Exhaust structure of compressor, compressor and refrigeration equipment

Abstract

The utility model discloses an exhaust structure of compressor, compressor and refrigeration equipment, the exhaust structure includes crankcase and exhaust subassembly, the crankcase is equipped with first exhaust chamber and second exhaust chamber, first inner discharge pipe connects first chamber cover and second chamber cover, through first inner discharge pipe communicates first exhaust chamber and second exhaust chamber, through second inner discharge pipe connects second chamber cover and second chamber cover. The second inner exhaust pipe is connected between the second exhaust cavity and an exhaust pipe of the compressor, so that the first exhaust cavity and the second exhaust cavity are connected in series; meanwhile, the first exhaust cavity and the second exhaust cavity are communicated through the inner channel of the crankcase to form parallel exhaust channels, so that one part of gas in the first exhaust cavity enters the second exhaust cavity through the first inner exhaust pipe, the other part of gas enters the second exhaust cavity through the inner channel, and the two parts of gas can generate convection; the exhaust pressure can be relieved, so that the airflow pressure is reduced, the exhaust pulsation is effectively improved, and the silencing effect is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to an exhaust structure of a compressor, a compressor and a refrigeration device. Background Art

[0002] During the operation of the compressor, the exhaust pulsation in the exhaust structure will generate noise. When the exhaust valve opens, the refrigerant enters the high-pressure chamber in the cylinder head, then enters the exhaust chamber on the crankcase, then enters the inner exhaust pipe, and finally enters the exhaust pipe of the compressor and is discharged outside the compressor housing. In order to improve the silencing effect, currently, a series of exhaust chambers are added to the crankcase. However, due to the large exhaust pressure and limited by the structure of the crankcase, the volume of the exhaust chamber is small, and the improvement of the exhaust pulsation effect is not obvious. Summary of the Utility Model

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides an exhaust structure of a compressor, which can relieve the exhaust pressure of the exhaust chamber, effectively improve the exhaust pulsation and enhance the silencing effect.

[0004] The utility model also provides a compressor and a refrigeration device applying the above exhaust structure.

[0005] The exhaust structure of the compressor according to the first aspect embodiment of the utility model includes a crankcase and an exhaust assembly. The crankcase is provided with a first exhaust chamber and a second exhaust chamber, and an inner channel communicating the first exhaust chamber and the second exhaust chamber is arranged in the crankcase; the exhaust assembly includes a first chamber cover, a second chamber cover, a first inner exhaust pipe and a second inner exhaust pipe; the first chamber cover covers the orifice of the first exhaust chamber, and the second chamber cover covers the orifice of the second exhaust chamber; two ends of the first inner exhaust pipe are respectively connected to the first chamber cover and the second chamber cover and communicate the first exhaust chamber and the second exhaust chamber; one end of the second inner exhaust pipe is connected to the second chamber cover and communicates with the second exhaust chamber, and the other end is used for connecting the exhaust pipe of the compressor.

[0006] The exhaust structure of the compressor according to the embodiment of the utility model has at least the following beneficial effects:

[0007] A first exhaust cavity and a second exhaust cavity are provided in the crankcase. A first inner exhaust pipe connects the first cavity cover and the second cavity cover, and the first exhaust cavity is communicated with the second exhaust cavity through the first inner exhaust pipe. A second inner exhaust pipe is connected between the second exhaust cavity and the exhaust pipe of the compressor, realizing the series connection of the first exhaust cavity and the second exhaust cavity. At the same time, the first exhaust cavity and the second exhaust cavity are communicated through the inner channel of the crankcase, forming a parallel exhaust channel, so that a part of the gas in the first exhaust cavity enters the second exhaust cavity through the first inner exhaust pipe, and another part of the gas enters the second exhaust cavity through the inner channel, enabling the two parts of the gas to generate convection, which is beneficial to relieving the exhaust pressure, thereby reducing the air flow pressure, effectively improving the exhaust pulsation and enhancing the silencing effect.

[0008] According to some embodiments of the present invention, the aperture of the port of the inner channel facing the first exhaust cavity is smaller than the aperture of the port facing the second exhaust cavity.

[0009] According to some embodiments of the present invention, the crankcase includes a first exhaust cylinder block, a second exhaust cylinder block, and a third inner exhaust pipe connected between the first exhaust cylinder block and the second exhaust cylinder block. The inner cavity of the first exhaust cylinder block is configured as the first exhaust cavity, the inner cavity of the second exhaust cylinder block is configured as the second exhaust cavity, and the inside of the third inner exhaust pipe is configured as the inner channel.

[0010] According to some embodiments of the present invention, one end of the third inner exhaust pipe is provided with a first through hole communicating with the first exhaust cavity, and the other end is provided with a second through hole communicating with the second exhaust cavity. The aperture of the second through hole is larger than the aperture of the first through hole.

[0011] According to some embodiments of the present invention, the third inner exhaust pipe includes a pipe section protruding from the inner wall surface of the first exhaust cavity, and the end surface of the pipe section is a closed structure. There are a plurality of the first through holes, and the plurality of the first through holes are distributed on the circumferential wall of the pipe section.

[0012] According to some embodiments of the present invention, the aperture of the first through hole is less than or equal to one-third of the inner diameter of the third inner exhaust pipe, and the aperture of the second through hole is equal to the inner diameter of the third inner exhaust pipe.

[0013] According to some embodiments of the present invention, the aperture range of the first through hole is from 1 mm to 6 mm.

[0014] According to some embodiments of the present invention, the crankcase is further provided with a third exhaust cavity, a third cavity cover covering the cavity opening of the third exhaust cavity, and a cylinder surface for connecting the cylinder head. The cylinder surface is provided with a first flow-through hole communicating with the first exhaust cavity and a second flow-through hole communicating with the third exhaust cavity.

[0015] According to some embodiments of the present utility model, the exhaust assembly further includes an elastic member, and the elastic member is sleeved on at least a part of the outer peripheral wall of the second inner exhaust pipe.

[0016] A compressor according to an embodiment of the second aspect of the present utility model includes a housing and the exhaust structure of the compressor according to the embodiment of the first aspect above. The exhaust structure of the compressor is disposed inside the housing, and the housing is provided with an exhaust pipe communicating with the second inner exhaust pipe.

[0017] The compressor according to the embodiment of the present utility model has at least the following beneficial effects:

[0018] The compressor applying the exhaust structure of the above embodiment can not only realize the series connection of the first exhaust cavity and the second exhaust cavity, but also form a parallel exhaust passage by connecting the first exhaust cavity and the second exhaust cavity through the inner channel of the crankcase, so that a part of the gas in the first exhaust cavity enters the second exhaust cavity through the first inner exhaust pipe, and another part of the gas enters the second exhaust cavity through the inner channel, enabling the two parts of the gas to generate convection, which is beneficial to alleviating the exhaust pressure, thereby reducing the air flow pressure, effectively improving the exhaust pulsation and enhancing the silencing effect, and helping to reduce the exhaust noise of the compressor.

[0019] A refrigeration device according to an embodiment of the third aspect of the present utility model includes the compressor according to the embodiment of the second aspect above.

[0020] Other features and advantages of the present utility model will be described in the subsequent description, and part of them will become obvious from the description, or be understood by implementing the present utility model. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 is an assembly structure schematic diagram of the exhaust structure of a compressor according to an embodiment of the present utility model;

[0022] Figure 2 is a structure schematic diagram of a crankcase according to an embodiment of the present utility model;

[0023] Figure 3 is a connection structure schematic diagram of an exhaust assembly according to an embodiment of the present utility model;

[0024] Figure 4 is a front structure schematic diagram of the exhaust structure of a compressor according to an embodiment of the present utility model;

[0025] Figure 5 is Figure 2 an enlarged structure schematic diagram at A in;

[0026] Figure 6 is Figure 4 a sectional structure schematic diagram in the B-B direction of;

[0027] Figure 7 is Figure 6 The enlarged structural schematic diagram at position C in

[0028] Reference numerals:

[0029] Crankcase 100; First exhaust cylinder block 110; First exhaust cavity 111; Connecting hole 112; Second exhaust cylinder block 120; Second exhaust cavity 121; Third exhaust cylinder block 130; Third cavity cover 131; Third exhaust cavity 132; Third inner exhaust pipe 140; Inner channel 141; First pipe section 142; Sealing structure 1421; First through hole 1422; Second pipe section 143; Second through hole 1431; Compression cylinder block 150; Cylinder bore 151; First flow-through hole 152; Second flow-through hole 153; Cylinder surface 154;

[0030] Exhaust assembly 200; First cavity cover 210; Connecting bolt 211; Second cavity cover 220; First inner exhaust pipe 230; Second inner exhaust pipe 240; Vibration damping spring 241;

[0031] Exhaust pipe 300;

[0032] Exhaust structure 1000. Detailed implementation manners

[0033] The embodiments of the present utility model will be described in detail below. The examples of the embodiments are shown in the drawings, wherein the same or similar reference numerals indicate the same or similar elements or elements with the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are only used to explain the present utility model and should not be construed as a limitation to the present utility model.

[0034] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by terms such as "front", "rear", "upper", "lower", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present utility model.

[0035] In the description of the present utility model, if the first and second are described only for the purpose of distinguishing technical features, they should not be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or implicitly indicating the sequence relationship of the indicated technical features.

[0036] In the description of the present utility model, it should be noted that terms such as "set", "installed", "connected", etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above terms in the present utility model in combination with the specific content of the technical solution.

[0037] The technical solution of the present utility model will be clearly and completely described below in conjunction with the accompanying drawings. Obviously, the embodiments described below are some, but not all, embodiments of the present utility model.

[0038] Referring to Figure 1 As shown, the exhaust structure 1000 provided by the embodiment of the present utility model includes a crankcase 100 and an exhaust assembly 200. The crankcase 100 is provided with a first exhaust chamber 111 and a second exhaust chamber 121. The first exhaust chamber 111 and the second exhaust chamber 121 are spaced apart on the crankcase 100. The exhaust assembly 200 includes a first chamber cover 210, a second chamber cover 220, a first inner exhaust pipe 230, and a second inner exhaust pipe 240. The first chamber cover 210 covers the opening of the first exhaust chamber 111, the second chamber cover 220 covers the opening of the second exhaust chamber 121. The two ends of the first inner exhaust pipe 230 are respectively connected to the first chamber cover 210 and the second chamber cover 220. The first exhaust chamber 111 and the second exhaust chamber 121 are connected through the first inner exhaust pipe 230, and the second exhaust chamber 121 is connected to the exhaust pipe 300 through the second inner exhaust pipe 240. The exhaust structure 1000 of the embodiment is specifically applicable to the compressor of a refrigeration device.

[0039] Wherein, the crankcase 100 is provided with a compression cylinder block 150. The compression cylinder block 150 is provided with a cylinder surface 154 for connecting with the cylinder head, and an exhaust mechanism is arranged between the cylinder head and the cylinder surface 154. It can be understood that when the compressor works, the piston is driven by the crank connecting rod mechanism to reciprocate in the compression cylinder block 150 to compress the refrigerant. When the exhaust valve of the exhaust mechanism is opened, the refrigerant enters the high-pressure chamber in the cylinder head, then enters the first exhaust chamber 111 from the high-pressure chamber. The refrigerant enters the second exhaust chamber 121 along the first inner exhaust pipe 230, and finally is discharged out of the compressor along the second inner exhaust pipe 240 and the exhaust pipe 300 in sequence.

[0040] Referring to Figure 2As shown, the crankcase 100 includes a first exhaust cylinder block 110 and a second exhaust cylinder block 120. A first exhaust cavity 111 is configured inside the first exhaust cylinder block 110. An orifice is formed at the top of the first exhaust cylinder block 110. The first cavity cover 210 is connected to the crankcase 100 and covers the orifice of the first exhaust cylinder block 110 to seal the top of the first exhaust cavity 111. A second exhaust cavity 121 is configured inside the second exhaust cylinder block 120. An orifice is formed at the top of the second exhaust cylinder block 120. The second cavity cover 220 is connected to the crankcase 100 and covers the orifice of the second exhaust cylinder block 120 to seal the top of the second exhaust cavity 121. One end of the first inner exhaust pipe 230 is fixedly connected to the first cavity cover 210, and the other end is fixedly connected to the second cavity cover 220, ensuring that during the exhaust process, the air flow can enter the second exhaust cavity 121 from the first exhaust cavity 111 along the first inner exhaust pipe 230, realizing the series connection of the first exhaust cavity 111 and the second exhaust cavity 121.

[0041] Referring to Figure 2 and Figure 4 As shown, in some embodiments, the first exhaust cylinder block 110 is disposed close to the compression cylinder block 150. A first flow-through hole 152 is provided inside the compression cylinder block 150. The first flow-through hole 152 is arranged in the direction from the cylinder surface 154 towards the first exhaust cavity 111, and penetrates through the cylinder surface 154 and the first exhaust cylinder block 110 through the first flow-through hole 152. Specifically, as Figure 4 and Figure 5 shown, one end port of the first flow-through hole 152 is located on the cylinder surface 154, and the other end port is located on the inner wall of the first exhaust cavity 111. When the cylinder head is installed on the cylinder surface 154, the first flow-through hole 152 communicates with the high-pressure cavity of the cylinder head, so that the refrigerant gas can enter the first exhaust cavity 111 along the first flow-through hole 152. In the embodiment, the first flow-through hole 152 is integrally cast with the crankcase 100.

[0042] Referring to Figure 3 shown, the first inner exhaust pipe 230 and the second inner exhaust pipe 240 each have an independent pipe body, and the two pipe bodies are separated from each other. The first inner exhaust pipe 230 is located between the first cavity cover 210 and the second cavity cover 220. The second inner exhaust pipe 240 is located between the second cavity cover 220 and the exhaust pipe 300. One end of the second inner exhaust pipe 240 is connected to the second cavity cover 220 and communicates with the second exhaust cavity 121, and the other end is connected to the exhaust pipe 300. During assembly, the crankcase 100 and the exhaust assembly 200 are both located inside the housing. The exhaust pipe 300 is fixedly installed in the housing and is connected to the heat exchanger of the refrigeration device through the exhaust pipe 300. The exhaust pipe 300 penetrates through the housing, so that the refrigerant gas is discharged from the compressor through the exhaust pipe 300 after being compressed, and the compressed refrigerant is provided to the heat exchanger, thereby realizing the refrigeration process of the refrigeration device.

[0043] Referring to Figure 2 andFigure 5 As shown, in some embodiments, the crankcase 100 is further provided with an inner channel 141. The inner channel 141 is formed inside the crankcase 100. One end of the inner channel 141 is communicated with the first exhaust cavity 111, and the other end is communicated with the second exhaust cavity 121. By connecting the first exhaust cavity 111 and the second exhaust cavity 121 through the inner channel 141, the air flow in the first exhaust cavity 111 can enter the second exhaust cavity 121 along the inner channel 141.

[0044] Referring to Figure 2 As shown, it can be understood that in the embodiment, the first exhaust cylinder block 110 and the second exhaust cylinder block 120 are adjacently arranged, and the outer side walls of the two cylinder blocks are connected. The inner channel 141 penetrates from the inner wall of the first exhaust cylinder block 110 to the inner wall of the second exhaust cylinder block 120, so that the first exhaust cavity 111 is communicated with the second exhaust cavity 121. Specifically, the inner channel 141 can be constructed by an integral casting method, or the inner channel 141 can be formed by drilling between the first row cylinder block and the second exhaust cylinder block 120 after the crankcase 100 is formed. The structure is easy to implement and the manufacturing cost is low.

[0045] It can be understood that the first exhaust cavity 111 and the second exhaust cavity 121 can be connected not only through the first inner exhaust pipe 230, but also through the inner channel 141. That is to say, the first inner exhaust pipe 230 is one of the exhaust channels between the first exhaust cavity 111 and the second exhaust cavity 121, and the inner channel 141 is the other exhaust channel between the first exhaust cavity 111 and the second exhaust cavity 121, thus forming a parallel exhaust channel. In this way, during the exhaust process of the compressor, a part of the gas in the first exhaust cavity 111 enters the second exhaust cavity 121 through the first inner exhaust pipe 230, and another part of the gas enters the second exhaust cavity 121 through the inner channel 141, realizing a parallel exhaust mode, enabling the two parts of gas to generate convection in the second exhaust cavity 121, which is beneficial to relieving the exhaust pressure, thereby reducing the air flow pressure, playing a role in improving the exhaust pulsation, and achieving an effective sound absorption and noise reduction effect.

[0046] In the related art, a series exhaust cavity exhaust mode is adopted. Due to the large exhaust pressure, the improvement of exhaust pulsation and sound absorption effect is not significant. The embodiment of the present utility model adopts a parallel exhaust mode, which can shunt and exhaust the high-pressure air flow, effectively reduce the exhaust pressure, thereby reducing the exhaust pulsation, and the sound absorption effect is more significant.

[0047] In some embodiments, the port apertures at both ends of the inner channel 141 are set to be unequal. Specifically, the aperture of the port of the inner channel 141 facing the first exhaust cavity 111 is smaller than the aperture of the port facing the second exhaust cavity 121. That is to say, the port of the inner channel 141 facing the first exhaust cavity 111 is narrower than the port at the other end. For example, a part of the port of the inner channel 141 facing the first exhaust cavity 111 is blocked, or the inner cavity of the inner channel 141 gradually decreases from the direction of the second exhaust cavity 121 towards the first exhaust cavity 111, so that the port of the inner channel 141 facing the first exhaust cavity 111 reaches the minimum.

[0048] It can be understood that the high-pressure gas flows from the first exhaust cavity 111 to the second exhaust cavity 121. When the high-pressure gas flows from a smaller aperture to a larger aperture, the flow rate will decrease. Since the air flow enters from the high-pressure side and the aperture increases, as long as the first exhaust cavity 111 maintains a high-pressure state and there is no intervention from an external pressure source, the air flow in the second exhaust cavity 121 will not generate a backflow along the inner channel 141, thus ensuring smooth exhaust.

[0049] Refer to Figure 2 and Figure 5 As shown, in the embodiment, the crankcase 100 is further provided with a third inner exhaust pipe 140. The third inner exhaust pipe 140 is connected between the first exhaust cylinder block 110 and the second exhaust cylinder block 120, so that the first exhaust cavity 111 and the second exhaust cavity 121 are communicated through the third inner exhaust pipe 140. The inner cavity of the third inner exhaust pipe 140 is the inner channel 141. Since the first exhaust cylinder block 110 and the second exhaust cylinder block 120 are arranged adjacent to each other, through holes are opened on the side walls of the first exhaust cylinder block 110 and the second exhaust cylinder block 120, and the first exhaust cavity 111 and the second exhaust cavity 121 can be connected by passing the third inner exhaust pipe 140 through the through holes.

[0050] It can be understood that in some embodiments, considering that a certain distance can be separated between the first exhaust cylinder block 110 and the second exhaust cylinder block 120, by respectively opening through-hole structures on the side walls of the first exhaust cylinder block 110 and the second exhaust cylinder block 120, the through-hole structures cannot directly realize the communication between the first exhaust cavity 111 and the second exhaust cavity 121. Therefore, the third inner exhaust pipe 140 is used to connect the first exhaust cavity 111 and the second exhaust cavity 121, and the length of the third inner exhaust pipe 140 is specifically selected according to the minimum distance between the first exhaust cavity 111 and the second exhaust cavity 121.

[0051] Specifically, both ends of the third inner exhaust pipe 140 penetrate through the side walls of the first exhaust cylinder block 110 and the second exhaust cylinder block 120 respectively. Both ends of the third inner exhaust pipe 140 can be fixedly connected to the first exhaust cylinder block 110 and the second exhaust cylinder block 120 by means of welding or interference fit, etc., to ensure the sealing performance between the third inner exhaust pipe 140 and the first exhaust cylinder block 110 and the second exhaust cylinder block 120.

[0052] It should be noted that the third inner exhaust pipe 140 is not limited to a straight pipe and can also be a bent pipe. In addition, the length of the third inner exhaust pipe 140 can be set to be greater than the minimum distance between the first exhaust cavity 111 and the second exhaust cavity 121, that is, the third inner exhaust pipe 140 can extend into the first exhaust cavity 111 or the second exhaust cavity 121.

[0053] Refer to Figure 6 As shown, in some embodiments, a first through hole 1422 is provided at one end of the third inner exhaust pipe 140 facing the first exhaust cavity 111, and a second through hole 1431 is provided at one end of the third inner exhaust pipe 140 facing the second exhaust cavity 121. The inner channel 141 communicates with the first exhaust cavity 111 through the first through hole 1422 and communicates with the second exhaust cavity 121 through the second through hole 1431. The high-pressure air flow in the first exhaust cavity 111 enters the inner channel 141 through the first through hole 1422 and enters the second exhaust cavity 121 through the second through hole 1431 after passing through the inner channel 141.

[0054] Since the aperture of the second through hole 1431 is larger than that of the first through hole 1422, when the high-pressure air flow flows from the first through hole 1422 to the second through hole 1431, the flow rate will decrease. When the first exhaust cavity 111 maintains a high-pressure state and there is no external pressure source intervening, the air flow in the second exhaust cavity 121 will not generate a backflow along the inner channel 141, thus ensuring smooth exhaust.

[0055] In some embodiments, the inner channel 141 can be a channel with an equal inner diameter, and the first through hole 1422 and the second through hole 1431 with different apertures are provided at both ends of the inner channel 141. In other embodiments, the inner cavity of the inner channel 141 gradually decreases from the direction of the second through hole 1431 towards the first through hole 1422, so that the aperture of the second through hole 1431 is larger than that of the first through hole 1422.

[0056] Refer to Figure 6 and Figure 7 As shown, in the embodiment, the length of the third inner exhaust pipe 140 is greater than the minimum distance between the first exhaust cavity 111 and the second exhaust cavity 121, and both ends of the third inner exhaust pipe 140 protrude from the inner walls of the first exhaust cavity 111 and the second exhaust cavity 121 respectively. Among them, the part of the third inner exhaust pipe 140 protruding from the inner wall of the first exhaust cavity 111 is the first pipe section 142, and the part protruding from the inner wall of the second exhaust cavity 121 is the second pipe section 143.

[0057] Among them, the end face of the first pipe section 142 is a closed structure 1421, and a plurality of first through holes 1422 are provided. The plurality of first through holes 1422 are distributed on the circumferential wall of the first pipe section 142, and each first through hole 1422 communicates with the first exhaust cavity 111 and the inner channel 141. The end face of the second pipe section 143 is an open structure to form a second through hole 1431, and the aperture of the second through hole 1431 is the same as the inner diameter of the inner channel 141.

[0058] It can be understood that a part of the gas in the first exhaust cavity 111 enters the second exhaust cavity 121 through the first inner exhaust pipe 230, and another part of the gas enters the inner channel 141 through the plurality of first through holes 1422 of the third inner exhaust pipe 140, and then enters the second exhaust cavity 121 from the second through hole 1431. Since the end face of the first pipe section 142 is a closed structure 1421 and the first through holes 1422 are distributed on the circumferential wall of the first pipe section 142, the axial direction of the first through holes 1422 is perpendicular to the axial direction of the third inner exhaust pipe 140. That is to say, the air flow in the first exhaust cavity 111 first enters the inner channel 141 from the first through holes 1422 along the radial direction of the third inner exhaust pipe 140, and then flows along the axial direction of the inner channel 141 to the second through hole 1431, which plays a role in reducing the air flow velocity, thereby being able to relieve the exhaust pressure.

[0059] It should be noted that the plurality of first through holes 1422 are distributed along the circumferential direction of the first pipe section 142, so that the air flow can enter the inner channel 141 from all around the first pipe section 142. Since the aperture of the first through holes 1422 is smaller than the aperture of the second through hole 1431 and the inner diameter of the inner channel 141, when the aperture of the first through holes 1422 and the length of the third inner exhaust pipe 140 meet certain conditions, the third inner exhaust pipe 140 can produce a microporous sound absorption effect. Specifically, during the exhaust process, sound waves will enter the third inner exhaust pipe 140 from the plurality of first through holes 1422, and the sound waves will be reflected and refracted multiple times inside the third inner exhaust pipe 140, so that the sound waves are continuously attenuated and dispersed, thereby dissipating the sound wave energy and achieving the effect of sound absorption and noise reduction.

[0060] Refer to Figure 7As shown, the aperture diameter of the first through hole 1422 is less than or equal to one-third of the inner diameter of the third inner exhaust pipe 140, that is, D1 ≤ 1 / 3 * D2, where D1 represents the aperture diameter of the first through hole 1422 and D2 represents the inner diameter of the third inner exhaust pipe 140. It can be understood that the sound absorption effect of the micro-hole sound absorption effect is related to the aperture diameter and the hole pitch. When D1 > 1 / 3 * D2, it means that the aperture diameter of the first through hole 1422 is too large and the sound absorption effect is not obvious. The aperture diameter of the first through hole 1422 can be selected according to the specific size of the inner diameter of the third inner exhaust pipe 140. For example, when the inner diameter of the third inner exhaust pipe 140 is 12 mm, the aperture diameter of the first through hole 1422 is less than or equal to 4 mm, and specifically, the aperture diameter of the first through hole 1422 can be set to 2 mm, 3 mm or 4 mm, etc.

[0061] In some embodiments, the aperture diameter range of the first through hole 1422 is 1 mm to 6 mm. This aperture diameter range meets the requirements of sound absorption, and the sound absorption effect is obvious. Especially for the noise in the frequency range of 500 Hz to 600 Hz, it plays an effective role in reducing such noise. It can be understood that under the conditions that the aperture diameter of the first through hole 1422 satisfies 1 mm to 6 mm and D1 ≤ 1 / 3 * D2, the inner diameter of the third inner exhaust pipe 140 can be determined according to the aperture diameter of the first through hole 1422. For example, when the aperture diameter of the first through hole 1422 is 3 mm, the inner diameter of the third inner exhaust pipe 140 needs to be greater than or equal to 9 mm. In addition, since the sound absorption effect of the micro-hole sound absorption effect is also related to the pipe length of the third inner exhaust pipe 140, in the embodiments, the specific pipe length can be designed according to the sound absorption frequency band, which is not specifically limited here.

[0062] In the exhaust structure 1000 of the embodiment of the present invention, a parallel exhaust mode is adopted between the first exhaust cavity 111 and the second exhaust cavity 121. The gas flowing into the second exhaust cavity 121 along the two exhaust channels can generate convection, which is beneficial to relieving the exhaust pressure and plays a role in improving the exhaust pulsation; and under the conditions that the first through hole 1422 satisfies 1 mm to 6 mm and D1 ≤ 1 / 3 * D2, the gas can generate a micro-hole sound absorption effect when passing through the third inner exhaust pipe 140, realizing the sound absorption effect and effectively reducing the exhaust noise generated during the operation of the compressor.

[0063] In addition, the end face of the first pipe section 142 in the third inner exhaust pipe 140 is a closed structure 1421, which can effectively prevent the gas in the second exhaust cavity 121 from flowing back through the third inner exhaust pipe 140.

[0064] Refer to Figure 1 and Figure 2As shown, the crankcase 100 further includes a third exhaust cylinder block 130. The inner cavity of the third exhaust cylinder block 130 is configured to form a third exhaust cavity 132. A third cavity cover 131 is provided at the top of the third exhaust cylinder block 130. The third cavity cover 131 is connected to the crankcase 100 and covers the cavity opening of the third exhaust cylinder block 130 to seal the top of the third exhaust cavity 132. Additionally, as Figure 4 shown, a second flow-through hole 153 is further provided on the cylinder surface 154. The second flow-through hole 153 and the second flow-through hole 153 are respectively located on both sides of the cylinder surface 154. The second flow-through hole 153 is arranged in the direction from the cylinder surface 154 towards the third exhaust cavity 132, and penetrates through the cylinder surface 154 and the third exhaust cylinder block 130 through the second flow-through hole 153. It can be understood that the first flow-through hole 152 and the second flow-through hole 153 are respectively communicated with the high-pressure cavity of the cylinder head, forming a parallel structure.

[0065] During the exhaust process of the compressor, part of the gas enters the first exhaust cavity 111 through the first flow-through hole 152, then enters the second exhaust cavity 121 along two parallel exhaust channels, and finally is discharged from the compressor along the second inner exhaust pipe 240 and the exhaust pipe 300 in sequence; another part of the gas enters the third exhaust cavity 132 through the second flow-through hole 153. The third exhaust cavity 132 is a closed cavity, which acts as a resonance cavity, helping to improve the exhaust pulsation and thus enhancing the sound absorption ability.

[0066] Referring to Figure 1 and Figure 2 shown, connecting holes 112 are respectively provided at the bottoms of the first exhaust cylinder block 110, the second exhaust cylinder block 120, and the third exhaust cylinder block 130. The first cavity cover 210, the second cavity cover 220, and the third cavity cover 131 are respectively connected to the corresponding connecting holes 112 by using connecting pieces to realize the installation of each cavity cover.

[0067] Referring to Figure 6 shown, taking the first exhaust cylinder block 110 and the first cavity cover 210 as an example for illustration, the connecting piece is a connecting bolt 211. An opening is provided at the middle position of the first cavity cover 210. The connecting bolt 211 passes through the opening of the first cavity cover 210 and is connected to the connecting hole 112 at the bottom of the first exhaust cylinder block 110, which is convenient for installation and disassembly and ensures the stability of the connection between the first cavity cover 210 and the first exhaust cylinder block 110. On this basis, a sealing gasket is provided between the first cavity cover 210 and the first exhaust cylinder block 110 to ensure the airtightness of the connection part between the first cavity cover 210 and the first exhaust cylinder block 110, effectively preventing gas leakage and ensuring the normal operation of the refrigeration system.

[0068] Referring to Figure 3As shown, the exhaust assembly 200 further includes an elastic member, which is sleeved on at least a part of the outer peripheral wall of the second inner exhaust pipe 240. Specifically, in the embodiment, the elastic member can be a damping spring 241 or other elastic kits.

[0069] Taking the damping spring 241 as an example, after adding the damping spring 241 to the second inner exhaust pipe 240, part of the vibration and impact force can be absorbed during the exhaust process, thereby reducing the outward transmission of vibration and the generation of noise, and further improving the noise reduction effect. It should be noted that the damping spring 241 is arranged along the length direction of the second inner exhaust pipe 240, and can cover part or all of the outer peripheral wall of the second inner exhaust pipe 240 to improve the damping effect. The specific length of the damping spring 241 can be set according to the length of the second inner exhaust pipe 240. In some embodiments, multiple damping springs 241 can also be sleeved on the second inner exhaust pipe 240.

[0070] An embodiment of the present invention also provides a compressor, which is specifically a reciprocating compressor. The compressor includes a housing and the exhaust structure 1000 of the compressor in the above embodiment. The exhaust structure 1000 of the compressor is arranged in the housing, and the housing is provided with an exhaust pipe 300, and the exhaust pipe 300 is communicated with the second inner exhaust pipe 240.

[0071] During the exhaust process of the compressor, part of the gas in the first exhaust chamber 111 enters the second exhaust chamber 121 through the first inner exhaust pipe 230, and another part of the gas enters the second exhaust chamber 121 through the inner channel 141, realizing a parallel exhaust mode, enabling the two parts of gas to generate convection in the second exhaust chamber 121, which is beneficial to relieve the exhaust pressure, thereby reducing the gas flow pressure, playing a role in improving the exhaust pulsation, achieving an effective sound absorption and noise reduction effect, and helping to reduce the exhaust noise of the compressor.

[0072] An embodiment of the present invention also provides a refrigeration device, which can be devices such as refrigerators and freezers. The refrigeration device includes the compressor in the above embodiment. Therefore, the refrigeration device of the present invention has all the beneficial effects of the above compressor.

[0073] The above has described the embodiments of the present invention in detail with reference to the drawings, but the present invention is not limited to the above embodiments. Within the knowledge scope of those of ordinary skill in the art to which it belongs, various changes can also be made without departing from the gist of the present invention.

Claims

1. An exhaust structure of a compressor, characterized in that, Comprising: A crankcase, provided with a first exhaust cavity and a second exhaust cavity, and an inner channel communicating the first exhaust cavity and the second exhaust cavity is provided inside the crankcase; An exhaust assembly, including a first cavity cover, a second cavity cover, a first inner exhaust pipe and a second inner exhaust pipe; the first cavity cover covers the opening of the first exhaust cavity, and the second cavity cover covers the opening of the second exhaust cavity; two ends of the first inner exhaust pipe are respectively connected to the first cavity cover and the second cavity cover, and communicate the first exhaust cavity and the second exhaust cavity; One end of the second inner exhaust pipe is connected to the second cavity cover and communicates with the second exhaust cavity, and the other end is used for connecting the exhaust pipe of the compressor.

2. The exhaust structure of the compressor according to claim 1, characterized in that, The aperture of the port of the inner channel facing the first exhaust cavity is smaller than the aperture of the port facing the second exhaust cavity.

3. The exhaust structure of the compressor according to claim 1, characterized in that, The crankcase includes a first exhaust cylinder block, a second exhaust cylinder block and a third inner exhaust pipe connected between the first exhaust cylinder block and the second exhaust cylinder block. The inner cavity of the first exhaust cylinder block is configured as the first exhaust cavity, the inner cavity of the second exhaust cylinder block is configured as the second exhaust cavity, and the inside of the third inner exhaust pipe is configured as the inner channel.

4. The exhaust structure of the compressor according to claim 3, characterized in that, One end of the third inner exhaust pipe is provided with a first through hole communicating with the first exhaust cavity, and the other end is provided with a second through hole communicating with the second exhaust cavity. The aperture of the second through hole is larger than that of the first through hole.

5. The exhaust structure of the compressor according to claim 4, characterized in that, The third inner exhaust pipe includes a pipe section protruding from the inner wall surface of the first exhaust cavity. The end face of the pipe section is a closed structure, and there are multiple first through holes. The multiple first through holes are distributed on the circumferential wall of the pipe section.

6. The exhaust structure of the compressor according to claim 4, characterized in that, The aperture of the first through hole is less than or equal to one-third of the inner diameter of the third inner exhaust pipe, and the aperture of the second through hole is equal to the inner diameter of the third inner exhaust pipe.

7. The exhaust structure of the compressor according to any one of claims 4 to 6, characterized in that, The aperture range of the first through hole is from 1 mm to 6 mm.

8. The exhaust structure of the compressor according to claim 1, characterized in that, The crankcase is further provided with a third exhaust cavity, a third cavity cover covering the opening of the third exhaust cavity and a cylinder surface for connecting the cylinder head. The cylinder surface is provided with a first flow-through hole communicating with the first exhaust cavity and a second flow-through hole communicating with the third exhaust cavity.

9. The exhaust structure of the compressor according to claim 1, characterized in that, The exhaust assembly further includes an elastic member, and the elastic member is sleeved on at least part of the outer peripheral wall of the second inner exhaust pipe.

10. A compressor, characterized in that, Comprising a housing and the exhaust structure of the compressor according to any one of claims 1 to 9. The exhaust structure of the compressor is provided inside the housing, and the housing is provided with an exhaust pipe communicating with the second inner exhaust pipe.

11. A refrigeration device, characterized in that, Comprising the compressor according to claim 10.

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