CN113464440B - Valve plate, valve component, compressor and refrigerating device - Google Patents
Valve plate, valve component, compressor and refrigerating device Download PDFInfo
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- CN113464440B CN113464440B CN202110959843.4A CN202110959843A CN113464440B CN 113464440 B CN113464440 B CN 113464440B CN 202110959843 A CN202110959843 A CN 202110959843A CN 113464440 B CN113464440 B CN 113464440B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
- F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
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Abstract
The invention relates to a valve plate, a valve component, a compressor and a refrigerating device, wherein the valve plate comprises a head part, a fixing part and a plurality of valve arms, and the fixing part is annular and is arranged around the head part; the valve arms are uniformly arranged between the head part and the fixing part along the circumferential direction of the head part, one end of each valve arm is connected with the head part, and the other end of each valve arm is connected with the fixing part and extends around the head part in an involute shape. The valve plate provided by the embodiment of the invention at least has the following beneficial effects: through setting up a plurality of valve arms of evenly distributed to set up every valve arm into and be involute-shaped, can guarantee the radial connection rigidity of the head of valve block and fixed part when guaranteeing valve arm length, thereby improve the response rate of valve block, open and close with the realization head fast.
Description
Technical Field
The invention belongs to the technical field of refrigeration equipment, and particularly relates to a valve plate, 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 rigidity of a valve plate of the reed valve can influence the performance of the compressor, and in the traditional reed valve exhaust structure, the flow resistance loss can be reduced by reducing the rigidity of the valve plate; however, under high-frequency working conditions, when the valve plate is long and the rigidity is too low, the valve plate is not closed timely, so that backflow loss is increased, and the overall performance is reduced.
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 which has a higher response speed and can be opened and closed quickly.
Meanwhile, the invention also provides a valve assembly with the valve plate, a compressor with the valve assembly and a refrigerating device with the compressor.
The valve plate comprises a head part, a fixing part and a plurality of valve arms, wherein the fixing part is annular and is arranged around the head part; the valve arms are uniformly arranged between the head part and the fixing part along the circumferential direction of the head part, one end of each valve arm is connected with the head part, the other end of each valve arm is connected with the fixing part, and the valve arms are arranged around the head part in an involute shape.
The valve plate provided by the embodiment of the invention at least has the following beneficial effects: through setting up a plurality of valve arms of evenly distributed to set up every valve arm into and be involute-shaped, can guarantee the radial connection rigidity of the head of valve block and fixed part when guaranteeing valve arm length, thereby improve the response rate of valve block, open and close with the realization head fast.
According to some embodiments of the invention, the valve arm is provided with 2 to 4.
According to some embodiments of the invention, the width of the valve arm in the direction of extension of the valve arm remains constant.
According to some embodiments of the invention, a width of a gap between adjacent valve arms in an extending direction of the valve arms is kept constant.
According to some embodiments of the invention, the valve arm has a swivel angle of 180 to 720 degrees.
According to some embodiments of the invention, a transition structure is provided at the connection of the valve arm with the head and/or the fixation part.
According to some embodiments of the invention, the transition structure is a stress concentrating hole.
According to some embodiments of the invention, the diameter of the vent hole covered by the head part is D, and the diameter of the circle where the connection points of the valve arms and the head part are located is D 1 And the minimum sealing distance of the head part is b, and the following requirements are met: d 1 = D +2b; wherein b =0.8mm to 1.5mm.
According to some embodiments of the invention, the involute equation of the valve arm is:
wherein a is the base circle radius, and satisfies the following conditions:
is an involute angle; θ is the phase difference.
According to some embodiments of the invention, a plurality of said valve arms andthe diameter of the circle where the connecting point of the fixing part is located is D 2 Satisfies the following conditions: d 2 = nD; of these, 2.51<n<3.52。
According to some embodiments of the invention, the valve arm has a width L a And satisfies the following conditions:
according to some embodiments of the invention, the valve arm has a length L, satisfying:
wherein, Y is the involute coefficient, satisfies: y is more than or equal to 0 and less than or equal to 4D 1 ；L 0 The valve arm is the minimum stress arm length, a stress concentration hole is formed in the joint of the valve arm and the head and/or the fixing part, the radius of the stress concentration hole is r, and the stress concentration hole satisfies the following conditions: l is more than or equal to 5r 0 ≤15r。
A valve assembly according to an embodiment of the second aspect of the present invention, which is disposed in a discharge passage of a compressor, and includes a valve seat having a discharge hole communicating with the discharge passage and a valve sheet according to an embodiment of the first aspect of the present invention; the head of the valve plate covers the exhaust hole.
The valve assembly according to the embodiment of the invention has at least the following advantages: through setting up a plurality of valve arms of evenly distributed to set up every valve arm into being involute form, can guarantee the radial connection rigidity of the head of valve block and fixed part when guaranteeing valve arm length, thereby improve the response rate of valve block, open and close with the realization head fast, thereby promote the efficiency of valve module.
According to some embodiments of the invention, the valve assembly further comprises a stopper comprising a connected fixing structure for fixing the fixing portion at a periphery of the vent hole and a limiting structure for limiting an opening height of the head portion.
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: by adopting the high-performance valve assembly of the embodiment of the second aspect of the invention, the working efficiency of the compressor can be improved, and the service life of the compressor can be prolonged.
A refrigeration unit according to an embodiment of the fourth aspect of the invention comprises a compressor according to an embodiment of the third aspect of the 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 of some embodiments of the present invention in a closed position;
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 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 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 according to some embodiments of the present invention.
Reference numerals:
a valve sheet 100, a head 101, a fixing portion 102, and a valve arm 103;
a stress concentrating hole 201;
the device comprises a limiter 600, a fixing structure 601, a limiting structure 602, a connecting structure 603 and a through hole 604;
mounting flange 800 and mounting groove 801;
a fastener 1001.
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 descriptions for distinguishing technical features, they are not interpreted as indicating or implying relative importance or implicitly indicating the number of indicated technical features or implicitly indicating the precedence of the indicated technical features.
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 a suction channel, drives a piston to compress the refrigerant gas through the operation of a motor, and discharges high-temperature and high-pressure refrigerant gas to an 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 optimized by reducing the clearance volume of the valve seat and reducing the exhaust resistance loss.
Firstly, the clearance volume can be reduced by reducing the thickness of the exhaust valve seat, the mounting valve seat of the reed valve is in a long and narrow shape, and when the thickness of the valve seat is reduced, on one hand, when the end face of a flange at the back of the valve seat is finely processed, the flatness and the like of a local thin-wall structure are obviously worsened compared with other areas. On the other hand, in the running 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 flange, is easy to deform and has adverse effects on the performance and the reliability of the compressor.
In addition, the rigidity of the valve plate can affect the performance of the compressor, and in the reed valve exhaust structure of the existing compressor, the flow resistance loss can be reduced by reducing the rigidity of the valve plate. However, under high-frequency working conditions, the valve plate is long, and the valve plate is not closed timely when the rigidity is too small, so that backflow loss is increased, and the overall performance is reduced.
To this end, embodiments of the present invention will be described in detail with reference to fig. 1 to 14.
Referring to fig. 1, there is shown some embodiments of a valve sheet 100 of the first aspect of the present invention, which comprises a head portion 101, a fixing portion 102 and a plurality of valve arms 103.
Specifically, referring to fig. 1, the head 101 is located at the geometric center of the valve sheet 100, and the fixing portion 102 is annular and disposed around the head 101; 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, 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 will be appreciated that the valve plate 100 is disposed on a valve seat (e.g., a mounting flange 800 shown in fig. 8) of the compressor, the valve seat being located in a discharge passage of the compressor, wherein the head 101 is configured to close a discharge hole (see fig. 1 and 2) when the compressor is in a suction state, and wherein the head 101 is configured to open the discharge hole (see fig. 3) when the compressor is in a discharge state, and gas is discharged from the compressor through a gap between the discharge hole and the head 101. When the exhaust is finished, the head 101 closes the exhaust hole again under the elastic restoring force of the valve arm 103, and covers and closes 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 set to be greater 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 present application, the number of valve arms 103 is selected to be 2 to 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: a line where the distance from a point to the center of the circle is proportional to the angle of the line connecting the point and the origin.
Specifically, a round shaft is fixed on a plane, a thread is wound on the shaft, a thread end is tensioned, the thread is moved 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 curve.
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 uniform force can avoid the stress concentration of the valve arm 103, thereby improving the fatigue resistance of the valve arm 103 and prolonging the service life of the valve sheet 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, 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 diameter of the vent hole (not shown) covered by the head portion 101 of the valve sheet 100 is D, and the diameter of the circle where the plurality of valve arms 103 are connected to the head portion 101 is D 1 (hereinafter, referred to as "diameter D1 of head 101"), minimum sealing distance of head 101 is b, hole diameter D of exhaust hole, and diameter D of head 101 1 And the minimum sealing distance b satisfies the formula one:
D 1 = D +2b; wherein b =0.8mm to 1.5mm.
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 reduced as much as possible on the premise of ensuring that the head 101 can better close the exhaust hole, and the exhaust performance of the valve assembly can be improved.
It should be noted that, when the stress concentration hole 201 is provided at the connection point of the valve arm 103 and the head 101, the connection points of the plurality of valve arms 103 and the head 101 may 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 circle 1 (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 D 1 The 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:
in the case of an involute angle, θ represents a phase difference. As is well known to those skilled in the art, the base circle, the involute angle
The phase difference theta is a mathematical concept in an involute equation, and the sizes of the phase difference theta, the phase difference theta and the involute equation can be combined to determine the specific shape of the involute.
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 one 1 Appropriate dimensions of (a); then, according to the diameter D of the head 101 1 And equation one above, the basic shape of the valve arm 103 can be determined.
In the equation one, the involute angle
The parameter selection of the phase difference θ can be further combined with the arm width L of the valve arm 103 a The arm length L is selected to satisfy the arm width L a And arm length L.
Referring to fig. 4, in some embodiments, the diameter of the vent hole covered by the head portion 101 of the valve sheet 100 is D, and the diameter of a circle where the connection points of the plurality of valve arms 103 and the fixing portion 102 are located is D 2 (hereinafter, the diameter D of the fixing part 102 2 "), the diameter D of the fixation section 102 2 And the aperture D of the exhaust hole satisfies the formula two:
D 2 ＝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-woven fabric was woven into 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 D 2 The 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 circle 2 (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 D 2 The circle of (c).
Referring to FIG. 4, in some embodiments, valve arm 103 has a width L a Diameter D of head 101 1 Diameter D of the fixing portion 102 2 And the width L of the valve arm 103 a The 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) can be ensured, and at the same time, the valve arm 103 can have enough deformation along the opening direction of the head 101, and the rigidity of the valve arm 103 can be properly reduced, so that the deformation capability and the rigidity of the valve arm 103 can be well balanced, and the flow resistance loss and the backflow loss can be balanced.
It should be noted that the diameter D of the fixing portion 102 can be determined according to the second formula 2 I.e. D 2 = (2.51 to 3.52) D, and the width L of the valve arm 103 can be determined from the formula three a While depending on the width L of the valve arm 103 a The 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 D 1 Diameter D of the fixing part 102 2 And the width L of the valve arm 103 a The 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 4D 1 ；
L 0 The minimum stress arm length is, a stress concentration hole is arranged at the joint of the valve arm 103 and the head part 101 and/or the fixing part 102, the radius of the stress concentration hole is r, and the formula six is satisfied: l is more than or equal to 5r 0 ≤15r。
It can be understood that when r is 0, it can be regarded that no stress concentration hole is arranged at the connection between the valve arm 103 and the head 101, or at the connection between the valve arm 103 and the fixing portion 102.
Therefore, when no stress concentration hole is 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, L 0 =0; 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 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 achieve 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 formula 2 Further, 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 adjusted
To further define the shape of the valve arm 103.
And it can be confirmed by experiments that the valve sheet 100 of the present invention has a higher response rate and an improved discharge flow rate per unit time in the operation of the rotary compressor, compared to the conventional reed valve sheet, so that the operation efficiency of the compressor is improved.
According to some embodiments of the second aspect of the invention, the valve assembly is arranged in a discharge passage of a compressor and comprises a valve seat and a valve plate 100 of the first aspect of the invention.
Specifically, referring to fig. 8, the valve seat has a vent hole (not directly shown) communicating with the vent passage, and the head 101 of the valve sheet 100 covers the vent hole.
In some embodiments, referring to fig. 5 and 6, the valve assembly further comprises a stopper 600, the stopper 600 comprises a fixing structure 601 and a limiting structure 602 which are connected, the fixing structure 601 is used for fixing the fixing part 102 at the periphery of the vent hole, and the limiting structure 602 is used for limiting the opening height of the head 101.
As shown in fig. 5 and 6, the stopper 600 further includes a connecting structure 603 for connecting the fixing structure 601 and the limiting structure 602, and a distance H between a bottom end surface of the limiting structure 602 and a bottom end surface of the fixing structure 601 along an opening direction of the head 101 (i.e., an axial direction of the exhaust hole), a size of H and an opening height space of the head 101 are determined.
In some embodiments, the opening height H and the vent 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 opening height H is not set to be 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 opening height H should not be set 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 plate are determined, based on the compressor complete machine energy efficiency performance simulation, when the exhaust aperture D is set, the other parameters of the valve plate are determined
And when the compressor is used, the energy efficiency performance coefficient of the compressor is obviously excellent.
It is understood that the limiting structure 602 has a plate shape, and the bottom end surface of the limiting structure 602 is configured to be flat, and when the head 101 is opened to the top end, the bottom end surface of the limiting structure 602 can be in surface contact with the head 101.
It will also be appreciated that the fixing structure 601 is annular and can be adapted to the shape of the fixing portion 102 of the valve sheet 100, so as to press-fit the valve sheet 100 at the periphery of the exhaust hole.
It will also be appreciated that the diameter D of the annular interior of the fixed structure 601 3 The 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 more 2 With this arrangement, the fixing structure 601 can be prevented from interfering with the elastic deformation of the valve arm 103.
In some embodiments, the lower end surface of the fixing portion 102 of the valve sheet 100 contacts the valve seat periphery of the mounting flange 800, the head portion 101 contacts the exhaust port, and the annular fixing structure 601 of the 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 800.
In the early stage of air exhaust of the compressor, the head part 101 of the valve plate 100 moves along the axial direction of the air exhaust hole and impacts the limiting structure 602 of the limiter 600; at the end of the exhaust period, the head 101 of the valve plate 100 falls back to strike the periphery of the exhaust port.
In some embodiments, referring to fig. 7, the through hole 604 is formed on the limiting structure 602, so that the limiting structure 602 forms a ring structure, and thus when the bottom end surface of the limiting structure 602 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 limiting structure 602, and the above technical effects can be achieved.
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, the compressor body has 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 the mounting flange 800 (i.e., the valve seat) of the compressor, in order to fix the position limiter 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 position limiter 600 is clamped in the mounting groove 801, for example, by an interference fit, where it is required that the inner diameter of the mounting groove 801 is slightly smaller than the outer diameter of the fixing structure 601.
In the prior art, the mounting structure of the reed valve is elongated, and when the thickness of the valve seat is reduced, on one hand, when the end face of the mounting flange of the valve seat is precisely machined, the flatness and the like of a local thin-wall structure are obviously worsened compared with other areas. On the other hand, in the running 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, 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: the high-performance valve assembly of the embodiment is adopted, the working efficiency of the compressor can be improved, and the service life is prolonged.
Meanwhile, the compressor provided by the embodiment of the invention can effectively reduce the maximum span and the cross-sectional area of the valve seat on the compressor, and can replace an exhaust valve plate structure 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, good sealing performance, timely closing and the like.
In addition, as shown in fig. 9 to 11, a mounting structure 901 may be further provided at the stopper 600, the mounting structure 901 may be provided with a connecting hole 902, and a fastening member 1001 may pass through the connecting hole 902 to fix the stopper 600 to the mounting flange 800 of the compressor, in this case, one mounting groove 801 may be provided around the exhaust hole or the mounting groove 801 may not be provided.
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 arranging the valve arms 103 on the valve plate 100, the valve arms 103 are uniformly distributed, and each valve arm 103 is arranged to be in an involute shape, the length of the valve arm 103 can be ensured, meanwhile, the radial connection rigidity of the head part 101 of the valve plate 100 and the fixing part 102 can be ensured, and thus, the response rate of the valve plate 100 is improved, and the head part 101 can be quickly opened and closed.
Therefore, the working efficiency of the refrigerating device can be effectively improved, the service life of the refrigerating device is prolonged, and the satisfaction degree of users is 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.
Claims (14)
1. A valve plate is applied to a compressor and is characterized by comprising:
a head;
the fixing part is annular and arranged around the head part;
the valve arms are uniformly arranged between the head part and the fixing part along the circumferential direction of the head part, one end of each valve arm is connected with the head part, the other end of each valve arm is connected with the fixing part, and the valve arms are arranged around the head part in an involute shape in an extending manner;
wherein a circle where connection points of the plurality of valve arms and the head portion are located has a diameter D 1 The diameter of a circle where the connection points of the plurality of valve arms and the fixing portion are located is D 2 (ii) a The width of the valve arm is L a And satisfies the following conditions:
the length of the valve arm is L, and the following requirements are met:
wherein, Y is the involute coefficient, satisfies: y is more than or equal to 0 and less than or equal to 4D 1 ，L 0 Is the minimum stress arm length.
2. The valve plate of claim 1, wherein there are between 2 and 4 valve arms.
3. The valve plate of claim 1, wherein the width of the valve arm in the direction of extension of the valve arm remains constant.
4. The valve sheet according to claim 2, wherein the width of the gap between adjacent valve arms in the extending direction of the valve arms is kept constant.
5. The valve plate of claim 1, wherein the valve arm has a pivot angle of 180 to 720 degrees.
6. The valve sheet according to any one of claims 1 to 5, wherein the hole diameter of the vent hole covered by the head is D, the minimum sealing distance of the head is b, and the following requirements are satisfied: d 1 = D +2b; wherein b =0.8mm to 1.5mm.
7. The valve plate of claim 6, wherein the involute equation of the valve arm is:
wherein a is the base circle radius, and satisfies the following conditions:
is an involute angle; θ is the phase difference.
8. The valve plate of claim 6, wherein D is 2 = nD; among them, 2.51<n<3.52。
9. The valve plate according to claim 6, wherein the joint of the valve arm and the head and/or the fixing portion is provided with a stress concentration hole.
10. The valve plate of claim 9, wherein the stress concentrating hole has a radius r, L 0 Satisfies the following conditions: l is not less than 5r 0 ≤15r。
11. 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 sheet of any one of claims 1 to 10, wherein the head covers the vent.
12. The valve assembly of claim 11, further comprising a retainer comprising a securing structure and a retaining structure connected, the securing structure for securing the securing portion at a periphery of the vent, the retaining structure for defining an opening height of the head.
13. A compressor, comprising:
a compressor body having a discharge passage;
a valve assembly according to claim 11 or 12 disposed in the exhaust passage.
14. A refrigeration apparatus comprising the compressor of claim 13.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110959843.4A CN113464440B (en) | 2021-08-20 | 2021-08-20 | Valve plate, valve component, compressor and refrigerating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110959843.4A CN113464440B (en) | 2021-08-20 | 2021-08-20 | Valve plate, valve component, compressor and refrigerating device |
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| Publication Number | Publication Date |
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| CN113464440A CN113464440A (en) | 2021-10-01 |
| CN113464440B true CN113464440B (en) | 2022-12-27 |
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| Application Number | Title | Priority Date | Filing Date |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1755108A (en) * | 2004-09-29 | 2006-04-05 | 丹福斯压缩器有限公司 | Piston type compressor especially sealed refrigerated compressor |
| CN109707873A (en) * | 2019-01-17 | 2019-05-03 | 北京宇航系统工程研究所 | A kind of ripple spring vibration prevention check valve |
| CN111502964A (en) * | 2020-04-26 | 2020-08-07 | 山东理工大学 | High-integration moving-coil type electromagnetic direct-drive metering pump |
| CN212272546U (en) * | 2020-08-31 | 2021-01-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Upper flange bearing, pump body assembly and compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8622315B2 (en) * | 2007-09-20 | 2014-01-07 | Robert Bosch Gmbh | Fluid injector having a reed valve |
-
2021
- 2021-08-20 CN CN202110959843.4A patent/CN113464440B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1755108A (en) * | 2004-09-29 | 2006-04-05 | 丹福斯压缩器有限公司 | Piston type compressor especially sealed refrigerated compressor |
| CN109707873A (en) * | 2019-01-17 | 2019-05-03 | 北京宇航系统工程研究所 | A kind of ripple spring vibration prevention check valve |
| CN111502964A (en) * | 2020-04-26 | 2020-08-07 | 山东理工大学 | High-integration moving-coil type electromagnetic direct-drive metering pump |
| CN212272546U (en) * | 2020-08-31 | 2021-01-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Upper flange bearing, pump body assembly and compressor |
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| CN113464440A (en) | 2021-10-01 |
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