Exhaust valve, exhaust assembly, compressor and refrigeration equipment of compressor

Abstract

The application discloses a compressor exhaust valve plate, an exhaust assembly, a compressor and a refrigeration device, and belongs to the technical field of compressors. The exhaust valve plate comprises a movable section and at least one tooth portion. The movable section is used for opening or closing an exhaust hole of an exhaust valve seat. The tooth portion is arranged on the outer circumferential edge of the movable section. The exhaust valve plate is corresponded to the exhaust hole of the exhaust valve seat through the movable section. The tooth portion can generate certain interference on the airflow at the exhaust hole. The width of the end portion of the tooth portion connected with the movable section is greater than the width of the end portion of the tooth portion away from the movable section. The width of the tooth portion can be gradually reduced in the direction away from the movable section. The distribution of the flow field near the exhaust hole can be improved, the exhaust noise can be reduced, and the purpose of reducing the exhaust noise is achieved. The exhaust assembly is suitable for the compressor.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to an exhaust valve plate of a compressor, an exhaust assembly of a compressor, a compressor and a refrigeration equipment. BACKGROUND

[0002] The exhaust noise of the compressor mainly includes the noise generated by the high-speed high-pressure fluid being discharged from the exhaust hole, the noise generated by the vibration of the exhaust valve plate, the vibration noise generated by the high-speed fluid driving the exhaust valve plate to hit the limiter, etc., so that the working noise of the compressor is relatively large. SUMMARY

[0003] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, the present application provides an exhaust valve plate of a compressor, which can be beneficial to improve the flow field at the exhaust hole, reduce the exhaust noise, and has a better noise reduction effect.

[0004] The present application further provides an exhaust assembly of a compressor, a compressor and a refrigeration equipment comprising the above-mentioned exhaust valve plate.

[0005] The exhaust valve plate of the compressor according to the first aspect of the present application comprises: a movable section for opening or closing an exhaust hole of an exhaust valve seat of the compressor; and at least one tooth portion provided on an outer periphery of the movable section, wherein the width of an end portion of the tooth portion connected to the movable section is greater than the width of an end portion of the tooth portion away from the movable section.

[0006] The exhaust valve plate of the compressor according to the present application has at least the following beneficial effects:

[0007] The exhaust valve plate of the embodiment corresponds to the exhaust hole of the exhaust valve seat through the movable section, and the movable section can move to open or close the exhaust hole. By adding at least one tooth portion on the outer periphery of the movable section, the tooth portion can interfere with the airflow at the exhaust hole, and the width of the end portion of the tooth portion connected to the movable section is greater than the width of the end portion of the tooth portion away from the movable section, so that the width of the tooth portion is gradually reduced in the direction away from the movable section, which can improve the distribution of the flow field near the exhaust hole and is beneficial to reduce the exhaust noise, thereby achieving the purpose of reducing the exhaust noise, and is suitable for the exhaust assembly of the compressor.

[0008] According to some embodiments of the present application, the profile lines on both sides of any tooth portion change in a power exponential curve towards the direction away from the movable section, the distance between the profile line and the center line of the tooth portion in the width direction is H, the distance between the profile line and the movable section in the length direction of the tooth portion is x, the coefficient of the power exponential curve is A, the constant of the power exponential curve is Ho, and the exponent of the power exponential curve is m, and H = Ax m or H = Ax m+ Ho, and m≥2, A>0, 0mm

[0009] According to some embodiments of the present application, the exponent m of the power exponential curve satisfies: 2.5≤m≤3.

[0010] According to some embodiments of the present application, the length of the tooth portion is L1, satisfying: L1≥2mm.

[0011] According to some embodiments of the present application, the width of the tooth portion away from the end of the movable section is L2, satisfying: 0

[0012] According to some embodiments of the present application, the width L2 of the tooth portion away from the end of the movable section satisfies: 0

[0013] According to some embodiments of the present application, the included angle between the center lines of any two adjacent tooth portions satisfies: a≥20°.

[0014] According to some embodiments of the present application, the profile lines of any two adjacent tooth portions are connected by a circular arc transition, and the fillet radius of the circular arc satisfies: R≥0.3mm.

[0015] The exhaust assembly of the compressor according to the second aspect of the embodiments of the present application comprises an exhaust valve seat, a limiter, and the exhaust valve sheet according to the first aspect of the embodiments of the present application, the exhaust valve seat is provided with an exhaust hole, the limiter is arranged on the exhaust valve seat, and the exhaust valve sheet is arranged between the exhaust hole and the limiter.

[0016] The exhaust assembly of the compressor according to the embodiments of the present application has at least the following beneficial effects:

[0017] The exhaust assembly adopts the exhaust valve sheet of the embodiments, the exhaust valve sheet is installed on the exhaust valve seat, the exhaust valve sheet is arranged between the exhaust valve seat and the limiter, the movable section of the exhaust valve sheet corresponds to the exhaust hole, and the movable section can move to open or close the exhaust hole; at least one tooth portion is added to the periphery of the movable section, the tooth portion can interfere with the airflow at the exhaust hole, the width of the end of the tooth portion connected with the movable section is greater than the width of the end of the tooth portion away from the movable section, the width of the tooth portion can be gradually reduced towards the direction away from the movable section, the distribution of the flow field near the exhaust hole can be improved, the exhaust noise can be reduced, the working noise of the compressor can be reduced, and the purpose of reducing the exhaust noise is achieved.

[0018] According to some embodiments of the present application, the exhaust valve sheet is provided with a mounting section connected with the exhaust valve seat, the mounting section and the limiter are both provided with mounting holes, and the exhaust valve sheet and the limiter are installed on the exhaust valve seat through rivets fitted in the mounting holes.

[0019] The compressor according to the third aspect of the present application comprises the exhaust assembly according to the second aspect of the present application.

[0020] The compressor adopts all the technical solutions of the exhaust assembly according to the above embodiments, and thus at least has all the beneficial effects brought by the technical solutions of the above embodiments.

[0021] The refrigeration equipment according to the fourth aspect of the present application comprises the compressor according to the third aspect of the present application.

[0022] The refrigeration equipment adopts all the technical solutions of the compressor according to the above embodiments, and thus at least has all the beneficial effects brought by the technical solutions of the above embodiments.

[0023] Other features and advantages of the present application will be described in the following description and, in part, will become apparent from the description or will be learned from the practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0024] The present application will be further described below in conjunction with the drawings and embodiments, in which:

[0025] Figure 1 is a front structure schematic diagram of an exhaust valve plate according to an embodiment of the present application;

[0026] Figure 2 is a three-dimensional structure schematic diagram of an exhaust valve plate according to an embodiment of the present application;

[0027] Figure 3 is a structure schematic diagram of an upper bearing and an exhaust assembly according to an embodiment of the present application;

[0028] Figure 4 is a comparison diagram of noise reduction effects of an exhaust valve plate according to an embodiment of the present application and a conventional exhaust valve plate;

[0029] Figure 5 is a cross-sectional structure schematic diagram of a compressor according to an embodiment of the present application.

[0030] Reference Signs:

[0031] Exhaust valve plate 100; mounting section 110; first mounting hole 111; connecting section 120; movable section 130; tooth portion 140; contour line 141; tooth groove 142; tip 143; circular arc 144;

[0032] Exhaust assembly 200; exhaust valve seat 210; exhaust hole 211; rivet 212; stopper 220;

[0033] Housing 300;

[0034] Driving mechanism 400; rotor assembly 410; stator assembly 420;

[0035] Compression mechanism 500; Cylinder 510; Upper bearing 520; Shaft hole 521; Lower bearing 530; Crankshaft 540; Piston 550;

[0036] Compressor 1000. DETAILED DESCRIPTION

[0037] Embodiments of the present application are described in detail below with reference to the attached drawings, which show by way of example, embodiments in which the same or similar elements have the same or similar reference numbers. The embodiments described below are examples only, and are not to be construed as limiting the present application.

[0038] In the description of the present application, it should be understood that the relative description of direction, such as up, down, etc. is based on the orientation or positional relationship shown in the drawings, and is only for the purpose of facilitating the description of the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation of the present application.

[0039] In the description of the present application, the plural refers to two or more. If there is a description of first, second, it is only for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated or the order of technical features indicated.

[0040] In the description of the present application, it should be noted that the words such as setting, mounting, connecting, etc. should be understood broadly, and the person skilled in the art can determine the specific meaning of the above words in the present application in combination with the specific content of the technical solution.

[0041] The technical solutions of the present application will be described below in conjunction with the drawings. Obviously, the following described embodiments are part of the embodiments of the present application, not all embodiments.

[0042] It can be understood that the exhaust noise is one of the main sources of the compressor and the air conditioning system noise. For the rotary compressor, the exhaust noise mainly includes the monopole source noise generated by the high-speed high-pressure fluid discharged from the exhaust hole; the monopole source noise generated by the vibration of the exhaust valve plate; the vibration noise generated by the high-speed fluid striking the stopper of the exhaust valve plate; the vibration noise generated by the exhaust valve plate striking the exhaust valve seat; the dipole source noise generated by the high-speed fluid discharged under the influence of the hard boundary of the exhaust valve plate, the stopper, the exhaust valve seat and the muffler, etc. As can be seen, the exhaust noise is closely related to the flow field at the exhaust hole. The exhaust valve plate 100 of the embodiment of the present application can improve the exhaust noise by increasing the tooth structure to affect the flow field velocity distribution and pressure distribution at the exhaust hole 211, thereby achieving the purpose of reducing the exhaust noise.

[0043] Reference will be made to Figures 1 to 2 The exhaust valve plate 100 of the embodiment of the present application is described below, which is suitable for the compressor 1000, for example, the rotary compressor, and is particularly applied to the exhaust assembly 200 of the compressor 1000.

[0044] Referring to Figure 1 and Figure 2 As shown in the figures, the exhaust valve plate 100 of the embodiment of the present application includes a mounting section 110, a connecting section 120 and a movable section 130. The mounting section 110 is used to connect the exhaust valve seat 210. One end of the connecting section 120 is connected to the mounting section 110, and the other end of the connecting section 120 is connected to the movable section 130. After the exhaust valve plate 100 is fixed to the exhaust valve seat 210, the movable section 130 corresponds to the exhaust hole 211 of the exhaust valve seat 210. The movable section 130 can move between the position of opening the exhaust hole 211 and the position of closing the exhaust hole 211. The exhaust valve plate can open or close the exhaust hole 211 through the movable section 130.

[0045] Referring to Figure 1 and Figure 2 As shown in the figures, Figure 1 Fig. 2 shows a front structure schematic diagram of the exhaust valve plate 100, Figure 2 Fig. 3 shows a three-dimensional structure schematic diagram of the exhaust valve plate 100. It can be understood that the exhaust valve plate 100 is generally in the form of a thin plate. The mounting section 110, the connecting section 120 and the movable section 130 are connected in sequence along the length direction of the exhaust valve plate 100 to form an integrated structure. The thickness of the mounting section 110, the connecting section 120 and the movable section 130 is consistent, that is, the thickness of the exhaust valve plate 100 is uniformly distributed along the length direction. The structure is stable and reliable, and is convenient for processing and forming the exhaust valve plate 100. In some embodiments, the mounting section 110, the connecting section 120 and the movable section 130 can also be set to different thicknesses, which are not limited in particular.

[0046] Referring to Figure 1 and Figure 2 As shown, it can be understood that a plurality of tooth portions 140 are arranged on the periphery of the active section 130, and the number of the tooth portions 140 is specifically seven, the seven tooth portions 140 are uniformly distributed on the edge of the active section 130, and tooth grooves 142 are formed between adjacent tooth portions 140, each tooth portion 140 extends towards the direction away from the active section 130 and the width of the tooth portion 140 gradually decreases, so that the width of the end of the tooth portion 140 connected with the active section 130 is greater than the width of the end of the tooth portion 140 away from the active section 130, that is, each tooth portion 140 gradually narrows towards the direction away from the active section 130, so that the tip of the tooth portion 140 forms a pointed end 143. It should be noted that the outer periphery of the active section 130 is in the shape of a circular arc, so that the plurality of tooth portions 140 are more uniformly distributed along the outer periphery of the active section 130, forming a sawtooth structure. As shown in Figure 1 As shown, the width direction of the tooth portion 140 can be understood as the opposite direction of the contour lines 141 on both sides of the tooth portion 140, and the length direction of the tooth portion 140 can be understood as the direction away from the active section 130.

[0047] Referring to Figure 3 As shown, it can be understood that the exhaust valve sheet 100 of the embodiment is suitable for the exhaust assembly 200 of the compressor 1000, when the exhaust valve sheet 100 is installed on the exhaust valve seat 210, the active section 130 corresponds to the exhaust hole 211, and the side of the active section 130 towards the exhaust hole 211 is the windward side and the side away from the exhaust hole 211 is the leeward side; after the fluid is discharged from the exhaust hole 211, it spreads in all directions along the windward side, when the fluid passes through the outer periphery of the active section 130, the tooth portions 140 can interfere with the fluid discharged from the exhaust hole 211, a part of the fluid will flow to the leeward side through the tooth grooves 142 between the tooth portions 140, and a part of the fluid will flow along the tooth portions 140; since the width of the tooth portion 140 gradually decreases towards the direction away from the active section 130, the fluid can flow to the end of the tooth portion 140 along the contour lines 141 on both sides of the tooth portion 140, so that the distribution of the flow field near the exhaust hole 211 can be changed. It should be noted that the airflow discharged from the exhaust hole 211 flows along the axial direction of the exhaust hole 211, the active section 130 disturbs the airflow to form a flow field, and the interference of the sawtooth structure to the flow field can improve the flow field near the exhaust hole 211, which is beneficial to reduce the exhaust noise, so as to achieve the purpose of reducing the exhaust noise, and the noise reduction effect is good; the exhaust assembly 200 is applied to the compressor 1000, so that the working noise of the compressor 1000 can be effectively reduced.

[0048] Referring to Figure 1 and Figure 2It is to be noted that the tooth portion 140 is integrally formed with the movable segment 130, the connecting segment 120 and the mounting segment 110 in the embodiment, for example, the exhaust valve plate 100 can be integrally formed by stamping a plate body, which has high structural stability and reliability. The width of the movable segment 130 is greater than the width of the connecting segment 120 in the embodiment, which is conducive to the movement of the movable segment 130 relative to the connecting segment 120. The length and width of the movable segment 130 meet certain dimensions, so that the movable segment 130 can completely cover the exhaust hole 211 when closing the exhaust hole 211. The specific dimensions are set according to actual application requirements, which are not limited here. In addition, the number of tooth portions 140 is not limited to the number shown in the above embodiment. The movable segment 130 can be provided with one, two or more tooth portions 140 to achieve the purpose of changing the flow field distribution.

[0049] Referring to Figure 1 and Figure 2 It can be understood that the exhaust noise is related to the flow field at the exhaust hole 211, and improving the distribution of the flow field can achieve the purpose of reducing the exhaust noise. The exhaust valve plate 100 of the embodiment further optimizes the tooth portion 140. Specifically, the profile lines 141 on both sides of the tooth portion 140 are set to change in a power exponential curve towards the direction away from the movable segment 130, and the power exponential curve satisfies H=Ax m or H=Ax m +Ho, where the distance between the profile line 141 and the center line of the tooth portion 140 in the width direction is H, the distance between the profile line 141 and the movable segment 130 in the length direction of the tooth portion 140 is x, the coefficient of the power exponential curve is A, the constant of the power exponential curve is Ho, and the index of the power exponential curve is m, where m≥2, A>0, 0mm<Ho≤0.5mm. As Figure 1 and Figure 2 As shown in the cases where the width of the tooth portion 140 gradually decreases towards the direction away from the movable segment 130, and the profile lines 141 on both sides of the tooth portion 140 change in a power exponential curve, the width of the tooth portion 140 changes in a power exponential rule. The farther the distance from the movable segment 130, the greater the width reduction of the tooth portion 140, and the width of the end of the tooth portion 140 is the smallest.

[0050] It should be noted that the contour lines 141 on both sides of the tooth 140 can be understood as the boundary contour lines 141 of the tooth 140 along its width direction. Using coordinates as a reference, the contour lines 141 on both sides of the tooth 140 can be understood as power-law curves on a coordinate system. In the plane containing the contour lines 141, the coordinates along the width direction of the tooth 140 are the ordinates, and the center line of the tooth 140 along its width direction is the abscissa. The intersection of the center line and the end of the tooth 140 is the origin. The contour lines 141 on both sides of the tooth 140 are symmetrically distributed on both sides of the abscissa. It can be understood that the width of the tooth 140 is greatest at the end connecting to the movable segment 130, where the ordinate value of the contour line 141 is greatest, and the width of the tooth 140 is also greatest; the ordinate value of the contour line 141 is smallest at the origin, where the width of the tooth 140 is smallest. It is understood that in some embodiments, the contour lines 141 on both sides of the tooth 140 may also be asymmetrically distributed, that is, the power exponent curves corresponding to the contour lines 141 on both sides of the tooth 140 are different; the coefficient A in the power exponent curves on both sides must be greater than zero so that the distance H between the contour line 141 and the center line of the tooth 140 can be greater than zero and change in a power exponent form. For example, the value of A can be 0.5, 1, 2, etc., and the value of A is set according to the usage requirements of different application scenarios.

[0051] It is understandable that the power curve includes H = Ax mm and H = Ax m +Ho two formula forms, power curve H=Ax m +Ho and H=Ax m The difference lies in adding a constant Ho. With parameters x and A remaining constant, as the curve constant Ho changes, the power curve H = Ax... m +Ho and the power curve H=Ax m The position along the vertical axis changes, but the shape of the curve remains unchanged. When the power curve is H = Ax... m In the formal sense, the dimension of the tip 143 of the tooth 140 can theoretically be understood as zero; however, considering that the dimension of the tip 143 of the tooth 140 is generally not zero in practical applications, it needs to be considered in Ax. m The addition of a constant Ho indicates that the end of tooth 140 has a certain dimension, making it easier to manufacture. The value of the constant Ho needs to be greater than 0 mm and less than or equal to 0.5 mm, and is set according to the actual application requirements. For example, using the power curve H = Ax m Taking +Ho as an example, the exponent m is 2, the coefficient A is 0.5, and the constant Ho is 0.1, that is, the power exponent curve function is H = 0.5x. 2+0.1, the tip 143 of the tooth portion 140 has a width of 0.1 mm (millimeter); x has a value of 2 mm, and the corresponding H is 2.1 mm, since the width of the tooth portion 140 is equal to the distance between the profile lines 141 on both sides, and the width of the tooth portion 140 at this point is 4.2 mm.

[0052] It should be noted that the greater the value of the exponent m of the power exponent curve, the faster the width dimension of the tooth portion 140 changes. In the embodiment of the present application, the value of the exponent m of the power exponent curve is preferably in the range of 2.5≤m≤3 under the condition that it is greater than or equal to 2, so that the shape of the tooth portion 140 formed is more conducive to improving the flow field at the exhaust hole 211.

[0053] Referring to FIGS. 1 and 2, Figure 1 and Figure 2 It can be understood that, under the condition that the profile lines 141 on both sides of the tooth portion 140 satisfy the variation law of the power exponent curve, the profile lines 141 on both sides of the tooth portion 140 are understood as acoustic black hole curves, that is, the boundary positions on both sides of the tooth portion 140 are acoustic black hole regions. Based on the principle of acoustic black holes, the propagation speed of waves in the acoustic black hole region gradually decreases by using the power exponent variation of the geometric parameters or material characteristic parameters of the thin-walled structure, and in an ideal case, the wave speed can be reduced to zero, so that the phenomenon of reflection does not occur. The use of acoustic black holes can concentrate the wave energy propagating in the structure at a specific position, thereby having obvious advantages in the application of vibration and noise reduction of thin-walled structures.

[0054] Referring to FIGS. 1 and 2, Figure 3 and Figure 3 FIG. 2 shows a cross-sectional view of the exhaust assembly 200 according to an embodiment of the present application. It can be understood that the embodiment increases the acoustic black hole structure on each tooth portion 140, so that the sawtooth structure has the vibration and noise reduction effect of the acoustic black hole. When the high-speed fluid is discharged from the exhaust hole 211 and passes along the outer periphery of the movable section 130, the use of the sawtooth structure can reduce the propagation speed of waves of a certain frequency, so that the wave energy can be dissipated at the tip 143, the flow field speed distribution at the exhaust hole 211 can be improved, and thus the monopole source noise generated by the fluid discharged from the exhaust hole 211 and the monopole source noise generated by the vibration of the exhaust valve plate 100 can be reduced. Moreover, the pressure distribution at the exhaust hole 211 can be further improved, so that the windward surface and the leeward surface of the sawtooth structure generate a certain pressure difference under the action of the fluid, the force of the exhaust valve plate 100 impacting the stopper 220 is reduced, and thus the vibration noise generated by the exhaust valve plate 100 impacting the stopper 220 is reduced, the exhaust noise of the exhaust assembly 200 is effectively reduced, and the sawtooth structure has a better noise reduction effect.

[0055] Referring to FIGS. 1 and 2, Figure 1 and Figure 2It is to be noted that the acoustic black hole structure of the embodiment of the present application is arranged at the outer periphery of the active section 130, and the acoustic black hole curve extends towards the direction away from the active section 130, so that the position of the wave gathering and deceleration occurs at the outermost end of the tooth portion 140 away from the active section 130, and the outermost end is least constrained by the structure and is easier to deform, so that the acoustic black hole effect is more likely to occur, and the multiple tooth portions 140 have better vibration reduction and noise reduction effects.

[0056] Referring to Figure 1 It is to be noted that the acoustic black hole structure of the embodiment of the present application is arranged at the outer periphery of the active section 130, and the acoustic black hole curve extends towards the direction away from the active section 130, so that the position of the wave gathering and deceleration occurs at the outermost end of the tooth portion 140 away from the active section 130, and the outermost end is least constrained by the structure and is easier to deform, so that the acoustic black hole effect is more likely to occur, and the multiple tooth portions 140 have better vibration reduction and noise reduction effects.

[0057] Referring to Figure 1 It is to be noted that the acoustic black hole structure of the embodiment of the present application is arranged at the outer periphery of the active section 130, and the acoustic black hole curve extends towards the direction away from the active section 130, so that the position of the wave gathering and deceleration occurs at the outermost end of the tooth portion 140 away from the active section 130, and the outermost end is least constrained by the structure and is easier to deform, so that the acoustic black hole effect is more likely to occur, and the multiple tooth portions 140 have better vibration reduction and noise reduction effects.

[0058] Referring to Figure 1As shown, it can be understood that the plurality of teeth 140 are distributed in the circumferential direction of the movable section 130, and in the embodiment, the center line of the tooth 140 is taken as a reference, the included angle between the center lines of adjacent teeth 140 is α, which satisfies: α≥20°. The included angle α represents the angle occupied by the teeth 140 in the circumferential direction of the movable section 130. The larger the included angle α, the larger the angle occupied by the teeth 140, and the larger the opening of the tooth groove 142 of the adjacent teeth 140, which is beneficial to make the flow field distribution more uniform. The windward surface and the leeward surface of the tooth 140 generate a certain pressure difference under the action of the fluid, which is beneficial to reduce the force of the exhaust valve plate 100 impacting the limiter 220. The included angle between the center lines of adjacent teeth 140 can be set according to the number of teeth 140 and application requirements, and is not specifically limited. It can be understood that if the angle occupied by the teeth 140 in the circumferential direction of the movable section 130 is too small, the opening of the tooth groove 142 is small, which generates a large resistance to high-speed fluid, affects the flow field velocity distribution and pressure distribution, and limits the noise reduction effect.

[0059] Referring to Figure 1 As shown, it can be understood that the tooth groove 142 is formed between adjacent teeth 140, and the profile lines 141 of the inner walls on both sides of the tooth groove 142 are acoustic black hole curves. The profile lines 141 on both sides are connected through a circular arc 144 at the bottom position of the tooth groove 142. The fillet radius of the circular arc 144 is R, which satisfies: R≥0.3mm. Since the exhaust valve plate 100 is a moving part, the movable section 130 can move between the position of closing the exhaust hole 211 and the position of opening the exhaust hole 211. Considering that the fillet radius of the circular arc 144 is too small, it may cause stress concentration at the transition connection between adjacent teeth 140, reduce the structural reliability, and not meet the long-term fatigue strength requirement. Therefore, in the embodiment, the fillet radius R of the circular arc 144 is greater than or equal to 0.3mm, which can effectively solve the problem of stress concentration at the transition connection between adjacent teeth 140, and improve the structural reliability.

[0060] Referring to Figure 3 and Figure 5 As shown, Figure 3 As shown is a cross-sectional structure schematic diagram of a bearing of the compressor 1000. The exhaust assembly 200 provided by the embodiment of the present application is installed on the bearing. The exhaust assembly 200 includes an exhaust valve seat 210, a limiter 220 and an exhaust valve plate 100. The bearing is provided with a shaft hole 521. The exhaust valve plate 100 adopts the structure of the above-mentioned embodiment. The exhaust valve seat 210 is located at the end face of the bearing. The exhaust valve seat 210 is provided with an exhaust hole 211. The limiter 220 and the exhaust valve plate 100 are both installed in the exhaust valve seat 210. The exhaust valve plate 100 is located between the exhaust hole 211 and the limiter 220. Figure 3 The structure of the limiter 220 is not shown in the figure.

[0061] Referring to Figure 1 , Figure 2 and Figure 3 As shown, the mounting section 110 of the exhaust valve plate 100 has a first mounting hole 111, one end of the limiter 220 has a second mounting hole, and the bottom of the exhaust valve seat 210 has a third mounting hole. A rivet 212 passes through the first mounting hole 111, the second mounting hole, and the third mounting hole to rivet the exhaust valve plate 100 and the limiter 220 to the bottom of the exhaust valve seat 210, thereby mounting the exhaust valve plate 100 and the limiter 220 on the exhaust valve seat 210. The movable section 130 of the exhaust valve plate 100 corresponds to the exhaust hole 211, and the limiter 220 is located on the side of the exhaust valve plate 100 facing away from the exhaust hole 211. The limiter 220 restricts the range of motion of the exhaust valve plate 100. It should be noted that in this embodiment, the bearing also includes a muffler (not shown in the attached drawings). The muffler covers the exhaust assembly 200, defines a muffler cavity, and the exhaust assembly 200 is located within the muffler cavity. The muffler reduces exhaust noise.

[0062] Reference Figure 3 As shown, the movable section 130 of the exhaust valve plate 100 has multiple teeth 140 along its circumference. The contour lines 141 on both sides of each tooth 140 are acoustic black hole curves. The specific structure of the tooth 140 can be found in [reference needed]. Figure 1 and Figure 2 The embodiment shown will not be described in detail here. It is understood that in this embodiment, the teeth 140 are arranged to form a sawtooth structure. By combining the sawtooth structure with the acoustic black hole structure, high-speed fluid is discharged from the exhaust port 211 of the bearing and enters the silencer cavity after passing through the exhaust valve plate 100. When the fluid passes through the exhaust valve plate 100, the sawtooth structure with the acoustic black hole curve interferes with the flow field, improving the velocity and pressure distribution at the exhaust port 211. This causes a certain pressure difference between the windward and leeward sides of the sawtooth structure under the action of the fluid, reducing the force of the exhaust valve plate 100 impacting the limiter 220. This reduces the structural vibration noise generated by the high-speed fluid driving the exhaust valve plate 100 to strike the limiter 220, as well as the structural vibration noise generated by the exhaust valve plate 100 striking the exhaust valve seat 210. Furthermore, the silencer can reduce the resonance noise generated by the compression cavity and the silencer cavity, achieving the purpose of reducing exhaust noise. It has a better noise reduction effect, thereby effectively reducing the operating noise of the compressor 1000.

[0063] Reference Figure 4 As shown, Figure 4 The image shown is a comparison of the noise reduction effect of the exhaust valve plate 100 using the embodiment of the present invention and a conventional exhaust valve plate. It can be understood that... Figure 4 The horizontal axis in the graph represents the noise frequency band and the corresponding noise improvement in dB (decibels), while the vertical axis represents the noise in decibels. The graph also includes... The noise reduction effect of the exhaust valve plate 100 of the embodiment of the present application is improved compared with the conventional exhaust valve plate, for example, at the frequency band of 630Hz, the exhaust valve plate 100 of the embodiment can reduce the noise value by 2.3db; at the frequency band of 2500Hz, the exhaust valve plate 100 of the embodiment can reduce the noise value by 3.1db, and in the frequency band range of 4000Hz to 16000Hz, the exhaust valve plate 100 of the embodiment can also reduce certain exhaust noise, that is, the exhaust valve plate 100 of the embodiment of the present application has more obvious noise reduction effect for the medium and high frequency band, thereby effectively reducing the working noise of the compressor 1000. It should be noted that, Figure 4 The rightmost contrast graph represents the total noise energy, and through comparison, it can be seen that the exhaust valve plate 100 of the embodiment can reduce the total noise energy by 1db.

[0064] Referring to Figure 5 The compressor 1000 comprises a shell 300 and a driving mechanism 400 and a compression mechanism 500 installed in the shell 300, wherein the driving mechanism 400 comprises a rotor assembly 410 and a stator assembly 420, the rotor assembly 410 is rotatably arranged inside the stator assembly 420; the compression mechanism 500 comprises a cylinder 510, a piston 550, a crankshaft 540, an upper bearing 520 and a lower bearing 530, the upper bearing 520 and the lower bearing 530 are arranged on the upper and lower sides of the cylinder 510 respectively, and the crankshaft 540 is supported by the upper bearing 520 and the lower bearing 530; the rotor assembly 410 drives the crankshaft 540 to rotate, and the crankshaft 540 drives the piston 550 to rotate in the cylinder 510 to compress the refrigerant. The exhaust assembly 200 of the embodiment of the present application is specifically installed in the upper bearing 520, and the compressor 1000 adopts all the technical solutions of the exhaust assembly 200 of the above embodiment, and therefore at least has all the beneficial effects brought by the technical solutions of the above embodiment, which will not be described here.

[0065] The embodiment of the present application also provides a refrigeration equipment (not shown in the drawings), which comprises the compressor 1000 of the above embodiment. The refrigeration equipment adopts all the technical solutions of the compressor 1000 of the above embodiment, and therefore at least has all the beneficial effects brought by the technical solutions of the above embodiment.

[0066] The above describes the embodiments of the present application in detail in combination with the drawings, but the present application is not limited to the above embodiments, and various changes can be made within the knowledge range of ordinary skilled in the art without departing from the purpose of the present application.

Claims

1. The discharge valve plate of a compressor, characterized in that, include: The movable section is used to open or close the exhaust port of the compressor's exhaust valve seat; At least one tooth is provided on the outer periphery of the movable segment, and the width of the end of the tooth connected to the movable segment is greater than the width of the end of the tooth away from the movable segment. The contour lines on both sides of any of the teeth exhibit a power-law curve trend away from the movable segment. The distance between the contour line and the centerline of the tooth along its width is H, and the distance between the contour line and the movable segment along the length of the tooth is x. The coefficient of the power-law curve is A, the constant of the power-law curve is Ho, and the exponent of the power-law curve is m, satisfying: H = Ax Or H=Ax +Ho, and m≥2, A>0, 0mm<Ho≤0.5mm.

2. The exhaust valve plate of the compressor according to claim 1, characterized in that, The exponent m of the power curve satisfies: 2.5 ≤ m ≤ 3.

3. The exhaust valve plate of the compressor according to claim 1 or 2, characterized in that, The length of the tooth is L1, which satisfies: L1≥2mm.

4. The exhaust valve plate of the compressor according to claim 1 or 2, characterized in that, The width of the end of the tooth furthest from the movable section is L2, which satisfies: 0 < L2 ≤ 0.2 mm.

5. The exhaust valve plate of the compressor according to claim 4, characterized in that, The width L2 of the end of the tooth furthest from the moving section satisfies: 0 < L2 ≤ 0.1 mm.

6. The exhaust valve plate of the compressor according to claim 1, characterized in that, The included angle between the center lines of any two adjacent teeth is α, which satisfies: α≥20°.

7. The exhaust valve plate of the compressor according to claim 1, characterized in that, The contour lines of any two adjacent teeth are connected by a circular arc transition, and the radius of the circular arc is R, which satisfies: R≥0.3mm.

8. The exhaust assembly of a compressor, characterized in that, It includes an exhaust valve seat, a limiter, and an exhaust valve plate as described in any one of claims 1 to 7, wherein the exhaust valve seat has an exhaust hole, the limiter is disposed on the exhaust valve seat, and the exhaust valve plate is disposed between the exhaust hole and the limiter.

9. The exhaust assembly of the compressor according to claim 8, characterized in that, The exhaust valve plate is provided with a mounting section that connects to the exhaust valve seat. Both the mounting section and the limiter are provided with mounting holes. The exhaust valve plate and the limiter are mounted to the exhaust valve seat by rivets that cooperate with the mounting holes.

10. A compressor, characterized in that, Includes the exhaust assembly of the compressor as described in claim 8 or 9.

11. A refrigeration device, characterized in that, Includes the compressor as described in claim 10.

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