary side 2021 of the economizer, cooling the refrigerant liquid in the primary side 2021 of the economizer to the required subcooling degree. At the same time, the temperature of the refrigerant gas in the secondary side 2023 of the economizer is raised and evaporated. The refrigerant gas flowing out from the secondary side 2023 of the economizer is then transported to the screw compressor 1 through the economizer pipeline 103. It mixes with the refrigerant gas flowing into the screw compressor 1 through the evaporator 205 and is compressed before being discharged. This improves the working efficiency of the screw compressor 1 and reduces the exhaust temperature.
[0027] Figure 2 yes Figure 1 The schematic diagram of a partial structure of the screw compressor 1 shown is as follows: Figure 2 As shown, the screw compressor 1 includes a compressor housing 101, a first silencer reaction chamber 102, an economizer compression chamber port 1021, an economizer pipeline 103, and a second silencer reaction chamber 104.
[0028] like Figure 1 and Figure 2 As shown, the economizer 202 is connected to the screw compressor 1 via the economizer pipeline 103. One end of the economizer pipeline 103 is connected to the economizer 202, and the other end is connected to the first silencer reaction chamber 102 located inside the compressor housing 101. The first silencer reaction chamber 102 is also provided with an economizer compression chamber port 1021 facing the compression outlet of the screw compressor 1. Refrigerant gas flowing from the economizer 202 flows through the economizer pipeline 103 to the first silencer reaction chamber 102, and then flows through the economizer compression chamber port 1021 into the compression cavity formed by the compressor housing 101, where it is further compressed and discharged from the screw compressor 1.
[0029] Figure 3 This is a partially enlarged schematic diagram of a screw compressor 1 provided in one embodiment of this application, in conjunction with... Figure 1 and Figure 2 and Figure 3 As shown, a second noise-absorbing reaction chamber 104 is also provided near the first noise-absorbing reaction chamber 102 in the economizer pipeline 103. The second noise-absorbing reaction chamber 104 is connected to the economizer pipeline 103 and surrounds and protrudes from the outer wall of the economizer pipeline 103.
[0030] In the screw compressor 1 provided in the above embodiments of this application, the refrigerant gas is continuously compressed during the operation of the screw compressor 1. The pressure difference between the refrigerant gas in the compression cavity and the refrigerant gas flowing into the compression cavity through the first silencer reaction chamber 102 is large, resulting in a relatively complex flow pattern and pressure pulsation of the refrigerant gas in the compression cavity and the economizer pipeline 103. In the prior art, the pressure pulsation in the first target frequency band is effectively attenuated by connecting the first silencer reaction chamber 102 inside the compressor housing 101. To address pressure pulsations within the second target frequency band, the embodiment provided in this application provides a second silencing reaction cavity 104 that surrounds and protrudes from the outer wall of the economizer pipe 103 near the first silencing reaction cavity 102, and connects the second silencing reaction cavity 104 to the interior of the economizer pipe 103. This allows sound waves to be reflected and interfered within the cavity, thereby enhancing sound wave transmission loss near the first silencing reaction cavity 102 and widening the effective frequency range. This reduces the problem of significant noise generated in the economizer pipe 103 and its downstream components due to pressure pulsations being transmitted downstream, thus affecting the user experience. It also reduces the risk of the economizer pipe 103 being under prolonged strong vibration, which could lead to loosening of the connection between the economizer pipe 103 and the first silencing reaction cavity 102 or the compressor housing 101, causing compressor damage.
[0031] It should be noted that this application does not limit the specific structure of the second silencing reaction cavity 104. As long as a setting is provided around and protruding from the outer wall of the economizer pipeline 103 near the first silencing reaction cavity 102, which can realize the attenuation of pressure pulsation in the economizer pipeline 103, such as a resonant cavity, it should be included in the protection scope of this application.
[0032] Meanwhile, although it has been described in the form of setting a second silencing reaction chamber 104 near the first silencing reaction chamber 102 in the economizer pipeline 103, as Figure 2 As shown, the second silencing reaction chamber 104 can be disposed inside the compressor housing 101 and between the first silencing reaction chamber 102 and the economizer pipeline 103. Disposing of it inside the compressor housing 101 achieves a full-cavity compressor design and also utilizes the shielding of the compressor housing 101 to reduce some of the noise from the second silencing reaction chamber 104.
[0033] Figure 4 This is a comparison graph showing the transmission loss calculated for the silencing cavity of a screw compressor according to one embodiment of this application, and the transmission loss curve calculated using only the first silencing reaction cavity 102 in a conventional method. Transmission loss is an important indicator describing the sound attenuation characteristics of a silencing device; generally, the greater the transmission loss, the greater the attenuation of pressure pulsations. Figure 4The first and second order frequency bands shown are the two pressure pulsation attenuation frequency bands that need to be focused on when designing for noise reduction and vibration damping, and are also the target frequency bands for cavity optimization. The w / a curve is the noise reduction cavity transmission loss curve calculated after adopting one embodiment of this application, and the w / o curve is the noise reduction cavity transmission loss curve calculated without using the second noise reduction reaction cavity 104 provided by this application. The comparison of the two curves shows that, compared with the transmission loss without adopting the embodiment of this application, the first order frequency band has a higher transmission loss after adopting the embodiment of this application, especially in the second order frequency band. The design without the second noise reduction reaction cavity 104 in series has a lower transmission loss in this frequency band. It is quite difficult to improve the transmission loss in the second order frequency band by further optimizing the first noise reduction reaction cavity 102 without reducing the transmission loss in the first order frequency band, which often requires a more complex design of the first noise reduction reaction cavity 102. By adopting the implementation scheme of this application, the target frequency band can be quickly optimized, the transmission loss in the target frequency band is significantly improved, and the transmission loss in other frequency bands is also improved. This greatly improves the transmission loss of the entire silencing design and expands the effective silencing frequency range of the design. This allows the second silencing reaction chamber 104 to achieve good pressure pulsation attenuation in the first and second order frequency ranges of the speed of interest, and greatly broadens the effective pulsation attenuation frequency range to adapt to the pressure pulsation generated by the compressor under different frequency operating conditions.
[0034] In addition, in a preferred embodiment of this application, the diameter D2 of the second silencing reaction chamber 104 is at least larger than the diameter D1 of the pipe at the end where the economizer pipe 103 connects to the first silencing reaction chamber 102.
[0035] Through the above implementation method, the diameter D2 of the second silencing reaction chamber 104 is controlled to be greater than the diameter D1 of the pipe at the end where the economizer pipe 103 connects to the first silencing reaction chamber 102. This ensures that a local space larger than the space of the economizer pipe 103 itself is formed in a local area of the economizer pipe 103 as the second silencing reaction chamber 104. This ensures that a good acoustic environment can be formed after the pressure pulsation enters the second silencing reaction chamber 104, and together with the first silencing reaction chamber 102, a greater degree of pressure pulsation attenuation effect can be achieved.
[0036] It should be noted that although the second silencing reaction chamber 104 in this embodiment is described as a cylindrical structure surrounding the outer wall of the economizer pipe 103, this application is not limited to this. Depending on the operating conditions of different screw compressors 1, the frequency range of pressure pulsation, etc., it can be elliptical or other shapes, such as providing multiple second silencing reaction chambers 104 locally on the outer wall of the economizer pipe 103, or locally expanding the diameter of the economizer pipe 103 to form a space equivalent to the second silencing reaction chamber 104. As long as it can ensure that the pressure pulsation is effectively attenuated within the second silencing reaction chamber 104, it should be included within the protection scope of this invention.
[0037] <Second Implementation Method>
[0038] The second embodiment of this application, which uses the same names and symbols as the first embodiment of this application, is identical in content and will not be repeated here.
[0039] Figure 5 This is a schematic diagram of the economizer piping provided in the second embodiment of this application. (See attached diagram) Figure 5 As shown, the screw compressor 1 provided in the second embodiment of this application differs from the first embodiment in that the distance d between the second silencing reaction chamber 104 and the first silencing reaction chamber 102 is preferably ≥10mm.
[0040] To reduce pressure pulsations generated during compressor compression that are transmitted along the economizer port of the compression chamber to the downstream economizer pipeline 103, the distance d between the second silencer chamber 104 and the first silencer chamber 102 is controlled to be ≥10mm. Through the combined action of the first silencer chamber 102, the second silencer chamber 104, and the pipeline connecting them, effective pressure pulsation attenuation is achieved after passing through two stages of silencer chambers. This prevents significant vibrations in the economizer pipeline 103 caused by pressure pulsations, which would otherwise lead to excessive noise during compressor operation and negatively impact user experience. It also reduces the risk of compressor component damage caused by prolonged strong vibrations in the economizer pipeline 103 due to high pressure pulsations.
[0041] As a preferred embodiment of this application, the height H of the second silencing reaction chamber 104 in the radial direction of the economizer pipe 103 satisfies the following numerical condition: H-D1≥5mm, and the length L in the extension direction of the economizer pipe 103 satisfies the following numerical condition: L≥10mm.
[0042] By controlling the dimensions of the second silencing reaction chamber 104, its attenuation effect on pressure pulsations of different frequencies can be adjusted, allowing the second silencing reaction chamber 104 to be optimized for specific pressure pulsations. Considering the frequency range variation of the compressor under different operating conditions, by controlling the height H of the second silencing reaction chamber 104 in the radial direction of the economizer pipe 103 to satisfy the following equation: H-D1≥5mm, and the length L in the extension direction of the economizer pipe 103 to satisfy the following equation: L≥10mm, the second silencing reaction chamber 104 has sufficient silencing space, allowing sound waves to form multiple reflections and interferences in the second silencing reaction chamber 104, resulting in sound energy dissipation and further reducing the pressure pulsations transmitted to the economizer pipe 103.
[0043] Although the embodiments of this application are described with the example of a distance d ≥ 10 mm between the second silencing reaction chamber 104 and the first silencing reaction chamber 102, a height H in the radial direction of the economizer pipe 103 satisfying the following formula: H-D1 ≥ 5 mm, and a length L in the extension direction of the economizer pipe 103 satisfying the following formula: L ≥ 10 mm, this application is not limited to this. Any changes in the size and shape of the second silencing reaction chamber 104 to accommodate pressure pulsations in different frequency ranges should be included within the scope of protection of this application.
[0044] <Third Implementation Method>
[0045] The third embodiment of this application, which uses the same names and symbols as the embodiments described above, is the same content and will not be repeated here.
[0046] Figure 6 This is a schematic diagram of the economizer pipeline 103 provided in the third embodiment of this application. (See attached diagram) Figure 6 As shown, the screw compressor 1 provided in the third embodiment of this application differs from the above embodiments in that it also includes an orifice plate 1041.
[0047] Figure 7 This is a schematic diagram of the specific structure of the orifice plate 1041 used in the economizer pipeline provided in the third embodiment of this application, as shown below. Figure 6 and Figure 7 As shown, in the screw compressor 1 provided in the third embodiment of this application, an orifice plate 1041 is disposed at the connection between the second silencer reaction chamber 104 and the economizer pipeline 103. The specific structure of the orifice plate 1041 is determined by the thickness t, the diameter 2a, the hole spacing b, and the perforation rate s of the orifice plate 1041. The perforation rate is defined as the ratio of the perforated area to the total area of the orifice plate 1041. Preferably, the thickness t of the orifice plate 1041 is ≤ 3 mm, the diameter 2a is ≤ 4 mm, and the hole spacing b is ≥ 6a.
[0048] Through the above implementation method, by setting the orifice plate 1041 to form multiple Helmholtz-like pulsation attenuation cavities in the second silencing reaction cavity 104, the energy loss of pressure pulsation is further increased, the effective pressure pulsation attenuation frequency range is widened, the acoustic transmission loss in the economizer pipeline 103 is enhanced, and the pressure pulsation generated during the compressor compression process and transmitted to the downstream economizer pipeline through the first silencing reaction cavity 102 is reduced.
[0049] It should be noted that in the embodiments of this application, there are no restrictions on the specific size, filling range, material, etc. of the orifice plate 1041. Different orifice plates 1041 are set according to different screw compressor models, the size of the second silencer reaction chamber 104 and the pressure pulsation attenuation requirements, and all of these should be included within the protection scope of this application.
[0050] <Fourth Implementation Method>
[0051] The fourth embodiment of this application, which uses the same names and symbols as the embodiments described above, is the same content and will not be repeated here.
[0052] Figure 8 This is a schematic diagram of the economizer pipeline 103 provided in the third embodiment of this application. (See attached diagram) Figure 8 As shown, the screw compressor 1 provided in the third embodiment of this application differs from the above embodiments in that it also includes: sound-absorbing material 1042.
[0053] like Figure 8 As shown, in the screw compressor 1 provided in the fourth embodiment of this application, the second noise-absorbing reaction chamber 104 is also filled with sound-absorbing material 1042.
[0054] By filling the space between the perforated plate 1041 and the cavity wall in the second silencing reaction chamber 104 with sound-absorbing material 1042, the pressure pulsations generated during the compressor compression process are transmitted through the silencing material 1042 in the second silencing reaction chamber 104. The sound waves propagate in the gaps of the internal fiber or porous structure, causing the fluid medium particles inside the material to vibrate. Due to mechanisms such as friction and viscous resistance, this is converted into heat energy, thereby further reducing the pressure pulsations generated during the compressor compression process that are transmitted to the downstream economizer pipeline through the first silencing reaction chamber 102. The converted heat energy also raises the temperature of the refrigerant gas delivered to the compression cavity through the economizer pipeline 103, mixing it with the refrigerant gas flowing into the compressor from the evaporator 205, improving the compressor's working efficiency, and reducing the exhaust temperature.
[0055] It should be noted that, in the embodiments of this application, there are no restrictions on the specific size, filling range, material, etc. of the sound-absorbing material 1042. The use of different sound-absorbing materials 1042 according to different screw compressor models, the size of the second noise-absorbing reaction chamber 104, and the pressure pulsation attenuation requirements should all be included within the protection scope of this application.
[0056] This application also provides a refrigeration system, specifically as follows: Figure 1 The refrigeration system 2 shown is the same as the refrigeration system 2 described in the first embodiment. The screw compressor 1 can be any screw compressor 1 provided in the various embodiments of this application; specific details will not be elaborated here.
[0057] The above are merely preferred embodiments of this application and are not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.
Claims
1. A screw compressor, comprising: The compressor housing has a built-in compression chamber; An economizer is connected to the compressor housing via an economizer pipeline; The first silencer reaction chamber is disposed inside the compressor housing and has an economizer compression chamber port that communicates with the compression chamber. One end of the economizer pipeline is connected to the first silencing reaction chamber, and the other end is connected to the economizer. Its characteristic is that it also includes, The second silencing reaction chamber is connected to the economizer pipeline and is arranged around and protruding from the outer wall of the economizer pipeline.
2. The screw compressor as described in claim 1, characterized in that, The diameter D2 of the second silencing reaction chamber is at least larger than the diameter D1 of the pipe at the end where the economizer pipe connects to the first silencing reaction chamber.
3. The screw compressor as described in claim 2, characterized in that, The distance d between the second silencing reaction chamber and the first silencing reaction chamber is ≥10mm.
4. The screw compressor as described in claim 2, characterized in that, The second silencing reaction chamber, at a height H in the direction of the economizer tube path, satisfies the following numerical condition: H-D1≥5mm.
5. The screw compressor as described in claim 2, characterized in that, The length L of the second silencing reaction chamber in the direction of the economizer pipeline extension satisfies the following numerical condition: L≥10mm.
6. The screw compressor as described in claim 2, characterized in that, It also includes, An orifice plate is installed at the connection between the second silencing reaction chamber and the economizer pipeline.
7. The screw compressor as described in claim 6, characterized in that, It also includes, Sound-absorbing material is filled and placed in the second silencing reaction chamber.
8. A refrigeration system, characterized in that, Includes any one of the screw compressors as described in any one of claims 1-2.