Rotary compressor and refrigeration equipment
By adding an exhaust port to the rotary compressor and designing valve plate assemblies with different stiffnesses, staged opening and closing can be achieved, solving the problem of exhaust over-compression loss at high speeds and improving energy efficiency and reliability.
Patent Information
- Application Number
- CN202511598571.4
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-11-03
- Publication Date
- 2026-02-10
AI Technical Summary
At high speeds, the exhaust valve port of a rotary compressor suffers from severe over-compression losses due to size limitations. Furthermore, traditional solutions, such as increasing the twin-cylinder span or using multi-outlet designs, cannot effectively adapt to dynamic pressure changes at high speeds, thus affecting reliability and energy efficiency.
By adding an exhaust port to the rotary compressor and designing valve plate assemblies with different stiffnesses, the exhaust area can be increased through staged opening and closing, and the exhaust port can be closed sequentially by utilizing the rotor movement sequence to ensure airtightness.
It effectively reduces exhaust over-compression losses, improves energy efficiency, and ensures the reliability and exhaust efficiency of the rotary compressor.
Smart Images
Figure CN121497616A_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application relates to the technical field of compressor, in particular to a rotary compressor and a refrigeration equipment. BACKGROUND
[0002] In the process of high speed (120Hz) exhaust of the rotary compressor, especially the double cylinder structure with single exhaust valve, the high speed leads to high exhaust speed of the high pressure refrigerant in the compression chamber. Due to the size limitation of the exhaust valve port, the pressure in the compression chamber is always significantly greater than the pressure outside the exhaust valve, which leads to obvious exhaust over-compression loss. In order to increase the exhaust capacity, some models choose to increase the exhaust valve on the partition plate, which significantly increases the span between the double cylinders, increases the vibration of the compressor and reduces the reliability. SUMMARY
[0003] The main purpose of the present application is to provide a rotary compressor and a refrigeration equipment, which can increase the exhaust capacity, reduce the over-compression loss and ensure the reliability.
[0004] In order to achieve the above purpose, the present application provides a rotary compressor, which comprises a cylinder and an exhaust valve assembly, wherein the exhaust valve assembly comprises: a valve seat having a first exhaust hole and a second exhaust hole which are spaced apart and communicated with the cylinder, the first exhaust hole and the second exhaust hole both penetrating through the valve seat, and the second exhaust hole is arranged lower than the corresponding port of the first exhaust hole around the circumference of the port of the cylinder; a valve plate assembly comprising a first valve plate and a second valve plate which are spaced apart along the axial direction of the valve seat, the second valve plate is used to open and close the second exhaust hole, the first valve plate covers the second valve plate and the first exhaust hole, the first valve plate is used to open and close the first exhaust hole, and the rigidity of the second valve plate is less than that of the first valve plate.
[0005] In an embodiment, the thickness of the second valve plate is less than the thickness of the first valve plate; and / or, the diameter of the second exhaust hole is D2, and the diameter of the first exhaust hole is D1, wherein D2>0.6D1.
[0006] In an embodiment, the first valve plate has a first fixed end and a first sealing end which are oppositely arranged along the length direction of the first valve plate, and the second valve plate has a second fixed end and a second sealing end which are oppositely arranged along the length direction of the second valve plate. The first fixed end and the second fixed end are fixed on the valve seat by a connecting piece.
[0007] In an embodiment, the center of the first exhaust hole, the center of the second exhaust hole and the center of the connecting piece are located on the same straight line.
[0008] In an embodiment, the first valve plate has a first fixed end and a first sealing end oppositely arranged along the length direction of the first valve plate, and the second valve plate has a second fixed end and a second sealing end oppositely arranged along the length direction of the second valve plate. The valve seat is provided with a mounting groove, and the mounting groove is arranged in steps to have a first step groove and a second step groove spaced along the axial direction of the valve seat, and the size of the first step groove along the circumferential direction of the valve seat is greater than the size of the second step groove along the circumferential direction of the valve seat. The first fixed end and the second fixed end are respectively located in the first step groove and the second step groove.
[0009] In an embodiment, the valve plate assembly further comprises a second limiting piece located between the first valve plate and the second valve plate and arranged in the second step groove, and the distance between the bottom surface of the first step groove and the second limiting piece is not more than 0.05 mm.
[0010] In an embodiment, the valve plate assembly further comprises a first limiting piece and a second limiting piece, the length of the second limiting piece is less than that of the first limiting piece, the second limiting piece is located between the first valve plate and the second valve plate to limit the opening of the second valve plate, and the first limiting piece is located on the side of the first valve plate away from the second valve plate to limit the opening of the first valve plate.
[0011] In an embodiment, the part of the first limiting piece corresponding to the first exhaust hole is arranged in an inclined manner away from the first exhaust hole; and / or, The side surface of the second limiting piece is formed with a limiting inclined surface inclined away from the second exhaust hole; and / or, The length of the second limiting piece is less than the length of the second valve plate.
[0012] In an embodiment, the valve seat is provided with an exhaust groove communicating with the second exhaust hole, and the side wall of the exhaust groove away from the second exhaust hole is arranged in an arc surface, wherein: The ratio of the diameter of the circle on which the arc surface is located to the diameter of the second exhaust hole is 0.5-0.8; and / or, The included angle between the line connecting the center of the valve seat and the center of the second exhaust hole and the tangent of the arc apex of the arc surface is 51°±5°.
[0013] In an embodiment, the piston in the cylinder rotates eccentrically, and in the rotation direction of the piston, the second exhaust hole is located on the front side of the first exhaust hole.
[0014] In an embodiment, the sliding plate in the cylinder and the inner wall of the cylinder and the piston jointly divide to form an intake chamber and a compression chamber. With the center of the cylinder bore as the base point, the position of the second exhaust hole is 326°±10°.
[0015] In an embodiment, the second valve plate starts to close when the piston rotation angle reaches 315°±10°; and / or, The second exhaust hole communicates with the suction chamber when the piston rotation angle reaches 330°±10°.
[0016] The application further provides a refrigeration device comprising a rotary compressor, and the rotary compressor comprises a cylinder and a plurality of exhaust valve assemblies of the cylinder. The valve seat has a first exhaust hole and a second exhaust hole which are spaced apart and communicate with the cylinder, the first exhaust hole and the second exhaust hole both pass through the valve seat and are both used to communicate the compression chamber of the cylinder, and the second exhaust hole is arranged lower than the corresponding port of the first exhaust hole in the circumferential direction of the port of the cylinder. The valve plate assembly comprises a first valve plate and a second valve plate which are spaced apart in the axial direction of the valve seat, the second valve plate is used to open and close the second exhaust hole, the first valve plate covers the second valve plate and the first exhaust hole, the first valve plate is used to open and close the first exhaust hole, and the rigidity of the second valve plate is less than that of the first valve plate.
[0017] In the technical scheme of the application, the second exhaust hole is arranged lower than the corresponding port of the first exhaust hole in the circumferential direction of the port of the cylinder, so that the first valve plate can be arranged above the second valve plate, and the axial spacing between the two provides an opening space for the second valve plate. The first valve plate can independently open and close the first exhaust hole, and the second valve plate can independently open and close the second exhaust hole, thereby ensuring the air tightness of the exhaust port. The rigidity gradient of the first valve plate and the second valve plate is configured such that the rigidity of the second valve plate is less than that of the first valve plate, so that the first exhaust hole and the second exhaust hole can be opened and closed in stages during the eccentric rotation of the piston of the rotary compressor, i.e., the first exhaust hole and the second exhaust hole are opened at different times, thereby realizing the sequential closing of the first exhaust port and the second exhaust hole according to the timing of the rotor movement. The total exhaust area is increased, the over-compression loss is reduced, and the energy efficiency is improved. BRIEF DESCRIPTION OF DRAWINGS
[0018] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings needed to be used in the embodiments or prior art description. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can also be obtained according to the structures shown in these drawings without creative labor for those skilled in the art.
[0019] Figure 1Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 2 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 1 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 3 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 1 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 4 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 3 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 5 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 3 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 6 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application; Figure 3 Structure diagram of one embodiment (piston one rotation angle) of the rotary compressor provided by the present application.
[0020] Brief Description of the Drawings: 100, exhaust valve assembly; 1, valve seat; 11, first exhaust hole; 12, second exhaust hole; 13, mounting groove; 131, first step groove; 132, second step groove; 14, exhaust groove; 2, valve plate assembly; 21, first valve plate; 21a, first fixed end; 21b, first plugging end; 22, second valve plate; 22a, second fixed end; 22b, second plugging end; 23, first limiting piece; 24, second limiting piece; 200, piston.
[0021] The present application is achieved, the function characteristics and advantages will be further described with reference to the drawings. DETAILED DESCRIPTION
[0022] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.
[0023] It should be noted that if the present application involves a directional indication, the directional indication is only used to explain the relative position relationship, movement condition, etc. between the components in a certain posture, and if the certain posture changes, the directional indication also changes accordingly.
[0024] In addition, if the description of "first", "second" and the like is involved in the embodiments of the present application, the description of "first", "second" and the like is only for the purpose of description, and cannot be understood as indicating or implying the relative importance of the indicated technical features or implicitly indicating the number of the indicated technical features. Therefore, the features limited by "first", "second" can be explicitly or implicitly included at least one of the features. In addition, the technical solutions of various embodiments can be combined with each other, but it must be based on the realization of ordinary skilled in the art, when the combination of technical solutions appears contradictory or unachievable, it should be considered that the combination of technical solutions does not exist, nor in the protection scope required by the present application.
[0025] The existing single-cylinder or double-cylinder rolling rotor compressor runs at high speed (>120Hz), and the high-speed rotating speed causes the high-speed exhaust of the high-pressure refrigerant in the compression chamber. Due to the size limitation of the exhaust valve port, the compression chamber pressure is continuously higher than the exhaust valve external pressure during exhaust, resulting in significant exhaust over-compression loss.
[0026] The traditional solution of double-cylinder compressor is to add exhaust valve on the partition plate, but this will increase the double-cylinder span, aggravate the vibration and reduce the reliability. In addition, although the exhaust valve added on the partition plate increases the exhaust area and reduces the exhaust over-compression resistance to a certain extent, it has limited effect on higher speed (>160Hz).
[0027] In addition, in the prior art, multiple exhaust ports are combined with reed valves to adjust the opening area and bending strength of the exhaust port according to the change of working volume, but the single valve piece cannot simultaneously ensure the sealing of multiple exhaust ports, and it is difficult to adapt to the dynamic pressure change under high speed, and there are problems of response lag and energy loss.
[0028] In view of this, in order to solve the problem of insufficient exhaust area of traditional exhaust valve port, the present application increases an exhaust hole on the basis of the original exhaust valve seat in the rotary compressor, and separately designs a valve piece to seal it, which increases the exhaust area and has high reliability, significantly reduces the exhaust over-compression loss under high speed, and improves the energy efficiency.
[0029] Please refer to Figure 1 , Figures 3-4The rotary compressor comprises a cylinder and an exhaust valve assembly 100, the exhaust valve assembly 100 comprising a valve seat 1 and a valve plate assembly 2, the valve seat 1 having a first exhaust hole 11 and a second exhaust hole 12 arranged at intervals and communicated with the cylinder, the first exhaust hole 11 and the second exhaust hole 12 each penetrating the valve seat 1 and each used for communicating the compression chamber of the cylinder, the second exhaust hole 12 being arranged lower than the corresponding port circumference of the first exhaust hole 11; the valve plate assembly 2 comprising a first valve plate 21 and a second valve plate 22 arranged at intervals along the axial direction of the valve seat 1, the second valve plate 22 used for opening and closing the second exhaust hole 12, the first valve plate 21 covering the second valve plate 22 and the first exhaust hole 11, the first valve plate 21 used for opening and closing the first exhaust hole 11, the rigidity of the second valve plate 22 being smaller than that of the first valve plate 21.
[0030] In the technical scheme of the present application, the second exhaust hole 12 is arranged lower than the corresponding port circumference of the first exhaust hole 11, so that the first valve plate 21 can be arranged above the second valve plate 22, and the axial interval between the two provides an opening space for the second valve plate 22. The first valve plate 21 can independently open and close the first exhaust hole 11, and the second valve plate 22 can independently open and close the second exhaust hole 12, thereby ensuring the air tightness of the exhaust port. The rigidity gradient of the first valve plate 21 and the second valve plate 22 is configured so that the rigidity of the second valve plate 22 is smaller than that of the first valve plate 21, so that the first valve plate 21 and the second valve plate 22 can be opened and closed in stages during the eccentric rotation of the piston 200 of the rotary compressor, i.e., the first exhaust hole 11 and the second exhaust hole 12 are opened at different times, thereby realizing the sequential closing of the first exhaust port and the second exhaust hole 12 according to the timing of the rotor movement. The total exhaust area is increased, the over-compression loss is reduced, and the energy efficiency is improved.
[0031] It should be noted that if the second valve plate 22 is arranged above the first valve plate 21, and the first exhaust hole 11 and the second exhaust hole 12 are flush, the first exhaust hole 11 cannot be independently opened, the second valve plate 22 will be opened at the same time as the first valve plate 21 is opened, and the second valve plate 22 can only be closed after the first valve plate 21 is closed, so that the closing time of the second exhaust hole 12 will be delayed due to the late closing of the first exhaust hole 11, at this time the second exhaust hole 12 is communicated with the suction chamber and the exhaust chamber, and serious exhaust backflow will occur. Moreover, when the first valve plate 21 seals the first exhaust hole 11, it cannot simultaneously seal the second exhaust hole 12, otherwise the hyperstatic problem will occur, so that leakage will occur between the first valve plate 21 and the second exhaust hole 12 at non-exhaust times.
[0032] Please refer to Figures 1-2The cylinder is provided with a piston 200 and a sliding sheet. The piston 200 is eccentrically rotated in the cylinder and abuts against the inner wall of the cylinder. The sliding sheet is movably arranged in the cylinder and is used for abutting against the outer periphery of the piston 200. During the rotation of the piston 200, a crescent-shaped cavity is defined together with the cylinder. Based on the design of the sliding sheet, due to the cooperation of the sliding sheet and the piston 200, the sliding sheet divides the cylinder and the piston 200 to form an air suction cavity and a compression cavity. In the embodiment, the piston 200 is used for being connected with a crankshaft of the rotary compressor and is rotated under the driving of the crankshaft. When the piston 200 rotates away from the air inlet hole, the volume of the air suction cavity, which is in communication with the air inlet hole of the cylinder, continuously increases, and a negative pressure is generated. Under the action of the negative pressure, the gas continuously enters the air suction cavity to provide conditions for the next compression. The volume of the compression cavity on the other side continuously decreases and compresses the gas in the compression cavity. When the pressure in the compression cavity reaches a certain degree, the first valve sheet 21 and the second valve sheet 22 are driven to move away from the cylinder. When the piston 200 passes the air inlet hole of the cylinder again, a new round of compression is started.
[0033] Specifically, the rigidity difference between the first valve sheet 21 and the second valve sheet 22 can be realized by material difference, or by width, length, thickness and the like. In some embodiments, the thickness of the second valve sheet 22 is smaller than that of the first valve sheet 21, so that the rigidity of the second valve sheet 22 is smaller than that of the first valve sheet 21. During the eccentric rotation of the piston 200 of the rotary compressor, the relative positions of the piston 200 and the first air outlet hole 11 and the second air outlet hole 12 change, and the second valve sheet 22 and the first valve sheet 21 can be opened or closed based on the change of the internal and external pressure difference. In the case that the rigidity of the second valve sheet 22 is smaller, the pressure when the first valve sheet 21 is opened is greater than the pressure when the second valve sheet 22 is opened, so that the rotary compressor opens the second air outlet hole 12 through the second valve sheet 22 at a lower pressure, and different air outlet holes are opened at different pressures, so that the first valve sheet 21 and the second valve sheet 22 can be opened and closed in stages.
[0034] It should be noted that the order of opening and closing of the first valve sheet 21 and the second valve sheet 22 is determined by the positions of the two. The first valve sheet 21 can be set to be opened first, and the second valve sheet 22 can be set to be opened later. The second valve sheet 22 can be set to be opened first, and the first valve sheet 21 can be set to be opened later.
[0035] Specifically, the position of the second air outlet hole 12 needs to be close to the inner wall of the cylinder, and the second air outlet hole 12 has a certain distance from the inner wall of the cylinder.
[0036] It should be noted that the height difference of the ports of the first air outlet hole 11 and the second air outlet hole 12 can be realized by machining a sink groove on the plane where the first air outlet hole 11 is located, and machining the second air outlet hole 12 on the bottom wall of the sink groove.
[0037] In the exhaust process of the rotary compressor, the first exhaust hole 11 serves as the main exhaust function with a diameter of D1, and the second exhaust hole 12 serves as the auxiliary exhaust function with a diameter of D2. Considering the space limitation and the exhaust capacity requirement, in this embodiment, D2>0.6D1. Since the first exhaust hole 11 and the second exhaust hole 12 are located at different positions, the high-pressure gas in the rotary compressor can be discharged from the first exhaust hole 11 or the second exhaust hole 12 at different flow rates, thereby improving the exhaust efficiency and reducing the risk of backflow of the discharged gas.
[0038] The first valve plate 21 has a first fixed end 21a and a first sealing end 21b arranged opposite along the length direction thereof, and the second valve plate 22 has a second fixed end 22a and a second sealing end 22b arranged opposite along the length direction thereof. The deformation of the valve plate is based on the fixed end, so the part close to the fixed end has a shorter relative lifting distance, and the sealing end has a larger relative lifting distance.
[0039] The first sealing end 21b and the second sealing end 22b are both disc designs. The diameter of the second sealing end 22b is greater than the diameter of the second exhaust hole 12, and the difference between them is in the range of 0.5mm-1mm.
[0040] The first fixed end 21a and the second fixed end 22a are fixed on the valve seat 1 by the connecting piece. That is, the first valve plate 21 and the second valve plate 22 are integrally riveted, the structure is compact, and the two valve plates cooperatively reduce the over-compression loss and effectively improve the energy efficiency.
[0041] Further, the center of the first exhaust hole 11, the center of the second exhaust hole 12, and the center of the connecting piece are located on the same straight line. That is, the increase of the second exhaust hole 12 does not change the original arrangement of the single exhaust valve plate, the structure is compact, and the space occupied is small.
[0042] Please refer to Figure 4 , the valve seat 1 is provided with a mounting groove 13, which is arranged in steps to have a first step groove 131 and a second step groove 132 spaced along the axial direction of the valve seat 1, and the size of the first step groove 131 along the circumferential direction of the valve seat 1 is greater than the size of the second step groove 132 along the circumferential direction of the valve seat 1; the first fixed end 21a and the second fixed end 22a are located in the first step groove 131 and the second step groove 132, respectively. The design of the step groove facilitates the positioning and installation of the first valve plate 21 and the second valve plate 22.
[0043] Furthermore, please refer to Figures 4-5The valve plate assembly 2 also includes a first limiting member 23 and a second limiting member 24. The length of the second limiting member 24 is shorter than that of the first limiting member 23. The second limiting member 24 is located between the first valve plate 21 and the second valve plate 22, and is used to limit the opening degree of the second valve plate 22. The first limiting member 23 is located on the side of the first valve plate 21 facing away from the second valve plate 22, and is used to limit the opening degree of the first valve plate 21. The specific structural form of the first limiting member 23 and the second limiting member 24 is not limited, and they mainly function as limiters.
[0044] Correspondingly, the first limiting member 23 is disposed within the first stepped groove 131, and the second limiting member 24 is disposed within the second stepped groove 132. The distance between the bottom surface of the first stepped groove 131 and the second limiting member 24 does not exceed 0.05mm. That is, the upper end surface of the second limiting member 24 is flush with or within 0.05mm lower than the first stepped groove 131. If the height of the second limiting member 24 is too high, it will affect the installation and use of the first limiting member 23. Therefore, by limiting the distance between the bottom surface of the first stepped groove 131 and the end surface of the second limiting member 24, it is ensured that the first limiting member 23 and the second limiting member 24 will not interfere with each other during installation and engagement, so that both can be used normally.
[0045] It should be noted that, in actual installation, both the first valve plate 21 and the second valve plate 22 have a certain slope, that is, the upper edges of the first stepped groove 131 and the first exhaust hole 11 are not flush, and the upper edges of the second stepped groove 132 and the second exhaust hole 12 are not flush.
[0046] The portion of the first limiting member 23 corresponding to the first exhaust port 11 is inclined in the direction away from the first exhaust port 11; when the first valve plate 21 opens to fit with the inclined section of the first limiting member 23 under the action of pressure difference, the first valve plate 21 reaches the maximum opening angle.
[0047] The second limiting member 24 has a limiting slope that is inclined in the direction away from the second exhaust port 12 on the side facing the second valve plate 22. When the second valve plate 22 opens to fit against the limiting slope of the second limiting member 24 under the action of pressure difference, the second valve plate 22 reaches its maximum opening angle. Specifically, the end face of the second limiting member 24 facing away from the second valve plate 22 can be set as a plane, and the shape of the part of the second limiting member 24 corresponding to the second fixed end 22a can be the same.
[0048] In some embodiments, the length of the second limiting member 24 is less than the length of the second valve plate 22. The second limiting member 24 is used to limit the opening degree of the second valve plate 22. Based on the current space, if the dimensions of the second limiting member 24 and the first valve plate 21 are matched, it will have a thin wall, which is not conducive to processing and will lose its limiting effect. Therefore, limiting the length of the second limiting member 24 can avoid thin-wall processing. At the same time, the length of the second limiting member 24 affects the opening angle of the second valve plate 22. This design allows the second valve plate 22 to abut against the first valve plate 21 when it opens, thereby applying external force to the first valve plate 21. This helps the first valve plate 21 to open before the piston 200 reaches the corresponding rotation angle, increasing the exhaust volume.
[0049] Since the first valve plate 21 is located above the second valve plate 22, it obstructs the second exhaust port 12 to some extent. To ensure smooth exhaust from the second exhaust port 12, please refer to... Figure 6 The valve seat 1 is provided with an exhaust groove 14 that connects to the second exhaust hole 12. The gas exhausted from the second exhaust hole 12 first enters the exhaust groove 14 and then exhausts. By making at least a part of the exhaust groove 14 exposed to the first valve plate 21, the smooth exhaust of the second exhaust hole 12 is ensured.
[0050] The specific configuration of the exhaust groove 14 is determined based on the position of the first exhaust hole 11 and the width of the first valve plate 21. Specifically, the side wall of the exhaust groove 14 away from the second exhaust hole 12 is provided with an arc-shaped surface. In one embodiment, the ratio of the diameter of the circumference of the arc-shaped surface to the diameter of the second exhaust hole 12 is 0.5 to 0.8. Specifically, in this embodiment, the ratio of the diameter of the circumference of the arc-shaped surface to the diameter of the second exhaust hole 12 is set to 2 / 3. It should be noted that the center of the circumference of the arc-shaped surface does not coincide with the center of the second exhaust hole 12. By limiting the diameters of both, the size of the arc-shaped protrusion of the exhaust groove 14 can be limited, thus satisfying the auxiliary exhaust function without wasting space.
[0051] The angle between the line connecting the center of valve seat 1 and the center of the second exhaust port 12 and the tangent to the apex of the arc surface is 51°±5°. The overall orientation of the exhaust groove 14 is defined by the angle design, and the apex of the arc surface 14 is staggered from the line connecting the first exhaust port 11 and the second exhaust port 12.
[0052] It should be noted that the first exhaust port 11 is also provided with an arc-shaped mating groove to assist in exhaust. The mating groove can be designed according to conventional methods. It is necessary to ensure that the mating groove and the exhaust groove 14 are offset in the radial direction and that their orientations are different.
[0053] In addition, a first boss is provided around the first exhaust hole 11, which abuts against the first sealing end 21b. A second boss is provided around the second exhaust hole 12, which abuts against the second sealing end 22b. On the one hand, this can compress the effective contact area of the first valve plate 21 and the second valve plate 22 during operation, reduce the amount of processing, and thus reduce manufacturing costs; on the other hand, it can also improve the sealing effect.
[0054] In the rotation direction of piston 200, the second exhaust port 12 is located in front of the first exhaust port 11. That is, during the eccentric rotation of piston 200, it first passes through the second exhaust port 12 and then through the first exhaust port 11. Thus, the sequential closing of the two exhaust ports is achieved by utilizing the rotor motion sequence.
[0055] Please refer to Figures 1-2 With the center of the cylinder cavity as the base point and the position of the sliding vane at 0°, the position of the second exhaust port 12 in a clockwise direction is 326°±10°. This angle refers to the angle formed by the line connecting the center of the second exhaust port 12 and the center of the cylinder, and the line connecting the center of the sliding vane and the center of the cylinder. The position of the second exhaust port 12 can be 316°, 320°, or 336°. Through the design of the relative positions of the first exhaust port 11 and the second exhaust port 12 in this embodiment, it can cooperate with the piston 200 to limit the opening and closing of the second exhaust port 12 at a specific rotation angle.
[0056] Specifically, the position of the first exhaust port 11130a can be 345°±10°.
[0057] The piston 200 completes one compression process by rotating 360° clockwise from the position of the sliding plate. The first valve plate 21 and the second valve plate 22 automatically open and close according to the changes in the compression state during the rotation of the piston 200.
[0058] Please refer to Figure 1 When the piston 200 rotates to an angle of 315°±10°, corresponding to the angle between centerline a and centerline b, the second valve plate 22 begins to close. This means the second valve plate 22 does not yet completely cover the second exhaust port 12. When the piston 200 rotates to the corresponding angle, it will cover the second exhaust port 12. The change in internal and external pressure difference on the second valve plate 22 causes it to fall freely under its own stiffness, thus automatically closing the second exhaust port 12. The angle at which the second exhaust port 12 is completely closed is when the piston 200 rotates to an angle of 327°±10°, which is approximately the design period angle of the bearing.
[0059] For the first exhaust port 11 and the second exhaust port 12 to function properly, the opening and closing timing of the first valve plate 21 and the second valve plate 22 needs to be controlled. The intake port of the cylinder connected to the intake chamber, and the rotation of the piston 200, will cause changes in the position and volume of the compression chamber and the intake chamber. Please refer to... Figure 2 When piston 200 rotates to an angle of 330°±10°, the angle between centerline a and centerline b corresponds to... Figure 2 and Figure 1 In contrast, the position of centerline b changes, and the second exhaust port 12 connects with the intake chamber. Thus, even if the second valve plate 22 is not currently closed, based on the connection between the second exhaust port 12 and the intake chamber, the second valve plate 22 accelerates its descent under the pressure difference. This controls the working time of the second exhaust port 12.
[0060] Moreover, the diameter of the small exhaust port is smaller than the thickness of the piston 200 inside the cylinder.
[0061] It should be noted that in the attached diagram, R1 corresponds to the radius of the cylinder's inner cavity, R2 corresponds to the outer diameter of piston 200, and R3 corresponds to the inner diameter of piston 200.
[0062] In the technical solution of this invention, a dual-valve collaborative design is adopted. A small exhaust valve space is machined on the front side of the original large exhaust valve seat 1 platform to form a dual-valve structure with large and small valves. The large and small valve plates open or close independently to ensure the airtightness of the exhaust port. The limiter is fixed by a single rivet to ensure a compact structure. The thickness of the second valve plate 22 is smaller than that of the first valve plate 21, and its width and length are optimized. Staged opening and closing are achieved through the difference in stiffness. The sequential closing of the large and small exhaust ports is achieved by utilizing the rotor movement sequence. The limiter is integrated with a riveted design, resulting in a compact structure. The dual-valve collaboration reduces over-compression losses and effectively improves energy efficiency.
[0063] The present invention also proposes a refrigeration device, which includes a rotary compressor. The specific structure of the rotary compressor is as described in the above embodiments. Since all the technical solutions of the above embodiments are adopted, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.
[0064] The above are merely preferred embodiments of the present invention and do not limit the scope of the patent. Any equivalent structural transformations made using the contents of the specification and drawings of the present invention under the inventive concept of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of patent protection of the present invention.
Claims
1. A rotary compressor, comprising a cylinder and an exhaust valve assembly (100), characterized in that, The exhaust valve assembly includes: The valve seat has a first exhaust port and a second exhaust port that are spaced apart and connected to the cylinder. Both the first exhaust port and the second exhaust port pass through the valve seat. The periphery of the port of the second exhaust port facing away from the cylinder is lower than the periphery of the port corresponding to the first exhaust port. The valve assembly includes a first valve plate and a second valve plate spaced axially along the valve seat. The second valve plate is used to open and close a second vent hole. The first valve plate covers the second valve plate and the first vent hole. The first valve plate is used to open and close the first vent hole. The stiffness of the second valve plate is less than that of the first valve plate.
2. The rotary compressor as described in claim 1, characterized in that, The thickness of the second valve plate is less than the thickness of the first valve plate; and / or, The diameter of the second vent is D2, and the diameter of the first vent is D1, wherein D2 > 0.6D1.
3. The rotary compressor as described in claim 1, characterized in that, The first valve plate has a first fixed end and a first blocking end disposed opposite to each other along its length direction, and the second valve plate has a second fixed end and a second blocking end disposed opposite to each other along its length direction; The first fixed end and the second fixed end are fixed to the valve seat by a connector.
4. The rotary compressor as described in claim 3, characterized in that, The centers of the first vent, the second vent, and the connector are on the same straight line.
5. The rotary compressor as described in claim 1, characterized in that, The first valve plate has a first fixed end and a first blocking end disposed opposite to each other along its length direction, and the second valve plate has a second fixed end and a second blocking end disposed opposite to each other along its length direction; The valve seat is provided with a mounting groove, which is stepped and has a first stepped groove and a second stepped groove spaced apart along the axial direction of the valve seat. The first stepped groove is larger in the circumferential direction of the valve seat than the second stepped groove is in the circumferential direction of the valve seat. The first fixed end and the second fixed end are located in the first step groove and the second step groove, respectively.
6. The rotary compressor as described in claim 5, characterized in that, The valve plate assembly further includes a second limiting member located between the first valve plate and the second valve plate, and disposed within the second stepped groove, wherein the distance between the bottom surface of the first stepped groove and the second limiting member does not exceed 0.05 mm.
7. The rotary compressor as described in claim 1, characterized in that, The valve plate assembly further includes a first limiting member and a second limiting member. The length of the second limiting member is less than that of the first limiting member. The second limiting member is located between the first valve plate and the second valve plate and is used to limit the opening degree of the second valve plate. The first limiting member is located on the side of the first valve plate facing away from the second valve plate and is used to limit the opening degree of the first valve plate.
8. The rotary compressor as described in claim 7, characterized in that, The portion of the first limiting member corresponding to the first exhaust port is inclined in a direction away from the first exhaust port; and / or, The second limiting member has a limiting slope that is inclined in the direction away from the second exhaust port on its side facing the second valve plate; and / or, The length of the second limiting member is less than the length of the second valve plate.
9. The rotary compressor as described in claim 1, characterized in that, The valve seat is provided with an exhaust groove communicating with the second exhaust port, and the side wall of the exhaust groove away from the second exhaust port is provided with an arc-shaped surface, wherein: The ratio of the diameter of the circumference containing the arc-shaped surface to the diameter of the second exhaust hole is 0.5 to 0.8; and / or, The angle between the line connecting the center of the valve seat and the center of the second exhaust hole and the tangent at the apex of the arc surface is 51°±5°.
10. The rotary compressor as claimed in claim 1, characterized in that, The piston inside the cylinder rotates eccentrically, and in the direction of piston rotation, the second exhaust port is located in front of the first exhaust port.
11. The rotary compressor according to claim 10, characterized in that, The sliding vane inside the cylinder, together with the inner wall of the cylinder and the piston, forms an intake chamber and a compression chamber. With the center of the cylinder cavity as the base point and the position of the sliding vane at 0°, the position of the second exhaust port is 326°±10°.
12. The rotary compressor according to claim 11, characterized in that, When the piston rotates to an angle of 315°±10°, the second valve plate begins to close; and / or, When the piston rotates to an angle of 330°±10°, the second exhaust port communicates with the intake chamber.
13. A refrigeration device, characterized in that, Including the rotary compressor as described in any one of claims 1 to 12.