阅读说明：本技术 阀片限位器、阀组件、压缩机及制冷装置 (Valve plate limiter, valve component, compressor and refrigerating device ) 是由 杜文清 张添 黎美銮 于 2021-08-20 设计创作，主要内容包括：本发明涉及一种阀片限位器、阀组件、压缩机及制冷装置,阀片限位器包括固定结构、限位结构和支撑结构,固定结构呈环形,用于压接固定阀片；限位结构用于限定阀片的开启高度；支撑结构的两端分别连接固定结构和限位结构,并使得固定结构和限位结构以上述开启高度间隔设置。根据本发明实施例的阀片限位器,至少具有如下有益效果：通过将固定结构设置为环形,以压接固定阀片,增大阀片的被固定区域,从而使得阀片的固定更为稳固,同时,受力面的增大,能够减少固定位置的应力集中,从而延长了阀片的使用寿命；此外,设置有限位结构用于限定阀片的开启高度,从而使得阀片的开启高度可以控制,能更为有效的控制阀片的开启和关闭的时间。(The invention relates to a valve plate limiter, a valve component, a compressor and a refrigerating device, wherein the valve plate limiter comprises a fixing structure, a limiting structure and a supporting structure, wherein the fixing structure is annular and is used for pressing and fixing a valve plate; the limiting structure is used for limiting the opening height of the valve plate; the two ends of the supporting structure are respectively connected with the fixing structure and the limiting structure, and the fixing structure and the limiting structure are arranged at the opening height interval. The valve plate limiter provided by the embodiment of the invention at least has the following beneficial effects: the fixing structure is arranged to be annular, so that the valve plate is fixed in a compression joint mode, the fixed area of the valve plate is enlarged, the valve plate is fixed more stably, meanwhile, the stress concentration of the fixed position can be reduced due to the enlargement of the stress surface, and the service life of the valve plate is prolonged; in addition, be provided with limit structure and be used for injecing the opening height of valve block to make opening height of valve block can control, the time of opening and closing of more effectual control valve block of ability.)

1. A valve plate retainer, comprising:

the fixing structure is annular and is used for pressing and connecting the fixed valve plate;

the limiting structure is used for limiting the opening height of the valve plate;

and the two ends of the supporting structure are respectively connected with the fixed structure and the limiting structure, so that the bottom end surface of the limiting structure and the bottom end surface of the fixed structure have the opening height.

So that the fixing structure and the limiting structure are arranged at intervals of the opening height.

2. The valve retainer of claim 1, wherein the retainer structure comprises:

the limiting head is positioned in the ring shape along the axial projection of the fixing structure;

one end of the cantilever is connected with the limiting head, and the other end of the cantilever is connected with the supporting structure.

3. The valve plate retainer of claim 2, wherein the retainer head has a through hole or the bottom end surface of the retainer head has a groove.

4. The valve retainer of claim 2, wherein the bottom end surface of the retainer head is parallel to the bottom end surface of the fixed structure.

5. The valve retainer of claim 1, further comprising a mounting structure for securing the valve retainer.

6. The valve retainer of claim 4, wherein the mounting structure is coupled to the support structure and projects from the support structure in a direction away from the fixed structure, and a bottom end surface of the mounting structure is parallel to a bottom end surface of the fixed structure.

7. The valve retainer of claim 5, wherein the mounting structure is provided with a coupling hole having a central axis parallel to a central axis of the fixed structure.

8. A valve assembly disposed in a discharge passage of a compressor, comprising:

a valve seat having an exhaust hole communicating with the exhaust passage;

the valve plate comprises a fixing part and an openable head part connected with the fixing part, and the head part covers the exhaust hole;

the valve plate retainer of any one of claims 1 to 7, wherein the fixing structure is pressed on the fixing portion, and the limiting structure is used for limiting the opening height of the head portion.

9. The valve assembly of claim 8, wherein the retainer portion is annular and disposed around the head portion; at least one valve arm is disposed between the fixed portion and the head portion.

10. The valve assembly of claim 9, wherein the valve arms are uniformly arranged in a plurality along a circumferential direction of the head portion, and each valve arm extends in an involute shape around the head portion.

11. The valve assembly of claim 9, wherein the bottom end surface of the fixed structure is provided with at least one notch, the position of the notch corresponding to the position of the valve arm.

12. A valve assembly according to any one of claims 8 to 11, wherein the bore diameter of the bleed orifice is D and the opening height of the head is H such that:

13. a compressor, comprising:

a compressor body having a discharge passage;

a valve assembly according to any one of claims 8 to 12 disposed in the exhaust passage.

14. A refrigeration apparatus comprising the compressor of claim 13.

Technical Field

The invention belongs to the technical field of refrigeration equipment, and particularly relates to a valve plate limiter, a valve component, a compressor and a refrigeration device.

Background

The exhaust assembly of the existing compressor, especially the rotary compressor, mainly comprises a reed valve, and a valve plate of the reed valve has the advantages of simple structure, high reliability and the like. The valve block of reed valve need be fixed on the disk seat, then utilize the elasticity degree deformation of valve block self in order to open the exhaust hole to utilize the rigidity of self to resume in order to close the exhaust hole, among the traditional art, adopt the screw to fix the valve block more, can lead to the valve block to become flexible easily, the time of opening and closing of valve block is difficult to control scheduling problem, and shortened the life of valve block.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides the valve plate limiter which can stably fix the valve plate, effectively control the opening and closing time of the valve plate and prolong the service life of the valve plate.

Meanwhile, the invention also provides a valve component with the valve plate limiter, a compressor with the valve component and a refrigerating device with the compressor.

The valve plate limiter comprises a fixing structure, a limiting structure and a supporting structure, wherein the fixing structure is annular and is used for pressing and connecting a fixed valve plate; the limiting structure is used for limiting the opening height of the valve plate; the two ends of the supporting structure are respectively connected with the fixing structure and the limiting structure, so that the bottom end face of the limiting structure and the bottom end face of the fixing structure are provided with the opening height.

The valve plate limiter provided by the embodiment of the invention at least has the following beneficial effects: the fixing structure is arranged to be annular, so that the valve plate is fixed in a compression joint mode, the fixed area of the valve plate is enlarged, the valve plate is fixed more stably, meanwhile, the stress concentration of the fixed position can be reduced due to the enlargement of the stress surface, and the service life of the valve plate is prolonged; in addition, be provided with limit structure and be used for injecing the opening height of valve block to make opening height of valve block can control, the time of opening and closing of more effectual control valve block of ability.

According to some embodiments of the invention, the retaining structure comprises a retaining head and a cantilever, the projection of the retaining head along the axial direction of the fixed structure being located within the annulus; one end of the cantilever is connected with the limiting head, and the other end of the cantilever is connected with the supporting structure.

According to some embodiments of the invention, the stopper has a through hole or the bottom end face of the stopper has a groove.

According to some embodiments of the invention, a bottom end surface of the stopper is parallel to a bottom end surface of the fixing structure.

According to some embodiments of the invention, the valve retainer further comprises a mounting structure for securing the valve retainer.

According to some embodiments of the invention, the mounting structure is connected to the support structure and projects therefrom in a direction away from the fixed structure, a bottom end face of the mounting structure being parallel to a bottom end face of the fixed structure.

According to some embodiments of the invention, the mounting structure is provided with a connection hole, a central axis of the connection hole being parallel to a central axis of the fixing structure.

The valve assembly according to the second aspect of the present invention is disposed in a discharge passage of a compressor, and includes a valve seat, a valve plate, and the valve plate stopper according to the first aspect of the present invention, the valve seat having a discharge hole; the valve plate covers the exhaust hole and comprises a fixing part and an openable head part connected with the fixing part; the fixing structure is pressed on the fixing part, and the limiting structure is used for controlling the opening height of the head.

The valve assembly according to the embodiment of the invention has at least the following advantages: in the valve component, the fixing structure is arranged to be annular, so that the valve plate is fixed in a compression joint mode, the fixed area of the valve plate is enlarged, the valve plate is fixed more stably, meanwhile, the stress concentration of the fixed position can be reduced due to the fact that the stress surface is enlarged, and the service life of the valve plate is prolonged; in addition, be provided with limit structure and be used for injecing the height of opening of valve block to make the height of opening of valve block can control, the time of opening and closing of more effectual control valve block of ability is favorable to promoting valve module's performance.

According to some embodiments of the invention, the anchoring portion is annular and disposed around the head portion; at least one valve arm is disposed between the fixed portion and the head portion.

According to some embodiments of the invention, the valve arms are uniformly arranged in a plurality along a circumferential direction of the head portion, and each valve arm extends around the head portion in an involute shape.

According to some embodiments of the invention, the bottom end face of the fixation structure is provided with at least one indentation, the position of the indentation corresponding to the position of the valve arm.

According to some embodiments of the invention, the aperture of the vent hole covered by the valve plate is D, the opening height of the head is H, and the following requirements are met:

a compressor according to an embodiment of a third aspect of the present invention, comprising a compressor body having a discharge passage and a valve assembly according to an embodiment of the second aspect of the present invention; the valve assembly is disposed in the exhaust passage.

The compressor provided by the embodiment of the invention has at least the following beneficial effects: because the valve plate in the valve component is more firmly fixed, the service life of the valve plate is prolonged, and the opening and closing time of the valve plate is effectively controlled, so that the energy efficiency of the compressor is improved.

A refrigeration device according to an embodiment of the fourth aspect of the present invention includes the compressor according to the embodiment of the third aspect of the present invention.

The refrigeration device provided by the embodiment of the invention has at least the following beneficial effects: by adopting the compressor of the embodiment of the third aspect of the invention, the working efficiency of the refrigerating device can be improved, the service life of the refrigerating device can be prolonged, and the satisfaction of users can be improved.

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

Drawings

The invention is further described with reference to the following figures and examples, in which:

FIG. 1 is a top view of a dual-arm valve plate in a closed position according to some embodiments of the present invention;

FIG. 2 is a top view of a dual arm valve plate in a closed position according to some embodiments of the present invention;

FIG. 3 is a schematic perspective view of the dual-arm valve plate shown in FIG. 2 in an open state;

FIG. 4 is a top view of a valve plate of a triple valve arm according to some embodiments of the present invention in a closed position;

FIG. 5 is a schematic perspective view of the valve plate of the triple valve arm shown in FIG. 4 in an open state;

FIG. 6 is a schematic perspective view of a valve plate retainer according to some embodiments of the present invention;

FIG. 7 is a cross-sectional view of the valve retainer of FIG. 6;

FIG. 8 is a schematic perspective view of a mounting flange (with valve assembly) of a compressor according to some embodiments of the present invention;

FIG. 9 is a perspective view of a valve plate retainer (without fasteners) according to some embodiments of the present invention;

FIG. 10 is a perspective view of a valve plate retainer (with fasteners) according to some embodiments of the present invention;

FIG. 11 is a cross-sectional view of the valve retainer of FIG. 10;

FIG. 12 is a schematic perspective view of a mounting flange (with valve assembly) of a compressor according to some embodiments of the present invention;

fig. 13 is a cross-sectional view of the mounting flange (with valve assembly) shown in fig. 12.

FIG. 14 is a graph of coefficient of performance versus valve lift for a compressor in accordance with certain embodiments of the present invention;

fig. 15 is a schematic perspective view of a valve plate stopper (with a notch) according to some embodiments of the invention.

Reference numerals:

a valve sheet 100, a head 101, a fixing portion 102, and a valve arm 103;

a stress concentrating hole 201;

valve plate limiter 600, fixing structure 601, limiting head 602, cantilever 603, through hole 604 and support structure 605;

mounting flange 800 and mounting groove 801;

mounting structure 901, connection hole 902;

a fastener 1001;

notch 1501.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

In the description of the present invention, it is to be understood that the positional descriptions, such as the top, bottom, inner, outer, etc., referred to herein are based on the positional or positional relationships shown in the drawings, which are for convenience in describing the present invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and is therefore not to be construed as limiting the present invention.

In the description of the present invention, if there are first and second described only for the purpose of distinguishing technical features, it is not understood that relative importance is indicated or implied or that the number of indicated technical features or the precedence of the indicated technical features is implicitly indicated or implied.

In the description of the present invention, unless otherwise expressly limited, the terms set, mounted, connected, assembled, located, and the like are to be construed broadly, and those skilled in the art can reasonably determine the specific meaning of the terms in the present invention by combining the detailed contents of the technical solutions.

The compressor is a driven fluid machine that raises low-pressure gas into high-pressure gas, and is the heart of a refrigeration apparatus. The refrigerating cycle power supply device sucks low-temperature and low-pressure refrigerant gas from the air suction channel, drives the piston to compress the refrigerant gas through the operation of the motor, and discharges high-temperature and high-pressure refrigerant gas to the exhaust channel to provide power for the refrigerating cycle.

The exhaust assembly of the existing compressor, especially the rotary compressor, mainly uses the reed valve as a main part, the reed valve is a form of an air valve, the valve plate is made of elastic thin steel sheet, one end of the valve plate is fixed on the valve seat, and the other end is free. The valve plate is a flexible opening and closing element, so that the valve plate has elasticity, and a spring can not be additionally arranged, so that the reed valve has the characteristics of simple structure, light movement mass and small residual system volume.

In order to optimize the performance of the valve plate lifting compressor, the valve plate lifting compressor can be improved by reducing the clearance volume of the valve seat and reducing the exhaust resistance loss.

The valve block of reed valve need be fixed on the disk seat, then utilize the elasticity degree deformation of valve block self in order to open the exhaust hole to utilize the rigidity of self to resume in order to close the exhaust hole, in the conventional art, adopt the screw fixed valve block more, can lead to the valve block to become flexible easily, the time of opening and closing of valve block is difficult to control, and reduces the life's of valve block problem.

To this end, embodiments of the present invention will be described in detail with reference to fig. 1 to 15.

Referring to fig. 6 and 7, which partially illustrate a valve plate retainer 600 according to an embodiment of the first aspect of the present invention, the valve plate retainer 600 includes a fixing structure 601, a retaining structure, and a supporting structure 605, where the fixing structure 601 is annular to crimp and fix the valve plate 100; the limiting structure is used for limiting the opening height of the valve plate 100; the two ends of the supporting structure 605 are respectively connected to the fixing structure 601 and the limiting structure, so that the fixing structure 601 and the limiting structure are disposed at the above-mentioned opening height interval along the axial direction of the fixing structure 601, in other words, so that the bottom end surface of the limiting structure and the bottom end surface of the fixing structure 601 have the above-mentioned opening height.

It should be noted that the fixing structure 601 is annular, and may include a circular ring shape or a shape similar to a circular ring.

It should be noted that the valve sheet 100 may be any valve sheet 100, such as the valve sheet 100 of a reed valve commonly used in a rotary compressor, and the annular fixing structure 601 is used to press the edge of the valve sheet 100 for fixing.

According to the valve plate stopper 600 provided by the embodiment of the invention, the fixing structure 601 is arranged in an annular shape to press and fix the valve plate 100, so that the fixed area of the valve plate 100 can be increased, the valve plate 100 can be fixed more stably, meanwhile, the stress concentration of the fixed position can be reduced due to the increase of the stress bearing surface, and the service life of the valve plate 100 is prolonged; in addition, the limiting structure is arranged for limiting the opening height of the valve plate 100, so that the opening height of the valve plate 100 can be controlled, and the opening and closing time of the valve plate 100 can be controlled more effectively.

It should be noted that, referring to fig. 6 and 7, the limiting structure includes a limiting head 602 and a cantilever 603, and a projection of the limiting head 602 on the fixed structure 601 is located in the ring; cantilever 603 is connected to a spacing head 602 at one end and to a support structure 605 at the other end.

It should be noted that, as the valve sheet 100, the movable portion (e.g., the head 101 shown in fig. 3 and 5) is disposed in the annular region defined by the annular fixing structure 601 to open or close the exhaust hole, and the projection of the limiting head 602 on the fixing structure 601 is located in the annular region, so that the opening height of the movable portion can be limited.

Compared with the conventional valve assembly, the valve assembly mainly utilizes the self-rigidity recovery to close the exhaust hole, and therefore, the opening height is different each time, which results in that the opening and closing time of the valve sheet 100 is not easy to control. The limiting head 602 of the valve plate limiter 600 in the embodiment of the present invention is used to limit the opening height of the valve plate 100.

In some embodiments, referring to fig. 6 and 9, the through hole 604 is formed on the limiting head 602, so that the limiting head 602 forms an annular structure, and thus when the bottom end surface of the limiting structure contacts the head 101, the viscous force of the oil can be reduced, the falling of the head 101 is accelerated, and the backflow loss is avoided.

It is understood that the through hole 604 can be replaced by a groove disposed on the bottom end surface of the stopper 602, and the viscous force of the oil can be reduced and the return loss can be reduced when the bottom end surface of the stopper contacts the head 101.

It should be noted that, in some embodiments, as shown in fig. 7 and 11, the bottom end surface of the position limiting head 602 is parallel to the bottom end surface of the fixing structure 601.

It should be noted that the parallel in the present application does not necessarily have to be perfectly parallel, and may have an acceptable degree of parallelism within a visual range of the naked eye, which is related to a specific use effect.

Through the arrangement, the movable part (such as the head part 101 shown in fig. 3 and 5) of the valve plate 100 can be stably contacted with the bottom end face of the limiting head 602, so that the movable part is prevented from deforming due to poor contact, and the service life of the valve plate 100 can be prolonged.

In some embodiments, referring to fig. 9 and 10, valve retainer 600 further includes a mounting structure 901, where mounting structure 901 is used to secure valve retainer 600.

It should be noted that, in some cases, a special mounting structure 901, such as the valve plate stopper 600 shown in fig. 6, may not be provided, and when mounting, it may be directly mounted in the mounting groove 801 of the mounting flange 800 in an interference fit manner, so that the mounting may be facilitated, and the overall strength of the mounting flange 800 may be improved.

In some embodiments, referring to fig. 9 and 10, the mounting structure 901 is specifically configured to: is connected to the support structure 605 and projects from the support structure 605 in a direction away from the fixed structure 601.

It will be appreciated that the mounting structure 901 can be secured to the mounting flange 800 by having the mounting structure 901 project from the support structure 605 in a direction away from the securing structure 601.

It should be noted that, referring to fig. 11, the bottom end surface of the mounting structure 901 is parallel to the bottom end surface of the fixing structure 601, so that the bottom end surface of the fixing structure 601 can be better crimped to fix the valve sheet 100, and unnecessary displacement of the valve sheet 100 is avoided.

Referring to fig. 11, mounting structure 901 is provided with a connecting hole 902, and valve plate stopper 600 can be fixed to mounting flange 800 through connecting hole 902 by using fastener 1001.

It is understood that fixing holes corresponding to the connecting holes 902 are provided at the top circumference of the mounting groove 801 at the mounting flange 800.

It can be further understood that, referring to fig. 11, the central axis of the connection hole 902 is parallel to the central axis of the fixing structure 601, so that the bottom end surface of the fixing structure 601 can be better pressed against the fixed valve sheet 100, and the valve sheet 100 is prevented from being unnecessarily displaced.

According to some embodiments of the second aspect of the present invention, the valve assembly is disposed in a discharge passage of a compressor, and includes a valve seat, a valve plate stopper 600 of the first aspect of the present invention, and a valve plate 100.

Specifically, referring to fig. 6-8, the valve seat has a vent hole communicating with the vent passage. It will be appreciated that the valve seat may be a mounting flange 800, with the mounting flange 800 being disposed within the compressor.

In some embodiments, referring to fig. 1, the valve sheet 100 may include a fixing portion 102 and an openable head portion 101 connected to the fixing portion 102, the head portion 101 covering the exhaust hole; the fixing structure 601 of the valve plate stopper 600 is pressed on the fixing portion 102, and the limiting structure can limit the opening height of the head 101.

Specifically, referring to fig. 1 to 3, the valve sheet 100 may include a head portion 101, a fixing portion 102, and two valve arms 103. The head 101 is positioned at the geometric center of the valve plate 100, and the fixing part 102 is annular and arranged around the head 101; the two valve arms 103 are uniformly arranged between the head part 101 and the fixing part 102 along the circumferential direction of the head part 101, the two ends of each valve arm 103 are respectively connected with the head part 101 and the fixing part 102, and the valve arms 103 are arranged around the head part 101 in an involute shape.

It can be understood that the valve plate 100 is disposed on a valve seat of the compressor, the valve seat is located in a discharge passage of the compressor, wherein, when the compressor is in a suction state, the head 101 is used for closing a discharge hole (refer to fig. 1 and 2), and when the compressor is in a discharge state, the head 101 opens the discharge hole (refer to fig. 3), and gas is discharged out of the compressor through a gap between the discharge hole and the head 101. When the exhaust is finished, the head part 101 closes the exhaust hole again under the elastic restoring force of the valve arm 103 to cover and close the exhaust hole.

It will also be appreciated that the location of the head 101 at the geometric center of the valve plate 100 ensures that the force applied to the valve arm 103 is uniform during the opening and closing movement of the head 101, thereby avoiding the head 101 failing to close the vent, resulting in backflow losses.

It should be noted that the number of the valve arms 103 is not limited to two, and may be one or more than two, for example, three (described in detail below), four, five or more.

It can be understood that when the number of the valve arms 103 is less, the flow resistance loss of the valve sheet 100 can be reduced, but at the same time, the rigidity of the valve arms 103 is too small, so that the valve arms are not closed timely, the backflow loss is increased, and the overall performance of the compressor is reduced.

When the number of the valve arms 103 is too large, the head 101 can be closed in time, so that the backflow loss is reduced, but the flow resistance loss of the valve sheet 100 is increased, and the overall performance of the compressor is also reduced.

In some embodiments of the invention, the number of valve arms 103 is selected to be 2-4 to balance flow resistance losses and return losses.

In some embodiments, referring to fig. 4 to 5, the number of the valve arms 103 is 3, and by setting to 3, the flow resistance loss and the backflow loss can be balanced, so that the response rate of the valve sheet 100 is increased, the head 101 can be rapidly opened and closed, and the usability of the compressor can be improved.

It should be further noted that the involute is a mathematical concept defined as: the distance from a point to the center of a circle is proportional to the angle between the point and the connecting line of the origin.

Specifically, a round shaft is fixed on a plane, a thread is wound on the shaft, a thread head is tensioned, the thread moves around the round shaft and is always tangent to the round shaft, and then the track of a fixed point on the thread on the plane is an involute.

By setting the valve arm 103 to be in an involute shape, the uniformity of the force applied to the valve arm 103 when the valve arm 103 deforms along the opening direction of the head 101 can be ensured, and the radial connection rigidity of the head 101 of the poppet valve 100 and the fixing portion 102 can be ensured while the length of the valve arm 103 is ensured, so that the response rate of the valve plate 100 is improved, and rapid opening and closing can be realized.

In addition, the involute shape is adopted, stress concentration of the valve arm 103 can be avoided due to uniform stress, so that the fatigue resistance of the valve arm 103 is improved, and the service life of the valve plate 100 is prolonged.

As shown in fig. 1, 2, and 4, the valve arm 103 has the same width in the extending direction of the valve arm 103, that is, the width is kept constant, so that the uniformity of the force applied when the valve arm 103 deforms along the opening direction of the head 101 can be ensured, and the stress concentration of the valve arm 103 can be avoided due to the uniform force applied, thereby improving the fatigue resistance of the valve arm 103 and prolonging the service life of the valve plate 100.

It should be noted that, in the extending direction of the valve arms 103, the widths of the gaps between the adjacent valve arms 103 are equal, that is, constant, so that the valve arms 103 can be easily machined, and the widths of the machined valve arms 103 can be kept constant.

In some embodiments, the pivot angle of the valve arm 103 is 180 to 720 degrees.

Referring to fig. 2, the rotation angle of the valve arm 103 exceeds 360 degrees, and referring to fig. 4, the rotation angle of the valve arm 103 is close to 360 degrees, and the rotation angle of the valve arm 103 is 180 to 720 degrees, so that the length of the valve arm 103 can be increased, the valve arm 103 has a sufficient deformation amount along the opening direction of the head 101, the rigidity of the valve arm 103 is reduced, and the rigidity of the valve arm 103 is not too small, so that the deformation capability and rigidity of the valve arm 103 can be well balanced, and the flow resistance loss and the return loss can be balanced.

In some embodiments, the junction of the valve arm 103 and the head 101, and the junction of the valve arm 103 and the fixation portion 102, are provided with a transition structure. By providing the transition structure, stress concentration at the joint of the valve arm 103 and the head 101 and at the joint of the valve arm 103 and the fixing portion 102 can be reduced, thereby affecting the service life of the valve sheet 100.

It will be appreciated that a transition structure may be provided only at the connection of the valve arm 103 with the head 101 or only at the connection of the valve arm 103 with the fixing portion 102, as desired.

As shown by comparing fig. 1 and fig. 2, in fig. 1, the transition structures are not provided at the connection of the valve arm 103 and the head portion 101 and at the connection of the valve arm 103 and the fixing portion 102, whereas in fig. 2, the transition structures are provided at the connection of the valve arm 103 and the head portion 101 and at the connection of the valve arm 103 and the fixing portion 102.

In some embodiments, the transition structure may be provided with a chamfer, such as a fillet, to reduce stress concentrations at the connection.

In particular, referring to fig. 2, fig. 3, the transition structure is specifically configured as a stress concentration hole 201. In general, the stress concentration hole 201 may be a circular hole, an elliptical hole or other holes with curved inner wall surfaces, and it should be noted that the inner avoiding surface of the stress concentration hole 201 should be smooth, so as to avoid stress concentration at the connection point of the valve arm 103 and the head 101 and/or the connection point of the valve arm 103 and the fixing portion 102.

Referring to fig. 4, in some embodiments, the aperture of the vent hole (not shown) covered by the valve sheet 100 is D, and the diameter of the circle where the connection points of the plurality of valve arms 103 and the head 101 are located is D₁(hereinafter, referred to as "diameter D1 of head 101"), minimum sealing distance b of head 101, hole diameter D of exhaust hole, and diameter D of head 101₁And the minimum sealing distance b satisfies the formula one:

D₁d +2 b; wherein, b is 0.8 mm-1.5 mm.

It can be understood that by limiting the minimum sealing distance b of the head 101 to 0.8mm to 1.5mm, the flow resistance loss can be minimized and the exhaust performance of the valve assembly can be improved on the premise of ensuring that the head 101 can better close the exhaust hole.

It should be noted that, when the joint of the valve arm 103 and the head 101 is providedWhen there is a stress concentration hole 201, the connection point of the plurality of valve arms 103 and the head 101 can be regarded as the geometric center of the stress concentration hole 201; when there are only two valve arms 103, the line connecting the two valve arms 103 with the head 101 forms the diameter D of the circle₁(ii) a When more than three valve arms 103 are provided, the connection points of the valve arms 103 to the head 101 can directly define a diameter D₁The circle of (c).

It should be noted that the involute parameters of the valve arm 103 in the present invention satisfy equation one:

wherein, the base radius a satisfies the following formula:theta is the phase difference. Base circle, involute angle, as is well known to those skilled in the artThe phase difference theta is a mathematical concept in an involute equation, and the specific shape of the involute can be determined by combining the magnitude of the phase difference theta, the magnitude of the phase difference theta and the magnitude of the phase difference theta with the magnitude of the equation.

It will be appreciated that the size of the bleed hole is a parameter that can be determined on the compressor by measurement, and first, the diameter D of the head 101 can be determined from the size of the bleed hole, in combination with the above equation one₁Appropriate dimensions of (a); then, according to the diameter D of the head 101₁And equation one above, the basic shape of the valve arm 103 can be determined.

In the equation one, the involute angleThe parameter of the phase difference theta can be further combined with the arm width L of the valve arm 103_aThe arm length L is selected to satisfy the arm width L_aAnd arm length L.

Referring to FIG. 4, in some embodiments, the valve flapThe diameter of the vent hole covered by the valve arm 103 is D, and the diameter of the circle where the connection points of the valve arms 103 and the fixing portion 102 are located is D₂(hereinafter, the diameter D of the fixing part 102₂"), diameter D of the fixation portion 102₂And the aperture D of the exhaust hole satisfies the formula two:

D₂＝nD；

wherein n is an empirical coefficient obtained based on a simulation result, and the value range of n is as follows: 2.51< n < 3.52.

It can be understood that the diameter by defining the circle on which the connection points of the plurality of valve arms 103 and the fixing portion 102 are located is D₂The relationship with the aperture D of the exhaust hole can optimize the elastic deformation amount of the valve arm 103, balance the deformability and rigidity of the valve arm 103, and thus improve the response rate of the valve sheet 100 to achieve rapid opening and closing of the head 101.

It should be noted that, when the stress concentration hole 201 is provided at the connection point of the valve arm 103 and the fixing portion 102, the connection points of the plurality of valve arms 103 and the fixing portion 102 may be regarded as the geometric center of the stress concentration hole 201; when there are only two valve arms 103, the connecting line of the two valve arms 103 and the fixing portion 102 forms the diameter D of the circle₂(ii) a When there are three or more valve arms 103, the connecting points of the valve arms 103 and the fixing portion 102 can directly define a diameter D₂The circle of (c).

Referring to FIG. 4, in some embodiments, valve arm 103 has a width L_aDiameter D of head 101₁Diameter D of the fixing part 102₂And the width L of the valve arm 103_aThe formula three is satisfied:

it can be understood that the width of the valve arm 103 can affect the rotation angle of the valve arm 103 and also affect the rigidity of the valve arm 103, and by the above arrangement, the length of the valve arm 103 (i.e. the rotation angle of the valve arm 103 is ensured at the same time) can be ensured, and at the same time, the valve arm 103 can have enough deformation along the opening direction of the head 101, the rigidity of the valve arm 103 can be properly reduced, and the deformation capability and the rigidity of the valve arm 103 can be well balanced, so that the flow resistance loss and the return loss can be balanced.

It should be noted that the diameter D of the fixing portion 102 can be determined according to the second formula₂I.e. D₂The width L of the valve arm 103 can be determined by the formula (2.51 to 3.52) D and the formula (iii)_aWhile depending on the width L of the valve arm 103_aThe value of the phase difference θ in the first equation can be appropriately adjusted to further determine the shape of the valve arm 103.

Referring to FIG. 4, in some embodiments, valve arm 103 has a length L and head 101 has a diameter D₁Diameter D of the fixing part 102₂And the width L of the valve arm 103_aThe formula four is satisfied:

wherein Y is an involute coefficient, satisfying the formula V: y is more than or equal to 0 and less than or equal to 4D₁；

L₀The minimum stress arm length is, a stress concentration hole 201 is formed in the joint of the valve arm 103 and the head 101 and/or the fixing portion 102, the radius of the stress concentration hole 201 is r, and the formula six is satisfied: l is not less than 5r₀≤15r。

It can be understood that when r is 0, it can be regarded that the joint between the valve arm 103 and the head 101 and the joint between the valve arm 103 and the fixing portion 102 are not provided with the stress concentration hole 201.

Therefore, when the stress concentration hole 201 is not provided at the joint of the valve arm 103 and the head 101, and at the joint of the valve arm 103 and the fixing portion 102, L₀0; accordingly, the method can be used for solving the problems that,

it can be understood that the length of the valve arm 103 can also affect the rigidity of the valve arm 103 and the deformation capability of the valve arm 103, and by the above arrangement, the rigidity of the valve arm 103 can be ensured, and at the same time, the valve arm 103 can have a sufficient deformation amount along the opening direction of the head 101, so that the deformation capability and the rigidity of the valve arm 103 can be well balanced, the flow resistance loss and the backflow loss can be balanced, and the response rate of the valve sheet 100 can be increased to realize rapid opening and closing of the head 101.

It should be noted that the diameter D of the fixing portion 102 can be determined according to the second formula₂Further, according to the formula four, the formula five, and the formula six, the length L of the valve arm 103 can be determined, and at the same time, according to the length range of the valve arm 103, the involute angle in the formula one can be appropriately adjustedTo further define the shape of the valve arm 103.

And it can be confirmed by experiments that the valve plate 100 of the present invention has a higher response rate in the operation of the rotary compressor and an improved exhaust flow rate per unit time compared to the conventional reed valve plate 100, so that the operation efficiency of the compressor is improved.

In some embodiments, referring to fig. 10 and 11, the bottom end surface of the fixing portion 102 of the valve sheet 100 contacts the valve seat periphery of the mounting flange 800800, the head portion 101 contacts the exhaust opening, and the annular fixing structure 601 of the valve sheet retainer 600 contacts the upper end surface of the fixing portion 102 of the valve sheet 100 to fix the valve sheet 100 to the mounting flange 800800.

It should be noted that, referring to fig. 5 and 6, the valve plate stopper 600 further includes a connecting structure for connecting the fixing structure 601 and the limiting structure, and along the opening direction of the head 101 (i.e. the axial direction of the exhaust hole), the distance between the bottom end surface of the limiting structure and the bottom end surface of the fixing structure 601 is H, the size of H and the lift space of the head 101 are determined.

In some embodiments, the lift height H and the vent hole diameter D satisfy the formula seven:

specifically, the larger the diameter D of the exhaust hole is, the larger the unit exhaust amount is, and the lift height H is not set too large, so as to shorten the exhaust time; the smaller the diameter D of the exhaust hole, the smaller the unit exhaust amount, and the height H of the lift is not set to be too small to prolong the exhaust time.

With the above arrangement, the relationship between the amount of exhaust gas per unit and the exhaust time can be balanced, whereby the flow resistance loss and the return loss can be balanced.

Referring to fig. 14, for a given exhaust aperture D, on the premise that other parameters of the valve sheet 100 are determined, based on the simulation of the overall energy efficiency performance of the compressor, when the exhaust aperture D is set, the overall energy efficiency performance of the compressor is determinedAnd when the compressor is used, the energy efficiency performance coefficient of the compressor is obviously excellent.

It is understood that the stopper 602 has a plate shape, and the bottom end surface of the stopper 602 is flat, and when the head 101 is opened to the top, the bottom end surface of the stopper 602 is in surface contact with the head 101.

It will also be appreciated that the diameter D of the annular interior of the fixed structure 601₃The diameter of the circle where the connection points of the plurality of valve arms 103 and the fixing portion 102 are located is D or more₂With this arrangement, the fixing structure 601 can be prevented from interfering with the elastic deformation of the valve arm 103.

It should be noted that, in some embodiments, referring to fig. 12 and 15, the bottom end surface of the fixing structure 601 is provided with at least one notch 1501, and the position of the notch 1501 corresponds to the position of the valve arm 103.

It can be understood that, at the position corresponding to the position of the valve arm 103, the bottom end surface of the fixing structure 601 is provided with the notch 1501, which can be used for avoiding the lifting movement deformation of the valve arm 103 of the valve sheet 100, and avoiding the generation of unnecessary interference.

It will also be appreciated that the notches 1501 are the same number as the valve arms 103 of the valve plate 100.

A compressor (not shown) according to some embodiments of the third aspect of the present invention comprises a compressor body and a valve assembly according to embodiments of the second aspect of the present invention.

Specifically, a compressor body having a discharge passage; a valve assembly is disposed in the exhaust passage.

It should be noted that, in some embodiments, the valve assembly is specifically disposed on a mounting flange 800 (i.e., a valve seat) of the compressor, in order to fix the valve plate stopper 600 on the mounting flange 800, a mounting groove 801 may be disposed on the mounting flange 800 around the exhaust hole, and then the valve plate stopper 600 is clamped in the mounting groove 801, for example, the valve plate stopper is mounted in an interference fit manner, at this time, it is required to satisfy that an inner diameter of the mounting groove 801 is slightly smaller than an outer diameter of the fixing structure 601; alternatively, the valve plate 100 may be fixed to the mounting flange 800 by the mounting structure 901 of the valve plate stopper 600.

In the prior art, when the valve seat for installing the reed valve is in a long and narrow shape and the thickness of the valve seat is reduced, on one hand, when the end face of the installation flange 800 of the valve seat is subjected to finish machining, the flatness and the like of a local thin-wall structure are obviously worsened compared with other areas. On the other hand, in the operation process of the compressor, the valve seat position is always extruded by high-low pressure gas on two sides of the valve seat, and the long and narrow valve seat structure greatly reduces the rigidity of the mounting flange 800, is easy to deform, and has adverse effects on the performance and the reliability of the compressor.

The compressor according to the embodiment of the invention has at least the following beneficial effects: since the valve sheet 100 is fixed more stably in the valve assembly, the service life of the valve sheet 100 is prolonged and the opening and closing time of the valve sheet 100 is effectively controlled, thereby facilitating the improvement of the energy efficiency of the compressor.

Meanwhile, the compressor adopting the embodiment of the invention can effectively reduce the maximum span and the section area of the valve seat on the compressor, and can replace the structure of the exhaust valve plate 100 used in the existing solution.

Compared with the traditional exhaust structure, the exhaust structure has the advantages of compact structure, higher rigidity of the mounting flange 800, good sealing performance, timely closing and the like.

In addition, referring to fig. 9 to 11, a mounting structure 901 may be further disposed on the valve plate stopper 600, a connecting hole 902 is disposed on the mounting structure 901, and a fastener 1001 is used to penetrate through the connecting hole 902 to fix the valve plate stopper 600 to the mounting flange 800800 of the compressor, in this case, a sinking groove structure may be disposed around the exhaust hole, or the sinking groove structure may not be disposed.

A refrigeration device (not shown) according to some embodiments of the fourth aspect of the invention comprises a compressor according to embodiments of the third aspect of the invention.

The refrigeration apparatus of the present invention may be an air conditioner, a refrigerator, or the like.

The refrigeration device provided by the embodiment of the invention has at least the following beneficial effects: by adopting the compressor of the embodiment of the third aspect of the invention, the working efficiency of the refrigerating device can be improved, the service life of the refrigerating device can be prolonged, and the satisfaction of users can be improved.

The embodiments of the present invention are described in detail above with reference to the accompanying drawings, and finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.