CN212774773U - Scroll compressor having a plurality of scroll members - Google Patents

Abstract

The utility model discloses a scroll compressor. The scroll compressor includes an orbiting scroll and a non-orbiting scroll. The non-orbiting scroll cooperates with the orbiting scroll to form a compression chamber that compresses the working fluid. The non-orbiting scroll includes a non-orbiting scroll end plate. And the static vortex end plate is provided with an exhaust hole. The compressed working fluid exits the compression chambers through the exhaust ports. A check valve is arranged above the exhaust hole. The check valve prevents the working fluid discharged through the discharge hole from flowing back to the compression chamber. The check valve includes: the valve seat is a step part arranged above the exhaust hole; the valve seat is positioned at the bottom end of the valve wall; and the valve plate can move towards or away from the valve seat under the guidance of the valve wall so as to press against or away from the valve seat, thereby closing or opening the exhaust hole. And a plurality of guide grooves are formed in the fixed vortex end plate. The guide groove extends outwards from the valve wall along the radial direction and the circumferential direction, and when the valve plate opens the exhaust hole, the guide groove is communicated with the exhaust hole.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The utility model relates to a scroll compressor, concretely relates to scroll compressor with built-in check valve in quiet vortex end plate.

Background

Generally, a scroll compressor includes an orbiting scroll, a non-orbiting scroll, a driving shaft, a bearing housing, a housing, and the like. The movable vortex, the fixed vortex, the driving shaft, the bearing seat and other parts are generally arranged in the shell. The orbiting scroll and the non-orbiting scroll constitute a compression mechanism and each have a wrap and an end plate. The orbiting and non-orbiting scrolls cooperate to form a compression chamber that compresses the working fluid. The driving shaft drives the movable scroll to do translational motion relative to the fixed scroll, and the working fluid in the compression cavity is compressed through the relative motion between the scroll of the movable scroll and the scroll of the fixed scroll. The working fluid is here typically a gas. The compressed high-pressure gas is discharged through a discharge hole provided on an end plate of the scroll. In order to prevent the discharged high-pressure gas from flowing back to the discharge hole, a check valve is generally installed on the discharge hole.

FIG. 1 illustrates a prior art non-orbiting scroll 100 'having a check valve 20'. The check valve 20 ' includes a valve plate 21 ' and a valve body 22 '. The valve body 22 'of the check valve 20' is fixed to an end plate of the non-orbiting scroll 100 'by means of a screw 26' connection. In the exhaust period, the check valve plate 21 'is pushed upwards under the exhaust pressure of the compressed gas, so that the exhaust hole 102' is opened, and the compressed gas in the compression cavity is exhausted to the high-pressure side in the compressor shell; when the discharge is finished, the pressure in the compression chamber of the compression mechanism is significantly reduced and is smaller than the gas pressure on the upper side (discharge side) of the check valve, so the valve sheet of the check valve is pressed against the discharge hole by the pressure difference, thereby preventing the high-pressure discharge gas on the upper side of the check valve from flowing back to the compression chamber.

The valve body 22 'of the check valve 20' according to the prior art has two legs. The inner side of the legs is designed as an inner cylindrical surface 221'. The outer circumference of the valve plate 21' of the check valve is in contact with the cylindrical surface. When the check valve plate moves up and down, the part of the cylindrical surface, which is contacted with the check valve plate, plays a role in guiding. In this structure, the check valve sheet contacts the inner cylindrical surface of the check valve body only at the narrow two portions. Therefore, the guiding function of the valve body is poor. Typically, the compressed gas is discharged from the discharge orifice in the form of a high frequency, high velocity pulse stream. The gas force acting on the check valve plate is difficult to be uniformly distributed on the valve plate, which easily causes two problems: (1) the valve plate of the check valve is easy to deflect under the condition of uneven stress and is clamped on the valve body of the check valve, so that the check valve fails, and the working fault of the compressor is caused; (2) the limiting area of the valve block of the restriction check valve is too small, the valve block of the check valve and the pulse airflow are easy to surge, and the valve block of the check valve is easy to vibrate, so that the noise of the compressor is abnormal. Therefore, there is a need to design a new check valve that overcomes the above technical problems. In addition, resistance in the flow path of the compressed gas discharged from the compression chamber is one of important aspects to be considered when designing the check valve. The flow resistance of the gas should be reduced as much as possible to improve the flow efficiency of the gas.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a scroll compressor with built-in check valve in quiet vortex end plate. Wherein, this kind of check valve can provide stable direction for the valve block to reduce the check valve and take place to deflect or the card is died and cause the condition that the check valve became invalid in opening and closing process valve block, and can reduce the chatter phenomenon of the valve block of check valve. In addition, the stability of the guide of the check valve is ensured, and meanwhile, a gas flow channel which accords with the gas flow characteristic is arranged, so that the flow resistance of the discharged gas is reduced, and the gas flow efficiency is improved.

Specifically, according to the utility model discloses a scroll compressor includes: carrying out movable vortex; and the fixed vortex is matched with the movable vortex to form a compression cavity for compressing the working fluid. The non-orbiting scroll includes a non-orbiting scroll end plate. And the static vortex end plate is provided with an exhaust hole, and the compressed working fluid is discharged out of the compression cavity through the exhaust hole. A check valve is arranged above the exhaust hole. The check valve prevents the working fluid discharged through the discharge hole from flowing back to the compression chamber. The check valve includes: the valve seat is a step part arranged above the exhaust hole; the valve seat is positioned at the bottom end of the valve wall; and the valve plate can move towards or away from the valve seat under the guidance of the valve wall so as to press against or be away from the valve seat, so that the exhaust hole is closed or opened. And a plurality of guide grooves are formed in the fixed vortex end plate. The flow guide groove extends outward from the valve wall in the radial direction and the circumferential direction. When the valve plate opens the exhaust hole, the diversion trench is communicated with the exhaust hole.

The flow guide groove is a groove formed by inwards recessing from the top surface of the fixed vortex end plate to the inside of the fixed vortex end plate.

Wherein, the guiding gutter has entry end and afterbody. When viewed along the axial direction, the included angle between the tangent of the inlet end and the tangent of the tail part is less than or equal to 90 degrees.

Wherein, the tail part of the diversion trench is provided with a diversion slope. The flow guide slope obliquely and axially extends upwards from the bottom of the flow guide groove to the top surface of the static vortex end plate.

Wherein, the water conservancy diversion slope is the plane, and the slope angle of water conservancy diversion slope is less than 40.

Wherein, the diversion slope is a circular arc surface.

Wherein the flow guide groove extends to 1/3-2/3 of the radius of the non-orbiting scroll end plate.

Wherein the non-orbiting scroll end plate comprises: a plurality of passages communicating different compression chambers to a high pressure side within a shell of the scroll compressor; and a plurality of variable volume ratio valves, each of which is provided on a corresponding passage to close or open the passage. The guide grooves are distributed according to the plurality of variable volume ratio valves.

The sum of the flow areas of the guide grooves is larger than the cross-sectional area of the exhaust hole.

And the part of the outer periphery of the valve plate, which is contacted with the valve wall, is more than or equal to one half of the outer periphery of the valve plate.

The scroll compressor with the structure ensures that the outer periphery of the valve block of the check valve is in contact with the valve wall at a plurality of positions, improves the stability of the valve wall for guiding the valve block, further can prevent the valve block of the check valve from deflecting when the check valve is opened and closed, and eliminates the vibration of the valve block of the check valve. Further, a plurality of guide grooves are provided around the valve wall of the check valve and a guide slope structure is provided at the end of the guide groove according to the flow characteristics of the discharged compressed gas and the arrangement of the discharge port of the compressed gas on the housing of the scroll compressor, which reduces the flow resistance of the gas discharged from the compression chamber. The sum of the flow areas of the guide grooves is larger than the cross-sectional area of the exhaust hole, so that the throttling effect is reduced, and the flowing efficiency of the gas is further improved.

Drawings

FIG. 1 is a perspective view of a non-orbiting scroll having a prior art check valve;

FIG. 2A is a perspective view of a non-orbiting scroll of a scroll compressor according to the present invention;

FIG. 2B is a cross-sectional view of the non-orbiting scroll with the check valve plate and the stop removed;

FIG. 2C is a top view of the non-orbiting scroll with the check valve plate and stop removed;

FIG. 2D is a top view of the non-orbiting scroll of FIG. 2A;

FIG. 3A is a top view of a non-orbiting scroll of a scroll compressor according to another embodiment;

FIG. 3B is a partial perspective view of the scroll compressor having the non-orbiting scroll shown in FIG. 3A;

FIG. 4A is a perspective view of a non-orbiting scroll of a scroll compressor according to another embodiment;

FIG. 4B is a top view of the non-orbiting scroll shown in FIG. 4A with the check valve plate and the stopper removed.

FIG. 5 is a partial perspective view of a scroll compressor with a discharge port disposed at the top of the housing.

Detailed Description

The scroll compressor according to the present invention will be described in detail with reference to the accompanying drawings. In the drawings, components having the same function have the same reference numerals.

As described in the background art, the check valve of the related art is disposed outside the non-orbiting scroll end plate. The portion of the outer circumference of the valve sheet contacting the guide surface is less than half of the outer circumference of the valve sheet. When the compressor exhausts, when the impact force of high-pressure gas acting on the check valve plate is uneven, the valve plate is easy to deflect and clamp, so that the check valve fails, the valve plate shakes easily, and the noise of the compressor is large. In order to solve the problems, the stability of the check valve is improved, the utility model provides a scroll compressor with novel check valve. The novel check valve is built in the fixed scroll end plate to enhance the guiding performance of the check valve on the valve plate. And a guide groove is provided around the valve wall to reduce flow resistance of the discharged high pressure gas, thereby improving performance of the compressor.

According to the utility model discloses a scroll compressor moves the vortex and the cooperation of quiet vortex is in order to form the compression chamber that compresses gas (working fluid) including moving vortex and quiet vortex. The orbiting scroll and the non-orbiting scroll have an end plate and a wrap, respectively. The compressed high-pressure gas is discharged from the compression chamber to the high-pressure side in the compressor casing through a discharge hole provided in the non-orbiting scroll end plate. In order to more clearly show the built-in check valve of the scroll compressor according to the present invention, only the non-orbiting scroll of the scroll compressor provided with the check valve is shown in the drawings, and other components are omitted. The scroll compressor according to the present invention will be described in detail with reference to the accompanying drawings.

As shown in fig. 2A-2D, the non-orbiting scroll 100 includes a non-orbiting scroll end plate 101 and a non-orbiting scroll wrap 102. The non-return valve 2 is provided in the non-orbiting scroll 101. The check valve includes a valve plate 21, a stopper 22, a valve wall 241, and a valve seat 242. In the exemplary embodiment shown, the valve plate 21 is a disc-shaped part. The valve wall 241 is a cylindrical circumferential wall. The valve seat 242 is a stepped portion at the bottom end of the circumferential wall. A valve wall 241 and a valve seat 242 are disposed above the exhaust hole 105. The valve wall 241 has a diameter corresponding to the diameter of the valve plate 21. When the valve sheet is fitted in the valve wall, the radially outer periphery of the valve sheet contacts the valve wall and the valve wall provides a guide for the valve sheet. The valve sheet can slide in the axial direction guided by the valve wall so that the valve sheet can be pressed against the valve seat or away from the valve seat, thereby being able to close or open the exhaust hole 105. The outer periphery of the valve plate of the check valve and the valve wall are in mutual contact at a plurality of positions along the circumferential direction, and the part of the outer periphery of the valve plate of the check valve, which is in contact with the valve wall, is greater than or equal to half of the whole outer periphery of the valve plate of the check valve, so that the guiding stability is improved.

The inner diameter of the valve seat 242 is smaller than the diameter of the valve plate 21, and the valve seat can provide support for the valve plate when the valve plate is fitted in the valve wall. When the check valve is closed, the valve plate can be pressed against the valve seat, so that the exhaust hole 105 can be closed. The stopper 22 is fixed to the non-orbiting scroll end plate 101 by a fixing member such as a screw 23. When the check valve is open, the stopper 22 prevents the valve plate from leaving the non-orbiting scroll end plate. As shown in detail in fig. 2B and 2C, a recess 222 for mounting the stopper 22 is provided on the non-orbiting scroll end plate. A threaded hole 223 for mating with the screw 23 is provided in the recess 222.

To direct the flow away from the discharge orifice 105 when the check valve is open, a plurality of guide slots 25 are provided in the non-orbiting scroll end plate extending radially outward from the valve wall.

The baffle groove 25 is a groove formed from the top surface 111 of the non-orbiting scroll end plate to be recessed inward of the non-orbiting scroll end plate. When the valve sheet opens the exhaust hole, the guide groove 25 communicates with the exhaust hole 105. As shown in fig. 2B, the channels have a bottom surface 251 and two side surfaces 253. The end of the baffle slot near the exhaust opening 105 is the inlet end 258 of the baffle slot, and the end of the baffle slot far from the inlet end is the tail 259 of the baffle slot. The two side surfaces 253 are shown as extending parallel to each other and perpendicular to the bottom surface 251. Alternatively, the side surfaces 253 may extend in an inclined manner with respect to the bottom surface 251, and the side surfaces may not be parallel to each other. In addition, in order to reduce the resistance when the gas flows in the diversion trench, a diversion slope 252 is arranged at the tail part of the diversion trench. The guide slope 252 extends obliquely upward from the bottom surface 251 to the top of the guide groove, i.e., to the top surface 111 of the non-orbiting scroll end plate. When the airflow flows in the diversion trench, the airflow flows out of the diversion trench along the inclined diversion slope. The flow guide slope structure avoids the direct impact of gas on the vertical wall, thereby avoiding the flowing dead zone of the gas flow and further reducing the pressure loss of the gas flow. In the exemplary embodiment shown, the guide slope 252 is a plane, and the angle between the guide slope and the bottom 251 of the guide channel, i.e. the slope angle α, is typically less than 40 °. Alternatively, the guide slope can be a curved surface, for example, a circular arc surface or an involute-type curved surface.

The number and distribution of the baffle slots 25 may be set based on the flow characteristics of the discharge airflow and the location of the discharge port 301 on the housing 300 of the scroll compressor. For example, each of the flow channels may be configured to direct the working fluid toward a discharge port of the scroll compressor. The plurality of channels may be arranged to direct the working fluid in a swirling flow towards the discharge port of the scroll compressor. A plurality of passages (not shown) that communicate different compression chambers to a high pressure side in the casing and a plurality of variable volume ratio valves provided on the respective passages to control closing or opening of the passages are provided on the non-orbiting scroll end plate 101. The variable volume ratio valves form a variable volume ratio valve group (VVR valve group) 106, and the distribution of the guide grooves can be appropriately adjusted according to the setting of the VVR valve group.

As shown in fig. 2C and 2D, the guide grooves extend outward from the valve wall in a curved shape in the radial direction and the circumferential direction as viewed in the axial direction. According to an exemplary embodiment, the flow guide groove extends outward from the valve wall in the radial direction and the circumferential direction along a smooth curve. Wherein, whole guiding gutter is crooked towards same circumferential direction. The included angle between the tangent line of the inlet end of the diversion trench and the tangent line of the tail part of the diversion trench is less than or equal to 90 degrees. Under the condition that the whole diversion trench is bent in a circular arc shape, the whole radian of the diversion trench is not more than 90 degrees. Alternatively, the channels may also extend in the shape of an involute, for example. The guide grooves are curved in the same manner when viewed in the axial direction. Fig. 2C shows a plurality of channels each curved in a counterclockwise direction, the plurality of channels being generally shaped like fan blades. Alternatively, each of the guide grooves may be curved in the clockwise direction. The plurality of channels may be evenly distributed around the valve wall or may be adapted to be unevenly distributed around the valve wall as the case may be. The trailing portion 259 of the baffle slots is located approximately at 1/3-2/3 of the outer radius of the non-orbiting scroll end plate. That is, the baffle slots extend outwardly in a radial direction from the valve wall to a location 1/3-2/3 of the radius of the non-orbiting scroll end plate. Each guide groove is distributed in the gap of the VVR valve group. This arrangement of the baffle slots is suitable for the case where the discharge port 301 on the scroll compressor housing 300 is located in the top center of the housing as shown in FIG. 5. The flow guide groove can control the air flow to be discharged to the top outlet in a spiral shape, so that the flow efficiency can be optimized, and the pressure loss can be reduced.

According to the utility model discloses, the flow area sum of each guiding gutter is greater than the cross-sectional area in exhaust hole. The flow area herein means a cross-sectional area of an inlet end of the guide groove communicating with the inside of the check valve when the check valve is opened. In the case of a rectangular flow guide groove, the flow area of the flow guide groove is the product of the depth h and the width d of the flow guide groove. This arrangement of the channels reduces the throttling effect. The depth h of the diversion trench can be smaller than the diameter of the check valve plate, so that the problem of resetting delay caused by overlarge stroke of the valve plate can be avoided. The depth h of the guide groove refers to the depth in the axial direction. The arrangement of the diversion trench can improve the gas flow efficiency and reduce the pressure loss.

FIG. 3A is a top view of a non-orbiting scroll of a scroll compressor according to another embodiment. This embodiment differs from the embodiment shown in fig. 2A in the distribution and the way of bending of the channels. This arrangement of channels is suitable for the case where the discharge port 301 on the scroll compressor housing 300 is located on the side of the housing as shown in FIG. 3B. According to this embodiment, a line connecting the center of projection of the discharge port 301 of the scroll compressor on the top surface 111 of the non-orbiting scroll end plate 101 and the center of projection of the discharge hole on the top surface forms the symmetry axis O as viewed in the axial direction. Each of the guide grooves 25 is arranged substantially symmetrically about the axis of symmetry O, and each of the guide grooves 25 is curved toward the orientation in which the exhaust port 301 is located, i.e., each of the guide grooves is curved toward the same end side of the axis of symmetry O. This arrangement of the baffle slots is adapted to direct the exhaust gas directly towards the exhaust port 301, shortening the gas flow path and reducing gas flow resistance.

Fig. 4A is a perspective view of a non-orbiting scroll of a scroll compressor according to yet another embodiment. FIG. 4B is a top view of the non-orbiting scroll shown in FIG. 4A with the check valve plate and the stopper removed. This embodiment differs from the embodiment shown in fig. 2A in the distribution and the way of bending of the channels. In the case where a plurality of VVR valves are provided, as shown in fig. 4A and 4B, the distribution and the curving direction of the guide grooves may be appropriately adjusted to suit a specific compressor configuration in order to avoid the VVR valves. This arrangement of the baffle slots is suitable for the case where the discharge port 301 on the scroll compressor housing is at the top of the housing 300 as shown in FIG. 5.

According to the utility model discloses a scroll compressor through with the check valve embeds in quiet vortex end plate, has ensured the valve block of check valve and has contacted with the valve wall in a plurality of positions department of its periphery to contact part more than or equal to half of valve block outer peripheral edges, thereby improved the stability of valve wall to the valve block direction. This arrangement prevents the valve plate from deflecting during opening and closing, while eliminating the risk of flutter of the valve plate. According to the utility model discloses a scroll compressor is provided with the guiding gutter and be provided with the water conservancy diversion slope at the afterbody of guiding gutter around the check valve. This structure reduces the flow resistance of the gas discharged from the compression chamber, so that the flow of the discharged gas is more smooth, and further, the chattering of the check valve due to the flow of the gas is reduced. In addition, the static vortex with the structure can be formed by casting according to the specific implementation process, so that the manufacturing cost can be saved. Of course, such a structure can also be manufactured in the form of machining.

Further, it should be noted that the radial direction in the above refers to a radial direction of a non-orbiting scroll of the compressor, the axial direction refers to a direction perpendicular to the radial direction, and the circumferential direction refers to a direction surrounding the axial direction.

Exemplary structures, components and couplings have been disclosed above for purposes of describing particular embodiments of the scroll compressor of the present invention in detail. It will be apparent, however, to one skilled in the art that the specific details set forth above are not necessarily required, that the exemplary structures, components, and couplings may be embodied in many different forms and that the specific details and exemplary structures, components, and couplings should not be construed as limiting the scope of the invention.

Claims (10)

1. A scroll compressor, the scroll compressor comprising:

carrying out movable vortex;

the fixed vortex is matched with the movable vortex to form a compression cavity for compressing working fluid, the fixed vortex comprises a fixed vortex end plate, an exhaust hole is formed in the fixed vortex end plate, the compressed working fluid is discharged out of the compression cavity through the exhaust hole,

characterized in that a check valve is disposed above the discharge hole, the check valve preventing the working fluid discharged through the discharge hole from flowing back to the compression chamber,

the check valve includes:

the valve seat is a step part arranged above the exhaust hole;

a valve wall, the valve seat being located at a bottom end of the valve wall;

a valve plate movable toward or away from the valve seat under the guidance of the valve wall to press against or away from the valve seat to close or open the exhaust hole,

the fixed vortex end plate is provided with a plurality of guide grooves, the guide grooves extend outwards along the radial direction and the circumferential direction from the valve wall, and when the valve plate opens the exhaust hole, the guide grooves are communicated with the exhaust hole.

2. The scroll compressor of claim 1, wherein the baffle slot is a groove formed recessed from a top surface of the non-orbiting scroll end plate into the non-orbiting scroll end plate.

3. The scroll compressor of claim 2, wherein the baffle slot has an inlet end and a tail portion, and wherein a tangent to the inlet end and a tangent to the tail portion form an angle of 90 ° or less when viewed in the axial direction.

4. The scroll compressor of claim 1, wherein the trailing portion of the baffle slot is provided with a baffle slope extending obliquely axially upward from a bottom of the baffle slot to a top surface of the non-orbiting scroll end plate.

5. The scroll compressor of claim 4, wherein the inducer slope is planar, the inducer slope having a slope angle of less than 40 °.

6. The scroll compressor of claim 4, wherein the flow guiding ramp is a circular arc surface.

7. The scroll compressor of any of claims 1-6, wherein the baffle slot extends to 1/3-2/3 of the radius of the non-orbiting scroll end plate.

8. The scroll compressor of any one of claims 1-6, wherein the non-orbiting scroll end plate comprises:

a plurality of passages communicating different compression chambers to a high pressure side within a shell of the scroll compressor; and

a plurality of variable volume ratio valves, each of which is provided on a corresponding passage to close or open the passage,

wherein the channels are distributed according to the plurality of variable volume ratio valves.

9. The scroll compressor of any one of claims 1-6, wherein a sum of flow areas of a plurality of the flow directing grooves is greater than a cross-sectional area of the discharge port.

10. The scroll compressor of claim 1, wherein a portion of the outer periphery of the valve plate in contact with the valve wall is equal to or greater than one-half of the outer periphery of the valve plate.

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