Scroll compressor and refrigeration apparatus

Abstract

A scroll compressor and a refrigeration apparatus. The scroll compressor comprises a stationary scroll (320) and a partition plate (330), wherein an exhaust port (321) and an exhaust channel (322) are provided in an upper end of the stationary scroll (320), and the exhaust port (321) is arranged at the bottom of the exhaust channel (322); the partition plate (330) is connected to the stationary scroll (320) and covers the stationary scroll (320), and the partition plate (330) is provided with a silencing hole (331); the silencing hole (331) is in communication with the exhaust channel (322); and the equivalent diameter of the silencing hole (331) is D, and the diameter of the exhaust channel (322) is D2, which satisfies D2 / D2 2≤0.6. By means of limiting the diameter ratio of the silencing hole (331) to the exhaust channel (322), the flow area of the silencing hole (331) is made relatively small, so that on one hand, the acoustic impedance of a cross section can be increased, thereby reducing the propagation of high-frequency noises (with relatively short wavelengths), and thus a good effect on reducing the high-frequency noises is achieved.

Description

Scroll compressors and refrigeration equipment

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to Chinese patent application number 202311341791.X, filed on October 16, 2023, entitled “Scroll compressor and refrigeration equipment,” the entire contents of which are incorporated by reference into this application. Technical Field

[0003] The present application relates to the technical field of compressors, and in particular to a scroll compressor and refrigeration equipment. Background Art

[0004] Scroll compressors are widely used in refrigeration equipment such as air conditioners and heat pumps due to their high efficiency, compact size, light weight, and smooth operation. The scroll is the core component of a scroll compressor. The meshing of the contoured scroll wraps on the orbiting and stationary scrolls forms a series of crescent-shaped compression chambers. As the orbiting scroll rotates eccentrically, the crescent-shaped compression chambers continuously move from the periphery toward the center, gradually decreasing in volume and increasing in pressure. Finally, the high-pressure refrigerant is discharged through the exhaust port of the stationary scroll, completing the compression process. The exhaust pressure pulsation and its direct impact on the scroll compressor casing cause high-frequency noise, impacting product performance and user experience.

[0005] Summary of the Invention

[0006] The present application aims to at least partially solve one of the technical problems existing in the prior art. To this end, the present application proposes a scroll compressor and a refrigeration device having the scroll compressor.

[0007] According to an embodiment of the first aspect of the present application, a scroll compressor includes a fixed scroll and a partition plate. An exhaust port and an exhaust passage are provided at the upper end of the fixed scroll, and the exhaust port is provided at the bottom of the exhaust passage. The partition plate is connected to the fixed scroll and is covered above the fixed scroll. The partition plate is provided with a silencer hole, and the silencer hole is connected to the exhaust passage. The equivalent diameter of the silencer hole is D, and the diameter of the exhaust passage is D2, satisfying the following conditions:

[0008] According to some embodiments of the first aspect of the present application, the diameter of the exhaust port is D1, which satisfies:

[0009] According to some embodiments of the first aspect of the present application, the axial length of the muffler hole is H, which satisfies:

[0010] According to some embodiments of the first aspect of the present application, along the axial direction of the exhaust passage, the distance between the muffler hole and the exhaust port is L, which satisfies:

[0011] According to some embodiments of the first aspect of the present application, the axial length of the exhaust channel is H1, satisfying: H1>D.

[0012] According to some embodiments of the first aspect of the present application, a check valve is provided in the exhaust channel, the check valve includes a valve seat and a piston valve column, the valve seat is connected to the static vortex disk, a guide inner hole is provided in the valve seat for guiding the movement of the piston valve column, and the silencer hole is located above the valve seat.

[0013] According to some embodiments of the first aspect of the present application, the axis of the valve seat coincides with the axis of the muffler hole, and the cross-sectional area of ​​the valve seat is larger than the cross-sectional area of ​​the muffler hole.

[0014] According to some embodiments of the first aspect of the present application, the static vortex includes a back pressure plate, which is arranged on a side of the static vortex close to the partition plate, the exhaust channel is arranged inside the back pressure plate, and the valve seat is arranged in the exhaust channel.

[0015] According to some embodiments of the first aspect of the present application, a pressure relief valve plate and a limiter are provided in the exhaust channel, the pressure relief valve plate is connected to the static vortex and covers the exhaust port, the limiter is connected to the static vortex and is located above the pressure relief valve plate, and the silencer hole is located above the limiter.

[0016] According to some embodiments of the first aspect of the present application, at least one of the exhaust port and the muffler hole deviates from the axis of the exhaust passage.

[0017] According to some embodiments of the first aspect of the present application, the cross-sectional shape of the muffler hole is circular, square, or waist-shaped.

[0018] According to an embodiment of the second aspect of the present application, a refrigeration device is provided, comprising the scroll compressor described in the embodiment of the first aspect.

[0019] Additional aspects and advantages of the present application will be given in part in the description below, and in part will become obvious from the description below, or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Additional aspects and advantages of the present application will become apparent and readily understood from the following description of the embodiments with reference to the accompanying drawings, in which:

[0021] FIG1 is a schematic structural diagram of a scroll compressor according to some embodiments of the first aspect of the present application;

[0022] FIG2 is a schematic structural diagram of the connection between the static vortex, the partition plate and the upper cover in FIG1 ;

[0023] FIG3 is a partial enlarged view of point A in FIG2 ;

[0024] FIG4 is a schematic structural diagram of the connection between the static vortex, the partition plate and the upper cover in other embodiments of the first aspect of the present application;

[0025] FIG5 is a partial enlarged view of point B in FIG4;

[0026] FIG6 is a schematic diagram of the flow direction of exhaust gas in the embodiment of FIG4 ;

[0027] FIG7 is a top view of the partition plate in FIG1 ;

[0028] FIG8 is a schematic structural diagram of a scroll compressor according to other embodiments of the first aspect of the present application;

[0029] FIG9 is a schematic structural diagram of the connection between the static vortex, the partition plate and the upper cover in FIG8 ;

[0030] FIG10 is a partial enlarged view of point C in FIG9; and

[0031] FIG11 is a graph showing noise and performance variables of the scroll compressor according to the first embodiment of the present application.

[0032] The accompanying figures are as follows:

[0033] Shell assembly 100, upper cover 110, exhaust pipe 111, cylinder 120, base 130;

[0034] Motor assembly 200, rotating shaft 210;

[0035] Compression assembly 300, orbiting scroll 310, stationary scroll 320, exhaust port 321, exhaust channel 322, partition plate 330, silencer hole 331, small hole 332, check valve 340, valve seat 341, piston valve column 342, back pressure plate 350, pressure relief valve plate 361, and limiter 362. DETAILED DESCRIPTION

[0036] The following describes in detail embodiments of the present application. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application and are not to be construed as limiting the present application.

[0037] In the description of this application, it should be understood that descriptions involving orientations, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, they cannot be understood as limitations on this application.

[0038] In the description of this application, if there is a description of first or second, it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0039] In the description of this application, unless otherwise clearly defined, terms such as setting, installing, and connecting should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in this application based on the specific content of the technical solution.

[0040] Refrigeration equipment relies on a refrigeration system to produce cold air to achieve cooling. The compressor is the power component of the refrigeration system, driving the refrigerant to circulate and achieve continuous cooling. A scroll compressor compresses the refrigerant using the coordination of an orbiting scroll and a stationary scroll. The meshed scrolls on the orbiting and stationary scrolls form a series of crescent-shaped compression chambers. As the orbiting scroll rotates eccentrically, the crescent-shaped compression chambers continuously move from the periphery to the center, and their volume gradually decreases, causing the refrigerant pressure within them to gradually increase, ultimately resulting in high-pressure refrigerant. The high-pressure refrigerant is then discharged through the exhaust port of the stationary scroll, completing the compression process.

[0041] The refrigerant discharged from the exhaust port of the static scroll has pressure pulsation. The exhaust passes through the through hole opened in the partition plate. Due to the large flow area of ​​the through hole, the exhaust directly impacts the shell of the scroll compressor, which can easily cause high-frequency noise and affect the performance of the scroll compressor and user experience.

[0042] To this end, an embodiment of the first aspect of the present application proposes a scroll compressor, which can effectively reduce the pulsation impact of the exhaust airflow and reduce noise by setting a silencer hole with a small flow area on the partition plate.

[0043] As shown in Figures 1 to 5, an embodiment of the first aspect of the present application proposes a scroll compressor, which includes a housing assembly 100, a motor assembly 200 and a compression assembly 300. The housing assembly 100 includes an upper cover 110, a cylinder 120 and a base 130. The upper cover 110 and the base 130 are fixed at the upper and lower ends of the cylinder 120 to form an accommodating cavity. The motor assembly 200 and the compression assembly 300 are arranged in the accommodating cavity. The compression assembly 300 includes a movable scroll 310 and a fixed scroll 320. The movable scroll 310 is connected to the rotating shaft 210 of the motor assembly 200. The motor assembly 200 is fixed on the inner wall of the cylinder 120 and is driven by the rotating shaft 210 of the motor assembly 200 to rotate eccentrically. The movable scroll 310 and the fixed scroll 320 cooperate to complete the compression of the refrigerant. An exhaust port 321 and an exhaust channel 322 are provided at the upper end of the static scroll 320. The exhaust port 321 is provided at the bottom of the exhaust channel 322. The compressed refrigerant enters the exhaust channel 322 through the exhaust port 321. The static scroll 320 is connected to a partition plate 330, and the partition plate 330 is covered above the static scroll 320. The upper cover 110 is covered above the partition plate 330. The upper cover 110 is provided with an exhaust pipe 111 to output high-pressure refrigerant. A muffler hole 331 is provided on the partition plate 330. The muffler hole 331 is connected to the exhaust channel 322. As shown in Figure 3, the equivalent diameter of the muffler hole 331 is defined as D, and the diameter of the exhaust channel 322 is defined as D2. The design meets the following requirements:

[0044] When the scroll compressor is running, high-pressure refrigerant is discharged from the exhaust port 321 of the fixed scroll 320, and the high-pressure refrigerant enters the exhaust passage 322. Since the exhaust passage 322 has a large diameter, it has an expansion and silencing effect. Then the refrigerant enters the silencer hole 331 provided on the partition plate 330. Due to the design limitation, the high-pressure refrigerant enters the silencer hole 331 provided on the partition plate 330. By limiting the diameter ratio of the silencer hole 331 and the exhaust channel 322, the flow area of ​​the silencer hole 331 is smaller. On the one hand, it can increase the acoustic impedance of the cross section, reduce the propagation of high-frequency noise (shorter wavelength), and have a good silencing effect on high-frequency noise; as shown in Figure 6, on the other hand, the refrigerant airflow changes the flow direction, and the high-frequency noise collides with the inner wall of the exhaust channel 322 and the partition plate 330, which can reduce the propagation of high-frequency noise. In addition, the partition plate 330 has an attenuation effect on the pressure pulsation of the refrigerant, which helps to reduce the operating noise of the scroll compressor and improve product performance and user experience.

[0045] Referring to Figure 11 , the OA curve represents noise in dB, and the COP curve represents performance improvement in pts. The resulting variations for different apertures of muffler holes 331 are shown in the figure. Therefore, by defining muffler holes 331 on partition plate 330, the embodiments of the present application can effectively improve the noise level and performance of a scroll compressor.

[0046] It is understood that the equivalent diameter of the silencer hole 331 is defined as D. When the silencer hole 331 is a circular hole, the equivalent diameter is the diameter of the circular hole; when the silencer hole 331 is a non-circular hole, the equivalent diameter is D. Wherein, A is the cross-sectional area of ​​the muffler hole 331 .

[0047] It is understood that the diameter of the exhaust port 321 is defined as D1, and the design also satisfies: That is to say, simultaneously satisfying: and The equivalent diameter of the silencer hole 331 is significantly smaller than the diameter of the exhaust channel 322, which changes the flow direction of the exhaust and increases the acoustic impedance, helping to reduce noise. The equivalent diameter of the silencer hole 331 is larger than the diameter of the exhaust port 321 in order to meet the exhaust volume requirements, prevent affecting the exhaust of the scroll compressor, and help improve the performance of the scroll compressor.

[0048] It can be understood that, referring to FIG. 3 , the axial length of the muffler hole 331 is defined as H, which satisfies the following design requirements: Since the muffler effect of the muffler hole 331 is affected by the equivalent diameter and the axial length, the smaller the equivalent diameter and the larger the axial length, the better the effect. However, this will affect the exhaust efficiency. Therefore, the equivalent diameter and the axial length must be limited to a certain range. By limiting the design: It can achieve better silencing effect and meet the exhaust requirements without affecting the exhaust volume.

[0049] It can be understood that, referring to FIG3 , along the axial direction of the exhaust passage 322 , the distance between the muffler hole 331 and the exhaust port 321 is L, which satisfies the following design requirements: By limiting the distance between the silencer hole 331 and the exhaust port 321, the refrigerant discharged from the exhaust port 321 must first move within the exhaust passage 322. Due to the large diameter of the exhaust passage 322, this has the effect of expanding and silencing the air. Furthermore, limiting the distance between the silencer hole 331 and the exhaust port 321 prevents the refrigerant from being discharged directly from the silencer hole 331, thus achieving a better silencing effect.

[0050] It can be understood that, referring to Figure 3, the axial length of the exhaust channel 322 is defined as H1, and the design satisfies: H1>D. By limiting the axial length of the exhaust channel 322 to be greater than the equivalent diameter of the silencer hole 331, the refrigerant discharged from the exhaust port 321 must first diffuse and move in the exhaust channel 322, which has the effect of expansion and silencing. Moreover, it prevents the refrigerant from quickly reaching the silencer hole 331, and has a better silencing effect.

[0051] 2 and 3 , in some embodiments, a scroll compressor is provided with a check valve 340 in the exhaust passage 322. The check valve 340 includes a fixed valve seat 341 and a movable piston valve rod 342. The valve seat 340 is fixedly connected to the fixed scroll 320. A guide inner hole for guiding the movement of the piston valve rod 342 is provided in the valve seat 341. The piston valve rod 342 can move in the guide inner hole. During exhaust, the refrigerant gas pushes up the piston valve rod 342 and then flows into the exhaust passage 322. The silencer hole 331 is located above the valve seat 341, and the refrigerant gas is finally discharged from the silencer hole 331. The function of the check valve 340 is to prevent the refrigerant from flowing back and to prevent the refrigerant from initiating the reverse rotation of the movable scroll 310 and damaging the motor assembly 200.

[0052] 2 and 3 , the static vortex 320 includes a back pressure plate 350, which is arranged on the side of the static vortex 320 close to the partition plate 330. The exhaust channel 322 and the valve seat 341 are both arranged on the back pressure plate 350. Since the valve seat 341 covers the piston valve column 342, during assembly, the piston valve column 342 is first installed into the guide inner hole of the valve seat 341, and then the valve seat 341 is installed on the static vortex 320, which simplifies the structure and assembly and improves production efficiency.

[0053] As shown in Figure 3, the axis of the valve seat 341 coincides with the axis of the silencer hole 331, and the cross-sectional area of ​​the valve seat 341 is larger than the cross-sectional area of ​​the silencer hole 331. The refrigerant discharged from the exhaust port 321 is blocked by the valve seat 341 and must bypass the valve seat 341 and then turn to enter the silencer hole 331. By changing the flow direction of the refrigerant airflow, the propagation of high-frequency noise is reduced. In addition, the valve seat 341 and the partition plate 330 have an attenuation effect on the pressure pulsation of the refrigerant, which helps to reduce the operating noise of the scroll compressor.

[0054] 4 and 5 , in other embodiments, a scroll compressor is provided with a pressure relief valve disc 361 and a stopper 362 in the exhaust passage 322. One end of the pressure relief valve disc 361 is fixedly connected to the fixed scroll 320, and the other end covers the exhaust port 321. The pressure relief valve disc 361 is used to seal the exhaust port 321. When the compression assembly 300 completes a refrigerant compression cycle, the high-pressure refrigerant can lift the pressure relief valve disc 361 for exhaust. The stopper 362 functions to limit the lift of the valve disc, prevent excessive deformation of the pressure relief valve disc 361, and protect the pressure relief valve disc 361. Therefore, the stopper 362 is connected to the fixed scroll 320 and is located above the pressure relief valve disc 361. The muffler hole 331 is located above the stopper 362. During exhaust, the refrigerant gas lifts the pressure relief valve disc 361, then flows into the exhaust passage 322, and is finally discharged from the muffler hole 331. The pressure relief valve plate 361 can also prevent the refrigerant from flowing back and driving the movable scroll 310 to reverse and damage the motor assembly 200 .

[0055] It is understood that at least one of the exhaust port 321 and the muffler hole 331 deviates from the axis of the exhaust channel 322, thereby causing the exhaust airflow to deflect in direction. Alternatively, both the exhaust port 321 and the muffler hole 331 may deviate from the axis of the exhaust channel 322, with the exhaust port 321 located on one side of the axis of the exhaust channel 322 and the muffler hole 331 located on the other side. Refrigerant discharged from the exhaust port 321 enters the exhaust channel 322, bypasses the stopper 362, and flows to the muffler hole 331 on the other side of the exhaust channel 322. This multiple change in the refrigerant's flow direction helps reduce pressure pulsation.

[0056] According to some embodiments of the first aspect of the present application, the cross-sectional shape of the muffler hole 331 is generally circular, which is easy to process and has a large flow area. Of course, the muffler hole 331 can also have a non-circular cross-sectional shape, such as a square or waist-shaped cross-sectional shape, which can meet the requirements of noise reduction and exhaust.

[0057] The embodiment of the second aspect of the present application proposes a refrigeration device, which has a refrigeration system. The refrigeration system includes a scroll compressor, a condenser, a throttling device and an evaporator of the first aspect embodiment connected in sequence by pipelines. The scroll compressor, the condenser, the throttling device and the evaporator form a circulation flow path for the refrigerant through the pipeline. When the refrigeration device is in operation, the scroll compressor compresses the refrigerant gas inhaled, and then inputs the high-temperature and high-pressure refrigerant obtained after compression into the condenser. The condenser is used to cool the refrigerant. The refrigerant output by the condenser enters the throttling device. The throttling device plays the role of throttling and reducing pressure, further reducing the temperature and pressure of the refrigerant, so that the refrigerant entering the evaporator becomes a low-pressure liquid with a lower saturation temperature. The refrigerant evaporates in the evaporator and absorbs heat from the air, thereby producing cold air, which is input into the use space to help cool down. The refrigerant output by the evaporator returns to the scroll compressor, completing a cycle. The scroll compressor continues to operate to provide power for the refrigerant, driving the refrigerant to circulate and continuously cool.

[0058] The scroll compressor includes a shell assembly 100, a motor assembly 200 and a compression assembly 300. The shell assembly 100 includes an upper cover 110, a cylinder 120 and a base 130. The upper cover 110 and the base 130 are fixed at the upper and lower ends of the cylinder 120 to form an accommodating cavity. The motor assembly 200 and the compression assembly 300 are arranged in the accommodating cavity. The compression assembly 300 includes a movable scroll 310 and a fixed scroll 320. The movable scroll 310 is connected to the rotating shaft 210 of the motor assembly 200. The motor assembly 200 is fixed on the inner wall of the cylinder 120 and is driven by the rotating shaft 210 of the motor assembly 200 to rotate eccentrically. The movable scroll 310 and the fixed scroll 320 cooperate to complete the compression of the refrigerant. An exhaust port 321 and an exhaust channel 322 are provided at the upper end of the static scroll 320. The exhaust port 321 is provided at the bottom of the exhaust channel 322. The compressed refrigerant enters the exhaust channel 322 through the exhaust port 321. The static scroll 320 is connected to a partition plate 330, and the partition plate 330 is covered above the static scroll 320. The upper cover 110 is covered above the partition plate 330. The upper cover 110 is provided with an exhaust pipe 111 to output high-pressure refrigerant. A muffler hole 331 is provided on the partition plate 330. The muffler hole 331 is connected to the exhaust channel 322. As shown in Figure 3, the equivalent diameter of the muffler hole 331 is defined as D, and the diameter of the exhaust channel 322 is defined as D2. The design meets the following requirements:

[0059] When the scroll compressor is running, high-pressure refrigerant is discharged from the exhaust port 321 of the fixed scroll 320, and the high-pressure refrigerant enters the exhaust passage 322. Since the exhaust passage 322 has a large diameter, it has an expansion and silencing effect. Then the refrigerant enters the silencer hole 331 provided on the partition plate 330. Due to the design limitation, the high-pressure refrigerant enters the silencer hole 331 provided on the partition plate 330. By limiting the diameter ratio of the silencer hole 331 and the exhaust channel 322, the flow area of ​​the silencer hole 331 is smaller. On the one hand, it can increase the acoustic impedance of the cross section, reduce the propagation of high-frequency noise (shorter wavelength), and have a good silencing effect on high-frequency noise; as shown in Figure 6, on the other hand, the refrigerant airflow changes the flow direction, and the high-frequency noise collides with the inner wall of the exhaust channel 322 and the partition plate 330, which can reduce the propagation of high-frequency noise. In addition, the partition plate 330 has an attenuation effect on the pressure pulsation of the refrigerant, which helps to reduce the operating noise of the scroll compressor and improve product performance and user experience.

[0060] As shown in Figures 8 to 10, other embodiments of the first aspect of the present application propose a scroll compressor, in which the partition plate 330 of the scroll compressor is provided with a plurality of small holes 332, which correspond to the exhaust channel 322 and are located above the exhaust channel 322.

[0061] When the scroll compressor is running, the movable scroll 310 and the fixed scroll 320 of the compression assembly 300 cooperate to compress the refrigerant to obtain high-pressure refrigerant. The high-pressure refrigerant is discharged from the exhaust port 321, passes through the exhaust channel 322, and then passes through the multiple small holes 332 set on the partition plate 330. The small holes 332 are used to suppress the airflow pulsation impact caused by the exhaust and reduce noise, which helps to reduce the operating noise of the scroll compressor and improve product performance and user experience.

[0062] It is understood that the refrigerant passing through the plurality of small holes 332 is dispersed into multiple small airflows, increasing the resistance encountered by the refrigerant during flow, thereby achieving the effect of reducing noise. Furthermore, the large space between the partition plate 330 and the upper cover 110 allows the small airflows to enter the larger space and quickly diffuse, which helps to reduce the impact on the upper cover 110 and reduce noise.

[0063] It can be understood that the multiple small holes 332 can fall within the cross-section of the exhaust channel 322 or exceed the cross-section of the exhaust channel 322. The refrigerant passing through the exhaust channel 322 enters the multiple small holes 332, which can meet the exhaust requirements and allow the refrigerant to enter between the partition plate 330 and the upper cover 110, and then be output through the exhaust pipe set in the upper cover 110.

[0064] It is understandable that the multiple small holes 332 can have the same cross-sectional area. The multiple small holes 332 can also have different cross-sectional areas, such as the cross-sectional areas of each small hole 332 are different, or the cross-sectional areas of some small holes 332 are the same, while the small holes 332 of another part have other cross-sectional areas. Among them, the cross-sectional area of ​​the small holes 332 can be a specification including two specifications, three specifications or a larger number of specifications. Using multiple small holes 332 with multiple cross-sectional areas can eliminate noise of multiple frequencies, which is more conducive to reducing the operating noise of the scroll compressor. The cross-sectional area and number of the multiple small holes 332 can be designed according to the exhaust detection data of the scroll compressor.

[0065] The equivalent diameter of the small hole 332 is defined as D. It can be understood that when the small hole 332 is a circular hole, Among them, d i is the diameter of the small hole 332, n i is the number of corresponding small holes 332, where i is the number of different apertures, i = 1, 2, 3...k; when the small hole 332 is a non-circular hole, then Among them, A i is the cross-sectional area of ​​the small hole 332, where i is the number of different hole diameters, i = 1, 2, 3...k. Referring to Figure 10, the diameter of the exhaust port 321 is defined as D1, and the diameter of the exhaust channel 322 is D2. The design meets the following requirements: as well as By limiting the value range of the equivalent diameter of the small hole 332, both the requirements of silencing and exhaust can be met, thereby preventing the performance of the scroll compressor from being reduced.

[0066] It can be understood that, referring to FIG. 10 , the axial length of the small hole 332 is defined as H, which satisfies the following design requirements: Since the muffler effect of the small hole 332 is affected by the equivalent diameter and axial length, the smaller the equivalent diameter and the larger the axial length, the better the effect. However, this will affect the exhaust efficiency. Therefore, the equivalent diameter and axial length must be limited to a certain range. By meeting the following requirements in the design: It can achieve better silencing effect and meet the exhaust requirements without affecting the exhaust volume.

[0067] It is understood that the number of holes 332 also affects the noise reduction effect, and too few holes 332 can even affect exhaust efficiency. Therefore, the number of holes 332 is N, satisfying 2 ≤ N ≤ 9, and D satisfies D ≥ 3.5 mm. By limiting the number of holes 332 and the minimum flow area of ​​holes 332, optimal noise reduction can be achieved while meeting exhaust requirements.

[0068] It is understood that the plurality of small holes 332 can be arranged in a variety of ways. For example, the plurality of small holes 332 can be spaced circumferentially around the exhaust passage 322, for example, evenly spaced in a ring-like arrangement. This dense arrangement of the plurality of small holes 332 can achieve a better noise reduction effect while meeting exhaust requirements without affecting exhaust volume. Alternatively, the plurality of small holes 332 can be spaced circumferentially around the exhaust passage 322, with each small hole 332 spaced unequally from the axis of the exhaust passage 322, and with the spacing between adjacent small holes 332 being equal or unequal. Alternatively, the plurality of small holes 332 can be arranged in two, three, or more rows around the axis of the exhaust passage 322.

[0069] Some embodiments of the present application are described in detail above in conjunction with the accompanying drawings, but the present application is not limited to the above embodiments. Various changes can be made within the scope of knowledge possessed by ordinary technicians in the relevant technical field without departing from the purpose of the present application.

Claims

1. Scroll compressor, including: A stationary vortex disk, wherein an exhaust port and an exhaust passage are arranged at the upper end of the stationary vortex disk, and the exhaust port is arranged at the bottom of the exhaust passage; as well as A partition plate is connected to the static vortex disk and is disposed above the static vortex disk. The partition plate is provided with a silencer hole, the silencer hole is connected to the exhaust passage, the equivalent diameter of the silencer hole is D, and the diameter of the exhaust passage is D2, satisfying:

2. The scroll compressor according to claim 1, wherein: The diameter of the exhaust port is D1, which satisfies:

3. The scroll compressor according to claim 1 or 2, wherein: The axial length of the muffler hole is H, which satisfies:

4. The scroll compressor according to claim 3, wherein: Along the axial direction of the exhaust passage, the distance between the muffler hole and the exhaust port is L, which satisfies:

5. The scroll compressor according to any one of claims 1 to 4, wherein: The axial length of the exhaust passage is H1, which satisfies: H1>D.

6. The scroll compressor according to any one of claims 1 to 5, wherein: A check valve is arranged in the exhaust passage, and the check valve includes a valve seat and a piston valve column. The valve seat is connected to the static vortex disk, and a guide inner hole for guiding the movement of the piston valve column is arranged in the valve seat. The silencer hole is located above the valve seat.

7. The scroll compressor according to claim 6, wherein: The axis of the valve seat coincides with the axis of the muffler hole, and the cross-sectional area of ​​the valve seat is larger than the cross-sectional area of ​​the muffler hole.

8. The scroll compressor according to claim 6 or 7, wherein: The fixed scroll includes a back pressure plate, which is arranged on a side of the fixed scroll close to the partition plate. The exhaust passage is arranged inside the back pressure plate, and the valve seat is arranged in the exhaust passage.

9. The scroll compressor according to any one of claims 1 to 8, wherein: A pressure relief valve plate and a limiter are provided in the exhaust passage. The pressure relief valve plate is connected to the static vortex and covers the exhaust port. The limiter is connected to the static vortex and is located above the pressure relief valve plate. The silencer hole is located above the limiter.

10. The scroll compressor according to claim 9, wherein: At least one of the exhaust port and the muffler hole is offset from an axis of the exhaust passage.

11. The scroll compressor according to any one of claims 1 to 10, wherein: The cross-sectional shape of the muffler hole is circular, square or waist-shaped.

12. Refrigeration equipment comprising the scroll compressor according to any one of claims 1 to 11.

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