Silencing assembly and compressor

Abstract

The present application relates to the compressor silencing field, provide a kind of silencing assembly and compressor, wherein the silencing assembly includes: upper cylinder cover, upper cylinder cover includes base body and exhaust hole through base body along the axial direction, base body has exhaust ramp around exhaust hole, exhaust ramp has cavity and passage at, cavity is located inside exhaust ramp below, passage is through exhaust ramp surface to cavity;Silencer, silencer includes silencer outlet, silencer is covered on upper cylinder cover, the space surrounded by silencer and upper cylinder cover constitutes silencer cavity, passage is communicated cavity and silencer cavity;Wherein, cavity, passage and silencer cavity jointly constitute the silencing cavity of silencing assembly, and the refrigerant discharged from exhaust hole passes through silencing cavity, and from silencer outlet flows out silencing assembly.The silencing assembly and compressor of the present application effectively reduce the noise of compressor exhaust stage, while avoiding to reduce cylinder volumetric efficiency, to improve the performance of compressor.

Description

Technical Field

[0001] This invention relates to the field of compressor noise reduction, and more specifically, to a noise reduction assembly and a compressor. Background Technology

[0002] The working cycle of a rotary compressor can be divided into three processes: intake, compression, and exhaust. Airflow noise is a significant noise source for rotary compressors. During the exhaust process, high-temperature, high-pressure refrigerant flows from the cylinder through the exhaust port into the muffler. To reduce exhaust noise, mufflers and exhaust silencers are typically used. However, the use of exhaust silencers reduces cylinder volumetric efficiency, affecting performance.

[0003] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of the present invention, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0004] In view of this, the present invention provides a noise reduction component and a compressor.

[0005] One aspect of the present invention provides a noise reduction assembly for a compressor, comprising:

[0006] An upper cylinder head includes a base and an exhaust port that extends through the base along its axial direction. The base has an exhaust ramp surrounding the exhaust port. The exhaust ramp has a cavity and a channel. The cavity is located below the interior of the exhaust ramp. The channel extends through the surface of the exhaust ramp to the cavity.

[0007] A muffler, the muffler including a plurality of muffler outlets, the muffler covering the upper cylinder head, the space enclosed by the muffler and the upper cylinder head forming a muffler cavity, and the channel connecting the cavity and the muffler cavity;

[0008] The cavity, the channel, and the muffler cavity together constitute the muffler cavity of the muffler assembly. The refrigerant discharged from the exhaust port passes through the muffler cavity and flows out of the muffler outlet of the muffler assembly.

[0009] In some embodiments, the exhaust ramp partially surrounds the exhaust port, the cavity is located inside the substrate, and extends along the direction in which the exhaust ramp surrounds the exhaust port.

[0010] In some embodiments, the channel is located at the bottom end of the exhaust ramp, and the cavity communicates with the outside world only through the channel.

[0011] In some embodiments, the geometry of the cavity and the channel satisfies that the value of K is in the range of (0, 1020):

[0012]

[0013] L ′ =L+βd,

[0014] Where L represents the length of the channel, β represents the length coefficient, d represents the equivalent diameter of the channel, L' represents the equivalent length of the channel, V represents the volume of the cavity, and K represents a dimensionless parameter used to measure the silencing bandwidth of the silencing component.

[0015] In some embodiments, the muffler assembly further includes: at least one flow guiding device located within the muffler cavity and arranged between the exhaust ramp and the muffler; the flow guiding device has a sheet-like structure; the refrigerant discharged from the exhaust port passes through the exhaust ramp and the flow guiding device, and flows out of the muffler from the muffler outlet.

[0016] In some embodiments, the upper cylinder head further includes a valve seat, which is recessed in the base along the axial direction of the base, and the exhaust port is located in the valve seat, the exhaust port being inclined outward from the base along the exhaust ramp from the bottom end to the top end.

[0017] In some embodiments, the upper cylinder head further includes a valve plate located on the valve seat, the valve plate being able to open and close cover the exhaust port, and when the cylinder pressure of the compressor is greater than the pressure provided by the valve plate, the refrigerant is discharged through the exhaust port.

[0018] In some embodiments, the substrate includes a plurality of waist-shaped holes that penetrate the substrate and are distributed circumferentially along the substrate.

[0019] In some embodiments, the base includes a plurality of threaded holes that penetrate the base and are distributed circumferentially along the base, and the upper cylinder head is detachably connected to the cylinder of the compressor through the plurality of threaded holes.

[0020] Another aspect of the present invention provides a compressor comprising: a cylinder, a lower cylinder head, and a muffler assembly as described in any of the preceding claims.

[0021] The beneficial effects of this invention compared to the prior art include at least the following:

[0022] The present invention provides a silencing component and a compressor. By providing a silencing component, a cavity and channel are opened under the exhaust slope, so that the cavity together with the muffler cavity constitutes the silencing cavity of the silencing component. When the high-speed refrigerant flows out from the exhaust port, the sound response in the cavity is reduced, effectively reducing the noise of the compressor during the exhaust stage. At the same time, the silencing component is located outside the cylinder, avoiding the reduction of cylinder volumetric efficiency caused by occupying the cylinder space, thereby improving the performance of the compressor.

[0023] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and are not intended to limit the invention. Attached Figure Description

[0024] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention. It is obvious that the drawings described below are merely some embodiments of the invention, and those skilled in the art can obtain other drawings based on these drawings without any inventive effort.

[0025] Figure 1 This diagram shows a structural schematic of the upper cylinder head in one embodiment of the present invention;

[0026] Figure 2 The noise reduction assembly of the present invention is shown in Figure 1 Schematic diagram of the BB section;

[0027] Figure 3 Show Figure 2 Enlarged view of the circled area;

[0028] Figure 4 This diagram shows another structural schematic of the upper cylinder head in one embodiment of the present invention;

[0029] Figure 5 The noise reduction assembly of the present invention is shown in Figure 4 A partial schematic diagram of section AA;

[0030] Figure 6 Show Figure 5 Enlarged view of the circled area;

[0031] Figure 7 A schematic diagram of the exhaust ramp of the present invention is shown;

[0032] Figure 8 The diagram shows the acoustic response test results of the compressor in the exhaust chamber of the present invention and the prior art.

[0033] Figure label:

[0034] 10. Upper cylinder head

[0035] 11 Matrix

[0036] 111 Exhaust ramp

[0037] 112 Cavity

[0038] Channel 113

[0039] 114 Waist-shaped holes

[0040] 115 Threaded hole

[0041] 12 Exhaust ports

[0042] 13 Valve seat

[0043] 20 silencers Detailed Implementation

[0044] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that the invention will be thorough and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and therefore repeated descriptions of them will be omitted.

[0045] The use of terms such as "first," "second," and similar terms in the specific description does not indicate any order, quantity, or importance, but is merely used to distinguish different components. Furthermore, in the description of this invention, terms such as "upper," "lower," etc., indicate orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings. These are merely for ease of description and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation; therefore, they should not be construed as limitations on the invention.

[0046] It should be noted that, unless otherwise specified, the embodiments of the present invention and the features in different embodiments can be combined with each other.

[0047] Through meticulous and in-depth research, the inventors in this case have provided a solution to the problems existing in the prior art. For example... Figure 1 and 7 As shown, Figure 1 This diagram shows a structural schematic of the upper cylinder head in one embodiment of the present invention; Figure 2 The noise reduction assembly of the present invention is shown in Figure 1 Schematic diagram of the BB section;

[0048] Figure 3 Show Figure 2 Enlarged view of the circled area; Figure 4 This diagram shows another structural schematic of the upper cylinder head in one embodiment of the present invention; Figure 5The noise reduction assembly of the present invention is shown in Figure 4 A partial schematic diagram of section AA; Figure 6 Show Figure 5 Enlarged view of the circled area; Figure 7 A schematic diagram of the exhaust ramp of the present invention is shown. The present invention discloses a muffler assembly and a compressor. The muffler assembly is used in a compressor and specifically includes: an upper cylinder head 10, the upper cylinder head 10 including a base 11 and an exhaust port 12 extending axially through the base 11; an exhaust ramp 111 surrounding the exhaust port 12; a cavity 112 and a channel 113 on the exhaust ramp 111; the cavity 112 being located below the interior of the exhaust ramp 111; and the channel 113 extending from the surface of the exhaust ramp 111 to the cavity 112; a muffler... The muffler 20 includes a muffler 20 outlet. The muffler 20 covers the upper cylinder head 10. The space enclosed by the muffler 20 and the upper cylinder head 10 constitutes the muffler 20 cavity. The channel 113 connects the cavity 112 and the muffler 20 cavity. The cavity 112, the channel 113 and the muffler 20 cavity together constitute the muffler cavity of the muffler assembly. The refrigerant discharged from the exhaust port 12 passes through the muffler cavity and flows out of the muffler assembly from the muffler 20 outlet. The silencing component and compressor of the present invention provide a silencing component by opening a cavity 112 and a channel 113 under the exhaust ramp 111, so that it together with the muffler cavity constitutes the silencing cavity of the silencing component. When the high-speed refrigerant flows out from the exhaust port, the sound response in the cavity is reduced, effectively reducing the noise of the compressor during the exhaust stage. At the same time, the silencing component is located outside the cylinder, avoiding the reduction of cylinder volumetric efficiency caused by occupying the cylinder space, thereby improving the performance of the compressor.

[0049] The present invention will be further described below with reference to the accompanying drawings.

[0050] refer to Figure 1 , 5 According to one aspect of the invention, a muffler assembly for a compressor is disclosed, specifically comprising at least an upper cylinder head 10 and a muffler 20.

[0051] In some embodiments, the upper cylinder head 10 includes a base 11 and an exhaust port 12 extending through the base 11 along its axial direction. The base 11 has an exhaust ramp 111 surrounding the exhaust port 12. Generally, the base of the upper cylinder head used in compressors is annular to match the overall shape of the compressor. The exhaust port 12 is located off-center from the base 11, and the axial direction of the base 11 is also the axial direction of the compressor. The exhaust ramp 111 partially surrounds the exhaust port 12, and the semi-enclosed position of the exhaust ramp 111 completely covers the direction of refrigerant flow, so that after the refrigerant flows out of the exhaust port 12, it is discharged upward through the exhaust ramp 111. Furthermore, the exhaust ramp 111 can be a smooth curved surface, or it can be composed of multiple planes joined together, or other forms.

[0052] In some embodiments, the upper cylinder head 10 further includes a valve seat 13, which is recessed into the base 11 along its axial direction. That is, the valve seat 13 is formed by creating a groove on the upper surface of the base 12, with a portion of the bottom of the groove serving as the valve seat 13. The exhaust ramp 111 is the inclined inner wall of the groove in the valve seat 13. Other inner walls of the groove can be parallel to the axial direction of the base 11 or have a certain angle, without limitation. The exhaust port 12 is located in the valve seat 13. In a preferred embodiment, the exhaust port 12 is inclined outward from the base 11 along the exhaust ramp 111 from bottom to top, meaning that the upward axial direction of the exhaust port 12 has a certain angle with the axial direction of the base 11. In a more preferred embodiment, the inclination direction of the exhaust port 12 matches the inclination direction of the exhaust ramp 111 to reduce collisions between the refrigerant and components such as the base 11 and the muffler 20, thereby reducing power consumption and noise.

[0053] In some embodiments, the upper cylinder head 10 further includes a valve plate (not shown) located on the valve seat 13, which can be opened and closed to cover the exhaust port 12. Generally, the valve plate is elastic, with one end detachably disposed on the end of the valve seat 13 away from the exhaust port, and the other end of the valve plate closing the exhaust port 12. The valve seat is subjected to the air pressure in the working chamber and the air pressure of the external environment. When the pressure difference is greater than a certain critical value, the end of the valve plate located on the exhaust port 12 tilts up and opens the exhaust port 12, allowing gas to be discharged.

[0054] In some embodiments, the substrate 11 includes a plurality of oblong holes 114 that penetrate the substrate 11 and are distributed circumferentially along the substrate 11. The plurality of oblong holes 114 may be the same in shape and size or may be different. The working chamber of the compressor includes an intake chamber and a compression chamber. During the operation of the compressor, most of the cylinder is immersed in the oil sump. The area of ​​the oblong holes 114 can fill the oil sump, which is beneficial for the high temperature in the compression chamber to dissipate heat to the oil sump.

[0055] In some embodiments, the base 11 includes a plurality of threaded holes 115 penetrating the base 11 and distributed circumferentially along the base 11. The upper cylinder head 10 is detachably connected to the compressor cylinder through the plurality of threaded holes 115. The threaded holes 115 are closer to the axis of the base 11 than the oblong holes 114. Specifically, the cylinder is also provided with a plurality of threaded holes, the threaded holes on the cylinder corresponding one-to-one with the threaded holes 115 on the base 11, and then the two are detachably connected by bolts.

[0056] In some embodiments, reference Figure 2The muffler 20 includes several muffler outlets (not shown in the figure), which can be located on the side or top of the muffler 20. The muffler 20 covers the upper cylinder head 10, and the space enclosed by the muffler 20 and the upper cylinder head 10 constitutes the muffler cavity. After the gas is discharged from the exhaust port 12, it passes through the muffler cavity and exits from the muffler outlets. The muffler 20 is used to eliminate the noise generated by the compressor during operation, especially the noise generated when gas is discharged from the exhaust port 12.

[0057] refer to Figure 7 In some embodiments, the exhaust ramp 111 has a cavity 112. Figure 7 The cavity formed by the long dashed lines) and a channel 113 ( Figure 7 The cavity 112 is located below the interior of the exhaust ramp 111, and the channel 113 extends from the surface of the exhaust ramp 111 to the cavity 112.

[0058] Specifically, refer to Figure 1 , 4 In section 7, the exhaust ramp 111 partially surrounds the exhaust port 12. The cavity 112 is located inside the base 11 and extends along the direction of the exhaust ramp 111 surrounding the exhaust port 12. The shape of the cross-section of the cavity 112 perpendicular to its extension direction can be polygonal, circular, etc., and the cross-section is preferably rectangular. The shape of the cavity 112 can be changed according to the shape of the exhaust ramp 111 to adapt to the exhaust ramp 111. For example, when the exhaust ramp 111 is a smooth curved surface, the turning points of the cavity 112 are smooth transitions. When the exhaust ramp 111 is composed of multiple planes joined together, the turning points of the cavity 112 are not smooth transitions.

[0059] Specifically, channel 113 is located at the bottom end of exhaust ramp 111, and cavity 112 communicates with the outside only through channel 113. In other embodiments, channel 113 may also be located at other positions on exhaust ramp 111, as long as channel 113 extends from the surface of exhaust ramp 111 to cavity 112. The shape of the cross-section of channel 113 perpendicular to its length direction can be polygonal, circular, etc., and the cross-section is preferably rectangular.

[0060] Cavity 112, channel 113, and the cavity of muffler 20 together constitute the silencing cavity of the silencing assembly. The refrigerant discharged from exhaust port 12 passes through the silencing cavity and flows out of the silencing assembly from the exhaust port of muffler 20. Cavity 112 and channel 113 are opened below exhaust ramp 111, so that cavity 112 and channel 113 together with the muffler cavity constitute the silencing cavity of the silencing assembly. When high-speed refrigerant flows out from exhaust port 12, the sound response in the cavity is reduced, effectively reducing the noise during the compressor exhaust stage.

[0061] When the silencing cavity is in operation, it can cancel noise at a specific frequency, which is the silencing frequency of the silencing component. In some preferred embodiments, the geometry of the cavity 112 and the channel 113 satisfies the following formula:

[0062]

[0063] L ′ =L+βd,

[0064] Where L represents the length of channel 113, β represents the length coefficient (value can be between 0.3 and 1.0), d represents the equivalent diameter of channel 113, L' represents the equivalent length of channel 113, V represents the volume of cavity 112, and K represents a dimensionless parameter used to measure the noise reduction bandwidth of the noise reduction component. Preferably, the value of K should be in the range of (0 to 1020). To achieve better noise reduction effect, the noise reduction bandwidth of the noise reduction cavity should be maximized. The larger K is, the larger the noise reduction bandwidth of the noise reduction cavity, and the better the noise reduction effect of the noise reduction cavity. Therefore, the geometric design of cavity 112 and channel 113 should aim to maximize the value of K.

[0065] In some embodiments, the muffler assembly further includes at least one flow guiding device located within the muffler cavity and arranged between the exhaust ramp and the muffler; the flow guiding device is a protruding structure; the refrigerant discharged from the exhaust port passes through the exhaust ramp, changes its flow direction under the action of the flow guiding device, and flows out of the muffler from the muffler outlet. Specifically, the flow guiding device is fixedly connected to the exhaust ramp; or fixedly connected to the muffler, and its width gradually increases along the vertical upward direction of the exhaust ramp.

[0066] In some embodiments, the flow guiding device is a sheet-like protruding structure. In the sheet-like cross-section of the flow guiding device, the height of the flow guiding device is h, and the width at the bottom end is b, both satisfying h / b≧0.15. A first angle is formed between the sheet-like cross-section of the flow guiding device and the direction parallel to the upward flow of the exhaust slope and the direction of refrigerant flow. The absolute value of the first angle ranges from 0 to 60°. Preferably, the absolute value of the first angle ranges from 20° to 40°. A second angle is formed between the sheet-like cross-section of the flow guiding device and the slope of the exhaust slope where the flow guiding device is located. The value of the second angle ranges from 45° to 135°. Preferably, the value of the second angle ranges from 60° to 120°. The tail of the flow guiding device has a third angle, the value of which ranges from 30° to 150°. The number of flow guiding devices in the silencing assembly is 1 to 10. When the number of flow guiding devices is greater than one, the flow guiding devices are symmetrically distributed in a fan shape. Preferably, the noise reduction assembly has 2 to 4 flow guiding devices; when the number of flow guiding devices is 2 to 3, the flow guiding devices are arranged in one row; when the number of flow guiding devices is 4, the flow guiding devices are arranged in two rows.

[0067] In some embodiments, the flow guide device is a V-shaped protruding structure, and the refrigerant flows through the flow guide device from the bottom end to the top end of the V. Optionally, the V-shaped protruding flow guide device can be considered as being composed of two sheet-like flow guide devices spliced ​​together. In this case, the parameters of the V-shaped protruding flow guide device can be referred to the sheet-like flow guide device, which will not be repeated here. Preferably, when the V-shaped protruding flow guide device is fixedly connected to the exhaust ramp 111, its cross-sectional area gradually decreases in the direction vertically upward along the exhaust ramp 111. When the V-shaped protruding flow guide device is fixedly connected to the muffler 20, its cross-sectional area gradually decreases in the direction vertically downward along the muffler 20.

[0068] Another aspect of the present invention provides a compressor, comprising: a cylinder, a lower cylinder head, and the aforementioned muffler assembly. The upper and lower cylinder heads of the muffler assembly are respectively disposed at both ends of the cylinder along the axial direction of the cylinder, forming a compression chamber for compressing refrigerant. The axial direction of the base 11 of the muffler assembly is parallel to the axial direction of the cylinder. An exhaust port 12 communicates with the compression chamber. Since the compressor includes the muffler assembly as described above, the compressor also has the beneficial effects brought by the muffler assembly. Specifically, see [link to relevant documentation]. Figure 8 , Figure 8 The diagram shows the acoustic response test results of the compressor's exhaust chamber in both the present invention and the prior art. The M-curve represents the acoustic response test curve of the compressor's exhaust chamber in the prior art, and the N-curve represents the acoustic response test curve of the compressor's exhaust chamber in the present invention. This test is performed by introducing airflow into the compressor and testing the acoustic response at multiple points inside, then summing the results. Compared to the prior art, the compressor of the present invention effectively reduces noise during the compressor's exhaust phase by creating cavities and channels under the exhaust ramp, thereby improving compressor performance.

[0069] In summary, the silencing component and compressor of the present invention provide a silencing component by creating a cavity and channel under the exhaust ramp, which together with the muffler cavity constitutes the silencing cavity of the silencing component. When the high-speed refrigerant flows out from the exhaust port, the sound response in the cavity is reduced, effectively reducing the noise during the compressor's exhaust phase. At the same time, the silencing component is located outside the cylinder, avoiding the reduction in cylinder volumetric efficiency caused by occupying cylinder space, thereby improving the performance of the compressor.

[0070] The above description, in conjunction with specific preferred embodiments, provides a further detailed explanation of the present invention. It should not be construed that the specific implementation of the present invention is limited to these descriptions. For those skilled in the art, various simple deductions or substitutions can be made without departing from the concept of the present invention, and all such modifications and substitutions should be considered within the scope of protection of the present invention.

Claims

1. A sound attenuation assembly for a compressor, comprising: include: An upper cylinder head includes a base and an exhaust port that extends through the base along its axial direction. The base has an exhaust ramp surrounding the exhaust port. The exhaust ramp has a cavity and a channel. The cavity is located below the interior of the exhaust ramp. The channel extends through the surface of the exhaust ramp to the cavity. A muffler, the muffler including a plurality of muffler outlets, the muffler covering the upper cylinder head, the space enclosed by the muffler and the upper cylinder head forming a muffler cavity, and the channel connecting the cavity and the muffler cavity; The cavity, the channel, and the muffler cavity together constitute the muffler cavity of the muffler assembly. The refrigerant discharged from the exhaust port passes through the muffler cavity and flows out of the muffler outlet of the muffler assembly.

2. The sound attenuation assembly of claim 1, wherein, The exhaust ramp partially surrounds the exhaust port, and the cavity is located inside the substrate and extends along the direction of the exhaust ramp surrounding the exhaust port.

3. The sound attenuation assembly of claim 1, wherein, The channel is located at the bottom end of the exhaust ramp, and the cavity is connected to the outside world only through the channel.

4. The sound attenuation assembly of claim 1, wherein, The geometry of the cavity and the channel should satisfy the condition that K takes the value of (0, 1020): L ′ = L + βd, Where L represents the length of the channel, β represents the length coefficient, d represents the equivalent diameter of the channel, L' represents the equivalent length of the channel, V represents the volume of the cavity, and K represents a dimensionless parameter used to measure the silencing bandwidth of the silencing component.

5. The sound attenuation assembly of claim 1, wherein, Also includes: At least one flow guiding device is located within the muffler cavity and arranged between the exhaust ramp and the muffler; the flow guiding device has a plate-like structure. The refrigerant discharged from the exhaust port passes through the exhaust ramp and the flow guide device, and flows out of the muffler from the muffler outlet.

6. The sound attenuation assembly of claim 1, wherein, The upper cylinder head also includes a valve seat, which is recessed in the base along the axial direction of the base. The exhaust port is located in the valve seat and is inclined outward from the base along the exhaust ramp from the bottom to the top.

7. The sound attenuation assembly of claim 6, wherein, The upper cylinder head also includes a valve plate located on the valve seat. The valve plate can be opened and closed to cover the exhaust port. When the cylinder pressure of the compressor is greater than the pressure provided by the valve plate, the refrigerant is discharged through the exhaust port.

8. The sound attenuation assembly of claim 1, wherein, The substrate includes a plurality of waist-shaped holes that penetrate the substrate and are distributed circumferentially along the substrate.

9. The sound attenuation assembly of claim 1, wherein, The base includes a plurality of threaded holes that penetrate the base and are distributed circumferentially along the base, and the upper cylinder head is detachably connected to the cylinder of the compressor through the plurality of threaded holes.

10. A compressor characterized by, include: Cylinder, lower cylinder head, and muffler assembly according to any one of claims 1 to 9.

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