Air suction and exhaust assembly, compressor and refrigeration device

Abstract

The application provides an air suction and exhaust assembly, a compressor and a refrigeration device. The air suction and exhaust assembly comprises a cylinder head provided with a cavity; a valve plate connected with the cylinder head, the valve plate being provided with an air suction port, a sink, an air exhaust port and a flow hole, the air suction port being communicated with the sink, and the flow hole being communicated with the cavity; an air exhaust valve arranged on one side of the valve plate close to the cylinder head, the air exhaust valve being used for opening or closing the air exhaust port, the air exhaust port being communicated with the cavity based on the air exhaust valve opening the air exhaust port; and a silencer arranged on the cylinder head, the silencer comprising a fitting part, at least a part of the fitting part being embedded in the sink, the fitting part being directly abutted with a sink wall in the thickness direction of the valve plate, the fitting part being provided with a silencing outlet, and the silencing outlet being communicated with the air suction port. In the process that the low-temperature refrigerant enters the compression cavity through the air suction port, the contact between the valve plate and the refrigerant can be effectively reduced, the heat transfer from the valve plate to the refrigerant is reduced, the problem of suction overheating is significantly improved, the suction efficiency is improved, and the energy efficiency of the compressor is improved.

Description

Technical Field

[0001] This invention relates to the field of compressor equipment technology, and more specifically, to a suction and discharge assembly, a compressor, and a refrigeration device. Background Technology

[0002] Currently, reciprocating compressors in related technologies generally use an intake muffler to draw low-temperature, low-pressure refrigerant into the cylinder and compress it into high-temperature, high-pressure refrigerant before discharging it. Therefore, during the operation of a reciprocating compressor, components such as the crankcase, valve plate, and cylinder head can be considered high-temperature heat sources compared to the refrigerant drawn in by the intake muffler. However, during the intake process of a reciprocating compressor, the low-temperature refrigerant enters the cylinder through the intake port on the valve plate. During this process, the valve plate transfers heat to the refrigerant, leading to overheating during intake and reducing the efficiency of the reciprocating compressor. Summary of the Invention

[0003] The embodiments of the present invention are intended to at least solve one of the technical problems existing in the prior art.

[0004] Therefore, a first aspect of the embodiments of the present invention provides an intake and exhaust assembly.

[0005] A second aspect of the present invention provides a compressor.

[0006] A third aspect of the present invention provides a refrigeration device.

[0007] In view of the above, according to a first aspect of the present invention, an intake and exhaust assembly is provided, comprising: a cylinder head having a cavity; a valve plate connected to the cylinder head, the valve plate having an intake port, a groove, an exhaust port and a flow hole, the intake port communicating with the groove and the flow hole communicating with the cavity; an exhaust valve disposed on the side of the valve plate near the cylinder head for opening or closing the exhaust port, the exhaust port communicating with the cavity based on the exhaust valve opening; and a muffler disposed on the cylinder head, the muffler including a mating part, at least a portion of the mating part being embedded in the groove, the mating part directly abutting against the groove wall along the thickness direction of the valve plate, the mating part having a muffler outlet communicating with the intake port.

[0008] The intake and exhaust assembly provided in this embodiment of the invention includes a cylinder head, a valve plate, an exhaust valve, and a muffler. Specifically, the cylinder head has a cavity, and a flow passage communicates with the cavity. Optionally, the compressor further includes a compression chamber, a high-pressure chamber, and an inner exhaust pipe. Either the intake port or the exhaust port communicates with the compression chamber, the high-pressure chamber communicates with the flow passage, and the inner exhaust pipe communicates with the high-pressure chamber. Specifically, during compressor operation, refrigerant flowing from the muffler outlet enters the compression chamber through the intake port. The refrigerant is compressed in the compression chamber. When the compressor discharges, the exhaust valve opens the exhaust port, which communicates with the cavity. The compressed, high-temperature, high-pressure refrigerant flows into the cavity through the exhaust port and then flows to the high-pressure chamber through the flow passage, finally being discharged through the inner exhaust pipe.

[0009] Because the exhaust port is located on the valve plate, the valve plate is at a relatively high temperature during compressor operation. In other words, compared to the refrigerant drawn in by the muffler, the valve plate is a high-temperature heat source. Therefore, when the refrigerant flows from the suction port into the compression chamber, the higher-temperature valve plate transfers heat to the refrigerant, causing overheating of the suction gas and reducing compressor efficiency.

[0010] The valve plate has an intake port and a recess, with the recess communicating with the intake port. At least part of the mating part is embedded in the recess, thereby effectively reducing the contact between the valve plate and the refrigerant during the process of the low-temperature refrigerant entering the compression chamber through the intake port, reducing heat transfer from the valve plate to the refrigerant. Furthermore, it is understood that the muffler is generally made of plastic, optionally PBT (polybutylene terephthalate), meaning the muffler material has a low thermal conductivity. Therefore, it can hinder heat transfer from the valve plate to the refrigerant, significantly improving the problem of intake overheating, which is beneficial for improving intake efficiency and thus improving the overall energy efficiency of the compressor.

[0011] Furthermore, by embedding at least part of the mating portion into the settling tank, and with the mating portion directly abutting against the tank wall along the thickness direction of the valve plate, the sealing performance at the mating position between the valve plate and the mating portion can be improved, preventing gas leakage. Moreover, the structure is simple and easy to manufacture.

[0012] Optionally, the intake and exhaust assembly also includes an intake valve plate, which is disposed on the side of the valve plate away from the mating part, for opening or closing the intake port.

[0013] In addition, the intake and exhaust assembly provided by the above-described technical solution of the present invention also has the following additional technical features:

[0014] In some technical solutions, optionally, the thickness H of the valve plate and the depth L of the settling groove satisfy the condition H / 2≤L<H.

[0015] In this technical solution, the relationship between the depth of the settling tank and the thickness of the valve plate is defined. Specifically, the depth of the settling tank is greater than or equal to 1 / 2 of the thickness of the valve plate, and the depth of the settling tank is less than the thickness of the valve plate.

[0016] It is understandable that if the depth of the groove is shallow, i.e., L is less than 1 / 2 of the valve plate thickness, the length of the mating part embedded in the groove is short. During the process of the low-temperature refrigerant entering the compression chamber through the suction port, there is still a lot of contact between the valve plate and the refrigerant, which causes the valve plate to transfer too much heat to the refrigerant, resulting in excessive suction overheating.

[0017] If the depth of the groove is relatively deep, i.e., L equals the thickness of the valve plate, meaning the groove penetrates the valve plate, after the mating part is inserted into the groove, the end of the mating part will protrude from the side of the valve plate facing away from the muffler. Since the intake valve plate is located on the side of the valve plate facing away from the muffler to open or close the intake port, the protrusion of the end of the mating part on this side of the valve plate reduces the flatness of that surface, causing the intake valve plate to be unable to effectively close the intake port when intake stops. Furthermore, having the groove penetrate the valve plate reduces the sealing performance between the valve plate and the mating part, easily leading to gas leakage.

[0018] By making the depth of the settling groove greater than or equal to 1 / 2 of the valve plate thickness, and the depth of the settling groove less than the valve plate thickness, it is possible to reduce the contact between the valve plate and the refrigerant, reduce the heat transfer from the valve plate to the refrigerant, ensure that the suction valve plate can effectively seal the suction port when suction stops, and improve the sealing performance of the mating position between the valve plate and the mating part to prevent gas leakage.

[0019] In some technical solutions, optionally, a gap exists between the outer wall of the mating part and the wall of the settling tank along the height direction of the valve plate.

[0020] In this technical solution, a gap is defined between the outer wall of the mating part and the wall of the settling tank along the height direction of the valve plate. This gap further hinders the heat transfer from the valve plate to the refrigerant during the process of the low-temperature refrigerant entering the compression chamber through the suction port, effectively improving the problem of suction overheating, increasing suction efficiency, and thus helping to improve the overall energy efficiency of the compressor.

[0021] In some technical solutions, the clearance surrounds the mating part.

[0022] In this technical solution, a gap surrounding mating part is defined, which can further hinder the heat transfer from the valve plate to the refrigerant during the process of the low-temperature refrigerant entering the compression chamber through the suction port, effectively improve the problem of suction overheating, improve suction efficiency, and thus help improve the overall energy efficiency of the compressor.

[0023] In some technical solutions, the gap h can optionally satisfy h≤0.2mm.

[0024] This technical solution defines the range of values ​​for the gap between the outer wall of the mating part and the wall of the recess along the height direction of the valve plate. It is understandable that if the gap is too large, i.e., h is greater than 0.2 mm, leakage is likely to occur during compressor operation. By making the gap between the outer wall of the mating part and the wall of the recess along the height direction of the valve plate less than or equal to 0.2 mm, heat transfer from the valve plate to the refrigerant can be hindered while preventing gas leakage. This also facilitates the assembly of the valve plate and the muffler, reduces the manufacturing difficulty of the valve plate and the mating part, and consequently lowers the production cost of the compressor.

[0025] In some technical solutions, optionally, the muffler includes a body, a mating part is provided on the outside of the body and extends protruding away from the body, the body is provided with a muffler channel, and the muffler channel is connected to the muffler outlet; wherein, at least one of the mating part and the body is a heat insulation component.

[0026] In this technical solution, the muffler includes a body. Specifically, a mating part is disposed on the body, and the mating part extends protruding away from the body. Optionally, the mating part and the body are an integral structure.

[0027] The main body is equipped with a silencing channel, which is connected to the silencing outlet. Specifically, when the compressor draws in gas, the low-temperature refrigerant flows into the compression chamber sequentially through the silencing channel, the silencing outlet, and the suction port. During this process, since at least part of the mating parts are embedded in the groove, the contact between the valve plate and the refrigerant can be effectively reduced, the heat transfer from the valve plate to the refrigerant can be reduced, the problem of suction overheating can be significantly improved, the suction efficiency can be improved, and thus the overall energy efficiency of the compressor can be improved.

[0028] Specifically, the mating part is a heat-insulating component, or the body is a heat-insulating component, or both the mating part and the body are heat-insulating components. The specific configuration can be determined according to actual needs. Optionally, the heat-insulating component may include a plastic part. That is, the mating part and / or the body are made of heat-insulating material. It is understood that the heat-insulating material has a low thermal conductivity, which can hinder heat transfer from the valve plate to the refrigerant, further improving the problem of suction overheating, increasing suction efficiency, and thus improving the overall energy efficiency of the compressor.

[0029] In some technical solutions, the valve plate may optionally be provided with at least two limiting holes, which are located on the side of the intake port away from the exhaust port and arranged along the width direction of the valve plate; the muffler may also include at least two limiting posts, which are respectively inserted into at least two limiting holes.

[0030] In this technical solution, the valve plate is further provided with at least two limiting holes. Specifically, at least two limiting holes are located on the side of the air intake port away from the exhaust port, and at least two limiting holes are arranged along the width direction of the valve plate.

[0031] The muffler also includes at least two limiting posts, which are inserted into at least two limiting holes respectively, thereby limiting the valve plate and improving the assembly stability and reliability between the valve plate and the muffler.

[0032] In some technical solutions, optionally, along the thickness direction of the valve plate, the length N of the mating part and the depth L of the sink groove satisfy 0.4mm≤NL≤0.6mm; and / or the diameter D of the flow hole satisfies 3mm≤D≤6mm.

[0033] In this technical solution, the range of the difference between the length of the mating part and the depth of the groove along the thickness direction of the valve plate is defined. Specifically, the difference between the length of the mating part and the depth of the groove is between 0.4mm and 0.6mm. That is to say, when the mating part is inserted into the groove, a space of 0.4mm to 0.6mm is reserved between the side of the valve plate facing the muffler and the end face of the muffler in the thickness direction. This space is used to install gaskets to improve the sealing of the intake and exhaust components, prevent gas leakage, and ensure the energy efficiency of the compressor.

[0034] Optionally, the intake and exhaust assembly also includes a gasket, which is fitted onto the mating part and located between the valve plate and the end face of the muffler.

[0035] Furthermore, the diameter of the flow orifice is limited to a range of 3mm to 6mm. If the diameter of the flow orifice is too small (less than 3mm), the throttling effect during gas exhaust is significant, resulting in a large pressure loss. If the diameter of the flow orifice is too large (greater than 6mm), the flow pulsation during exhaust is significant. By limiting the diameter of the flow orifice to between 3mm and 6mm, the throttling effect during exhaust is avoided while reducing exhaust pulsation.

[0036] Optionally, the diameter D of the flow orifice is 4 mm or 5 mm.

[0037] In some technical solutions, optionally, in the height direction of the valve plate, the cross-sectional shape of the intake port is the same as the cross-sectional shape of the muffler outlet, and the flow area of ​​the intake port is equal to the flow area of ​​the muffler outlet; and / or the valve plate is also provided with multiple positioning holes, the valve plate is connected to the cylinder head through multiple positioning holes, the multiple positioning holes are distributed at intervals on the outer periphery of the intake port, each positioning hole is constructed to be close to the outer edge of the valve plate, and the distance between the positioning hole and the center of the valve plate is equal.

[0038] In this technical solution, the intake port and the silencer outlet are respectively defined in the height direction of the valve plate. The cross-sectional shape of the intake port and the cross-sectional shape of the silencer outlet are the same, and the flow area is equal. That is to say, the cross-sectional shape of the intake port is consistent with the cross-sectional shape of the silencer outlet. In this way, the flow resistance of the gas can be reduced and the flow loss can be reduced during the intake process of the compressor, thus ensuring the efficiency of the compressor.

[0039] The valve plate also has multiple positioning holes. Specifically, the valve plate is connected to the cylinder head through multiple positioning holes. These positioning holes are spaced apart on the outer periphery of the intake port, and each positioning hole is located close to the outer edge of the valve plate, meaning they are circumferentially distributed. Each positioning hole is equidistant from the center of the valve plate, ensuring even distribution and thus guaranteeing uniform force on the valve plate's fixed position. This helps extend the valve plate's service life and improves the compressor's reliability.

[0040] According to a second aspect of the present invention, a compressor is provided, comprising an intake and exhaust assembly as provided in any of the above-described technical solutions, and thus possessing all the beneficial technical effects of the intake and exhaust assembly, which will not be elaborated further here.

[0041] According to a third aspect of the present invention, a refrigeration device is provided, comprising an intake and exhaust assembly or compressor as provided in any of the above-described technical solutions, and thus possessing all the beneficial technical effects of the intake and exhaust assembly or compressor, which will not be elaborated further here.

[0042] Additional aspects and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description or may be learned by practice of the invention. Attached Figure Description

[0043] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0044] Figure 1 An exploded view of an intake and exhaust assembly according to an embodiment of the present invention is shown;

[0045] Figure 2 A schematic diagram of the intake and exhaust assembly according to an embodiment of the present invention is shown.

[0046] in, Figure 1 and Figure 2 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0047] 100 Intake and exhaust assembly, 110 Valve plate, 111 Intake port, 112 Sump, 113 Exhaust port, 114 Flow hole, 115 Positioning hole, 116 Limiting hole, 120 Silencer, 121 Fitting part, 122 Silencer outlet, 123 Body, 124 Silencer channel, 125 Limiting post, 130 Clearance. Detailed Implementation

[0048] To better understand the above-mentioned objectives, features, and advantages of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0049] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and therefore the scope of protection of the invention is not limited to the specific embodiments disclosed below.

[0050] The following reference Figure 1 and Figure 2 This describes the intake and exhaust assembly 100, compressor, and refrigeration equipment provided according to some embodiments of the present invention.

[0051] In one embodiment according to this application, such as Figure 1 and Figure 2 As shown, an intake and exhaust assembly 100 is proposed, comprising: a cylinder head having a cavity; a valve plate 110 connected to the cylinder head, the valve plate 110 having an intake port 111, a groove 112, an exhaust port 113, and a flow hole 114, the intake port 111 communicating with the groove 112, and the flow hole 114 communicating with the cavity; an exhaust valve located on the side of the valve plate 110 near the cylinder head, used to open or close the exhaust port 113, the exhaust port 113 being open based on the exhaust valve, and the exhaust port 113 communicating with the cavity; and a muffler 120 located on the cylinder head, the muffler 120 including a mating part 121, at least a portion of the mating part 121 being embedded in the groove 112, the mating part 121 directly abutting against the groove wall of the groove 112 along the thickness direction of the valve plate 110, the mating part 121 having a muffler outlet 122 communicating with the intake port 111.

[0052] The intake and exhaust assembly 100 provided in this embodiment of the invention includes a cylinder head, a valve plate 110, an exhaust valve, and a muffler 120. Specifically, the cylinder head is provided with a cavity, and a flow hole 114 communicates with the cavity. Optionally, the compressor further includes a compression chamber, a high-pressure chamber, and an inner exhaust pipe. Either the intake port 111 or the exhaust port 113 communicates with the compression chamber, the high-pressure chamber communicates with the flow hole 114, and the inner exhaust pipe communicates with the high-pressure chamber. Specifically, during compressor operation, the refrigerant flowing out from the muffler outlet 122 enters the compression chamber through the intake port 111. The refrigerant is compressed in the compression chamber. When the compressor exhausts, the exhaust valve opens the exhaust port 113, which communicates with the cavity. The compressed high-temperature and high-pressure refrigerant flows into the cavity through the exhaust port 113 and flows to the high-pressure chamber through the flow hole 114, and finally is discharged through the inner exhaust pipe.

[0053] Because the exhaust port 113 is located on the valve plate 110, the valve plate 110 has a relatively high temperature during compressor operation. In other words, compared to the refrigerant drawn in by the muffler 120, the valve plate 110 is a high-temperature heat source. Therefore, when the refrigerant flows into the compression chamber through the suction port 111, the higher-temperature valve plate 110 transfers heat to the refrigerant, causing overheating of the suction and reducing compressor efficiency.

[0054] The valve plate 110 is provided with an intake port 111 and a recess 112, and the recess 112 is connected to the intake port 111. At least a portion of the mating part 121 is embedded in the recess 112, thereby effectively reducing the contact between the valve plate 110 and the refrigerant during the process of the low-temperature refrigerant entering the compression chamber through the intake port 111, reducing the heat transfer from the valve plate 110 to the refrigerant. At the same time, it is understood that the material of the muffler 120 is generally a plastic part, optionally PBT (polybutylene terephthalate), that is, the material of the muffler 120 has a low thermal conductivity, thus hindering the heat transfer from the valve plate 110 to the refrigerant, significantly improving the problem of intake overheating, which is conducive to improving intake efficiency, and thus improving the overall energy efficiency of the compressor.

[0055] Furthermore, by embedding at least a portion of the mating part 121 into the recess 112, and with the mating part 121 directly abutting against the wall of the recess 112 along the thickness direction of the valve plate 110, the sealing performance of the mating position between the valve plate 110 and the mating part 121 can be improved, preventing gas leakage. Moreover, the structure is simple and easy to manufacture.

[0056] Optionally, the intake and exhaust assembly 100 also includes an intake valve plate, which is disposed on the side of the valve plate 110 opposite to the mating part 121, for opening or closing the intake port 111.

[0057]

[0058] In the comparative examples in the table above, compressors 1 and 2 do not have a groove on the valve plate, while compressors 3 and 4 have a groove 112 on the valve plate 110. Optionally, two compressors with identical structures can be selected, and valve plates without grooves can be installed respectively. The two sets of data from the comparative examples above can be obtained, and their average values ​​can be calculated. Then, the valve plates in both compressors can be disassembled, and valve plates 110 with grooves 112 can be installed. The tests can then be repeated to obtain the two sets of data from the above embodiments, and their average values ​​can be calculated. The COP value represents the compressor efficiency. As shown in the table above, by providing a groove 112 on the valve plate 110, the compressor's cooling capacity, input force, and COP value are all improved.

[0059] like Figure 2 As shown, in some embodiments, optionally, the thickness H of the valve plate 110 and the depth L of the groove 112 satisfy the condition H / 2≤L<H.

[0060] In this embodiment, the relationship between the depth of the sink 112 and the thickness of the valve plate 110 is defined. Specifically, the depth of the sink 112 is greater than or equal to half the thickness of the valve plate 110, and the depth of the sink 112 is less than the thickness of the valve plate 110.

[0061] It is understandable that if the depth of the groove 112 is shallow, that is, L is less than 1 / 2 of the thickness of the valve plate 110, the length of the mating part 121 embedded in the groove 112 is short. During the process of the low-temperature refrigerant entering the compression chamber through the suction port 111, there is still a lot of contact between the valve plate 110 and the refrigerant, which causes the valve plate 110 to transfer too much heat to the refrigerant, resulting in excessive suction overheating.

[0062] If the depth of the groove 112 is relatively deep, i.e., L equals the thickness of the valve plate 110, meaning the groove 112 penetrates the valve plate 110, after the mating part 121 is inserted into the groove 112, the end of the mating part 121 will be exposed on the side of the valve plate 110 facing away from the muffler 120. Since the intake valve plate is located on the side of the valve plate 110 facing away from the muffler 120 to open or close the intake port 111, the exposed end of the mating part 121 on the side of the valve plate 110 facing away from the muffler 120 will reduce the flatness of that side surface, causing the intake valve plate to be unable to effectively close the intake port 111 when intake stops. Furthermore, having the groove 112 penetrate the valve plate 110 will reduce the sealing performance of the mating position between the valve plate 110 and the mating part 121, easily leading to gas leakage.

[0063] By making the depth of the recess 112 greater than or equal to half the thickness of the valve plate 110, and the depth of the recess 112 less than the thickness of the valve plate 110, it is possible to reduce the contact between the valve plate 110 and the refrigerant, reduce the heat transfer from the valve plate 110 to the refrigerant, ensure that the suction valve plate can effectively seal the suction port 111 when suction stops, and improve the sealing of the mating position between the valve plate 110 and the mating part 121 to prevent gas leakage.

[0064] like Figure 2 As shown, in some embodiments, optionally, a gap 130 is provided between the outer wall of the mating part 121 and the groove wall of the settling tank 112 along the height direction of the valve plate 110.

[0065] In this embodiment, a gap 130 is defined between the outer wall of the mating part 121 and the groove wall of the sink 112 along the height direction of the valve plate 110. This gap further hinders the heat transfer from the valve plate 110 to the refrigerant during the process of the low-temperature refrigerant entering the compression chamber through the suction port 111, effectively improving the problem of suction overheating, improving suction efficiency, and thus helping to improve the overall energy efficiency of the compressor.

[0066] In some embodiments, the gap 130 may optionally surround the mating portion 121.

[0067] In this embodiment, a gap 130 is defined around the mating part 121, thereby further hindering the heat transfer from the valve plate 110 to the refrigerant during the process of the low-temperature refrigerant entering the compression chamber through the suction port 111, effectively improving the problem of suction overheating, improving suction efficiency, and thus helping to improve the overall energy efficiency of the compressor.

[0068] like Figure 2 As shown, in some embodiments, optionally, the gap 130h satisfies h≤0.2mm.

[0069] In this embodiment, the range of the gap 130 between the outer wall of the mating part 121 and the wall of the recess 112 along the height direction of the valve plate 110 is defined. It is understood that if the gap 130 is too large, i.e., h is greater than 0.2 mm, leakage is likely to occur during compressor operation. By making the gap 130 between the outer wall of the mating part 121 and the wall of the recess 112 along the height direction of the valve plate 110 less than or equal to 0.2 mm, heat transfer from the valve plate 110 to the refrigerant can be hindered while preventing gas leakage. This also facilitates the assembly between the valve plate 110 and the muffler 120, and reduces the manufacturing difficulty of the valve plate 110 and the mating part 121, thereby reducing the production cost of the compressor.

[0070] like Figure 1 and Figure 2 As shown, in some embodiments, optionally, the muffler 120 includes a body 123, a mating part 121 is disposed on the outside of the body 123 and extends protruding away from the body 123, the body 123 is provided with a muffler channel 124, the muffler channel 124 is connected to the muffler outlet 122; wherein, at least one of the mating part 121 and the body 123 is a heat insulation element.

[0071] In this embodiment, the muffler 120 includes a body 123. Specifically, a mating portion 121 is disposed on the body 123, and the mating portion 121 extends protrudingly away from the body 123. Optionally, the mating portion 121 and the body 123 are integrally formed.

[0072] The main body 123 is provided with a silencing channel 124, which is connected to the silencing outlet 122. Specifically, when the compressor draws in gas, the low-temperature refrigerant flows into the compression chamber through the silencing channel 124, the silencing outlet 122 and the suction port 111 in sequence. During this process, since at least part of the mating part 121 is embedded in the groove 112, the contact between the valve plate 110 and the refrigerant can be effectively reduced, the heat transfer from the valve plate 110 to the refrigerant can be reduced, the problem of suction overheating can be significantly improved, the suction efficiency can be improved, and thus the overall energy efficiency of the compressor can be improved.

[0073] Specifically, the mating part 121 is a heat-insulating component, or the body 123 is a heat-insulating component, or both the mating part 121 and the body 123 are heat-insulating components. The specific configuration can be determined according to actual needs. Optionally, the heat-insulating component may include a plastic part. That is, the mating part 121 and / or the body 123 are made of heat-insulating material. It is understood that the heat-insulating material has a low thermal conductivity, which can hinder heat transfer from the valve plate 110 to the refrigerant, further improving the problem of suction overheating, increasing suction efficiency, and thus improving the overall energy efficiency of the compressor.

[0074] like Figure 1 As shown, in some embodiments, the valve plate 110 may optionally be provided with at least two limiting holes 116, the at least two limiting holes 116 being located on the side of the intake port 111 away from the exhaust port 113 and arranged along the width direction of the valve plate 110; the muffler 120 may also include at least two limiting posts 125, the at least two limiting posts 125 being inserted into at least two limiting holes 116 respectively.

[0075] In this embodiment, the valve plate 110 is further provided with at least two limiting holes 116. Specifically, the at least two limiting holes 116 are located on the side of the air intake 111 away from the exhaust port 113, and the at least two limiting holes 116 are arranged along the width direction of the valve plate 110.

[0076] The muffler 120 also includes at least two limiting posts 125, which are respectively inserted into at least two limiting holes 116, thereby limiting the valve plate 110 and improving the assembly stability and reliability between the valve plate 110 and the muffler 120.

[0077] like Figure 2 As shown, in some embodiments, optionally, along the thickness direction of the valve plate 110, the length N of the mating portion 121 and the depth L of the recess 112 satisfy 0.4mm≤NL≤0.6mm; and / or the diameter D of the flow hole 114 satisfies 3mm≤D≤6mm.

[0078] In this embodiment, the range of the difference between the length of the mating part 121 and the depth of the recess 112 along the thickness direction of the valve plate 110 is defined. Specifically, the difference between the length of the mating part 121 and the depth of the recess 112 is between 0.4 mm and 0.6 mm. That is, when the mating part 121 is inserted into the recess 112, a space of 0.4 mm to 0.6 mm is maintained between the side of the valve plate 110 facing the muffler 120 and the end face of the muffler 120 in the thickness direction. This space is used to install a gasket to improve the sealing of the intake and exhaust assembly 100, prevent gas leakage, and ensure the compressor efficiency.

[0079] Optionally, the intake and exhaust assembly 100 also includes a gasket, which is fitted onto the mating part 121 and located between the end faces of the valve plate 110 and the muffler 120.

[0080] Furthermore, the diameter of the flow orifice 114 is limited to a range of 3 mm to 6 mm. If the diameter of the flow orifice 114 is too small, i.e., less than 3 mm, the throttling effect during gas exhaust is large, resulting in a large pressure loss. If the diameter of the flow orifice 114 is too large, i.e., greater than 6 mm, the flow pulsation during exhaust is large. By limiting the diameter of the flow orifice 114 to between 3 mm and 6 mm, the throttling effect during exhaust is avoided while reducing exhaust pulsation.

[0081] Optionally, the diameter D of the flow passage 114 is 4 mm or 5 mm.

[0082] In some embodiments, optionally, in the height direction of the valve plate 110, the cross-sectional shape of the intake port 111 is the same as the cross-sectional shape of the muffler outlet 122, and the flow area of ​​the intake port 111 is equal to the flow area of ​​the muffler outlet 122; and / or the valve plate 110 is also provided with a plurality of positioning holes 115, the valve plate 110 is connected to the cylinder head through the plurality of positioning holes 115, the plurality of positioning holes 115 are spaced apart on the outer periphery of the intake port 111, and each positioning hole 115 is configured to be close to the outer edge of the valve plate 110 and the distance between it and the center of the valve plate 110 is equal.

[0083] In this embodiment, the suction port 111 and the silencer outlet 122 are respectively defined in the height direction of the valve plate 110. The cross-sectional shape of the suction port 111 and the cross-sectional shape of the silencer outlet 122 are the same and the flow area is equal. That is to say, the cross-sectional shape of the suction port 111 is consistent with the cross-sectional shape of the silencer outlet 122, thereby reducing the flow resistance of the gas and reducing the flow loss during the compressor suction process, and ensuring the compressor efficiency.

[0084] The valve plate 110 is also provided with multiple positioning holes 115. Specifically, the valve plate 110 is connected to the cylinder head through multiple positioning holes 115. The multiple positioning holes 115 are distributed at intervals on the outer periphery of the intake port 111, and each positioning hole 115 is located close to the outer edge of the valve plate 110. That is to say, the multiple positioning holes 115 are circumferentially distributed. The distance between each positioning hole 115 and the center of the valve plate 110 is equal, that is, the multiple positioning holes 115 are evenly distributed, thereby ensuring that the fixed position of the valve plate 110 can be evenly stressed, which helps to extend the service life of the valve plate 110 and improve the reliability of the compressor.

[0085] According to a second aspect of the present invention, a compressor is provided, comprising the intake and exhaust assembly 100 as provided in any of the above embodiments, and thus possessing all the beneficial technical effects of the intake and exhaust assembly 100, which will not be repeated here.

[0086] According to a third aspect of the present invention, a refrigeration device is provided, comprising an intake and exhaust assembly 100 or a compressor as provided in any of the above embodiments, and thus possessing all the beneficial technical effects of the intake and exhaust assembly 100 or the compressor, which will not be repeated here.

[0087] In the description of this specification, the terms "connection," "installation," and "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0088] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0089] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A suction and exhaust assembly, characterized in that, include: Cylinder head, wherein the cylinder head is provided with a cavity; A valve plate is connected to the cylinder head. The valve plate is provided with an intake port, a groove, an exhaust port, and a flow hole. The intake port is connected to the groove, and the flow hole is connected to the cavity. An exhaust valve is located on the side of the valve plate near the cylinder head, and is used to open or close the exhaust port. The exhaust port is opened based on the exhaust valve, and the exhaust port is in communication with the cavity. A muffler is provided on the cylinder head. The muffler includes a mating part, at least a portion of which is embedded in the recess. Along the thickness direction of the valve plate, the mating part directly abuts against the wall of the recess. The mating part is provided with a muffler outlet, which is connected to the intake port.

2. The intake and exhaust assembly according to claim 1, characterized in that, The thickness H of the valve plate and the depth L of the settling groove satisfy the condition that H / 2 ≤ L < H.

3. The intake and exhaust assembly according to claim 1, characterized in that, Along the height direction of the valve plate, there is a gap between the outer wall of the mating part and the wall of the settling tank.

4. The intake and exhaust assembly according to claim 3, characterized in that, The gap surrounds the mating part.

5. The intake and exhaust assembly according to claim 3, characterized in that, The gap h satisfies h≤0.2mm.

6. The intake and exhaust assembly according to any one of claims 1 to 5, characterized in that, The silencer includes: The main body, wherein the mating part is located on the outside of the main body and extends protruding away from the main body, the main body is provided with a noise reduction channel, and the noise reduction channel is connected to the noise reduction outlet; Wherein, at least one of the mating part and the body is a heat insulation component.

7. The intake and exhaust assembly according to any one of claims 1 to 5, characterized in that, The valve plate is also provided with at least two limiting holes, which are located on the side of the air intake opposite to the exhaust port and are arranged along the width direction of the valve plate. The muffler also includes at least two limiting posts, and the at least two limiting posts are respectively inserted into at least two limiting holes.

8. The intake and exhaust assembly according to any one of claims 1 to 5, characterized in that, Along the thickness direction of the valve plate, the length N of the mating portion and the depth L of the countersink satisfy the following condition: 0.4mm ≤ NL ≤ 0.6mm; and / or The diameter D of the flow passage satisfies 3mm≤D≤6mm.

9. The intake and exhaust assembly according to any one of claims 1 to 5, characterized in that, In the height direction of the valve plate, the cross-sectional shape of the air intake is the same as that of the silencer outlet, and the flow area of ​​the air intake is equal to that of the silencer outlet. and / or The valve plate is also provided with a plurality of positioning holes. The valve plate is connected to the cylinder head through the plurality of positioning holes. The plurality of positioning holes are distributed at intervals on the outer periphery of the intake port. Each positioning hole is configured to be close to the outer edge of the valve plate and to be equidistant from the center of the valve plate.

10. A compressor, characterized in that, Includes the intake and exhaust assembly as described in any one of claims 1 to 9.

11. A refrigeration device, characterized in that, include: The intake and exhaust assembly as described in any one of claims 1 to 9; or The compressor as described in claim 10.

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