CN114593048B - A scroll compressor scroll profile structure - Google Patents

Abstract

The present invention discloses a scroll compressor scroll profile structure. The present invention processes a groove on the side wall near the starting point of the outer involute at the fixed scroll and/or movable scroll core. Before the main shaft angle turns to the exhaust angle, the central cavity is connected with the second compression cavity through the pressure relief groove, and the high-pressure gas flows to the low-pressure gas through the narrow channel; after the connection, when the main shaft angle continues to rotate 20° to 40°, the scroll teeth at the center of the movable scroll still cover the exhaust hole. When the main shaft angle continues to rotate more than 20° to 40°, the outer scroll line of the center of the movable scroll passes through the exhaust hole, and the exhaust hole is connected with the second compression chamber. At this time, the clearance between the exhaust channels on the movable and fixed scroll teeth is less than 0.2mm. The technical solution of the present invention solves the technical problem that at the moment of exhaust, the air flow at the exhaust hole produces a large instantaneous pressure mutation, which generates a pressure wave and has an adverse effect on the vibration and noise of the compressor, so that the compressor has the advantages of low vibration and low noise.

Description

A scroll compressor scroll profile structure

Technical Field

The invention relates to the technical field of a structure for weakening exhaust pressure waves of a scroll compressor, in particular to a scroll profile structure of a scroll compressor.

Background Art

The existing scroll compressor is composed of a pair of scroll disks with the same parameters, a phase difference of 180°, and a base circle center distance r, forming several pairs of symmetrical crescent-shaped closed compression chambers, from the inside to the outside, respectively, the first (center chamber), the second, and the third compression chambers; when the compressor is working, the volume of the compression chamber changes with the main shaft rotation angle. When the compression is finished, the second compression chamber is connected to the center chamber and the gas is discharged through the exhaust hole. Therefore, the scroll compressor does not need to set a suction and exhaust valve, and can also form a closed compression chamber. It is a compressor with a constant volume ratio. The constant volume ratio of the scroll compressor is designed according to a specific working condition of the compressor, but the actual operating condition of the scroll compressor changes with the indoor and outdoor ambient temperature. The actual internal and external pressure ratios are not equal, and sometimes this difference is very large.

When the exhaust pressure of the scroll compressor is not equal to the end pressure of the internal compression, insufficient compression (under-compression) or over-compression occurs. At the moment when the second compression chamber is connected to the central compression chamber, the gas needs to be compressed or expanded at a constant volume, which will produce a large instantaneous pressure mutation and form a pressure wave. This pressure wave can stimulate the resonance of the compressor and the gas resonance in the compressor exhaust chamber, causing the compressor to produce noise and vibration.

At the same time, this exhaust pressure wave enters the system through the exhaust pipe, and will form a certain exciting force at the bends or cross-section changes, causing pipe vibration.

In view of the problems existing in the above-mentioned prior art, it is very necessary to study and design a structure for weakening the pressure wave of a scroll compressor, so as to overcome the problems existing in the prior art.

Summary of the invention

According to the above-mentioned prior art, due to the large instantaneous pressure change of the airflow at the exhaust hole, a pressure wave is generated, which has an adverse effect on the vibration and noise of the compressor. In order to solve these problems, a structure for weakening the exhaust pressure wave of the compressor is provided. The present invention mainly solves the above-mentioned problem of the exhaust pressure wave caused by the exhaust airflow pulsation on the compressor by designing the scroll disk profile of the scroll compressor.

The technical means adopted by the present invention are as follows:

A scroll compressor scroll profile structure, comprising a fixed scroll, a movable scroll, a pressure relief groove and an exhaust hole;

The fixed scroll profile of the fixed scroll and the movable scroll profile of the movable scroll are both composed of an inner involute, a core transition line and an outer involute;

The involute angle of the fixed scroll profile is the same as the involute angle of the movable scroll profile, or the involute angle of the fixed scroll profile is greater than the involute angle of the movable scroll profile;

The pressure relief groove is a groove opened at the center of the fixed scroll and/or the movable scroll and close to the side wall near the starting point of the outer involute. The pressure relief groove can be a groove of any shape.

The disengagement point of the outer involute of the fixed scroll is Q, and the disengagement point of the outer involute of the movable scroll is P;

The opening position of the pressure relief groove is within the range of 10° to 120° along the involute starting from point P or Q;

The height of the pressure relief groove is h, and the heights of the fixed vortex and the movable vortex are H, 0＜h≤H.

The depth of the pressure relief groove is L, 0＜L≤0.2mm.

The exhaust hole is opened on the back plate of the fixed scroll and is connected to the exhaust channel of the high-pressure chamber.

The location of the exhaust hole meets the following conditions:

1) At the moment when the main shaft rotation angle turns to the exhaust angle, the movable scroll and the fixed scroll begin to disengage, the second compression chamber formed by the movable scroll and the fixed scroll is connected to the central compression chamber, and the core scroll teeth of the movable scroll cover the exhaust hole, and the exhaust hole does not cross the core scroll line of the movable scroll;

2) After the second compression chamber is connected with the central compression chamber, when the main shaft continues to rotate by 20° to 40°, the center vortex of the movable scroll still covers the exhaust hole, and the exhaust hole does not cross the center vortex line of the movable scroll. At this time, the gap between the outer arc of the center of the movable scroll and the inner arc of the center of the fixed scroll does not exceed 0.2 mm;

3) After the second compression chamber is connected with the central compression chamber, when the main shaft angle continues to rotate more than 20° to 40°, the outer vortex line of the core of the movable scroll passes through the exhaust hole, and the exhaust hole is connected with the second compression chamber.

The exhaust hole may be circular or irregular (non-circular), as long as the shape satisfies the above conditions.

Compared with the prior art, the present invention has the following advantages:

1. A scroll compressor scroll profile structure provided by the present invention is characterized in that a groove is machined on the side wall near the starting point of the outer involute at the center of the fixed scroll and/or the movable scroll, so that the central cavity and the second compression cavity are connected through the pressure relief groove before the main shaft angle turns to the exhaust angle, and the high-pressure gas flows to the low-pressure gas through the narrow channel, thereby avoiding a sharp change in gas pressure;

2. The present invention provides a scroll compressor scroll line structure, by setting the position of the exhaust hole, after the second compression chamber is connected with the central compression chamber, when the main shaft angle continues to rotate 20° to 40°, the scroll teeth of the core of the movable scroll still cover the exhaust hole, and when the main shaft angle continues to rotate more than 20° to 40°, the outer scroll line of the core of the movable scroll passes through the exhaust hole, and the exhaust hole is connected with the second compression chamber, and the gap between the outer circular arc of the core of the movable scroll and the inner circular arc of the core of the fixed scroll does not exceed 0.2mm, thereby reducing the pressure change at the moment of exhaust;

In summary, the technical solution of the present invention solves the technical problems existing in the prior art, and enables the compressor to have advantages such as low vibration and low noise.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

FIG. 1 is a schematic diagram of the structure of a pressure relief groove (equal width groove) in a specific implementation manner of the present invention.

FIG. 2 is a top view of a pressure relief groove (equal width groove) in a specific embodiment of the present invention.

FIG. 3 is a schematic diagram of the structure of the pressure relief groove (arc-shaped groove) in a specific implementation manner of the present invention.

FIG. 4 is a top view of a pressure relief groove (arc-shaped groove) in a specific embodiment of the present invention.

FIG. 5 is a schematic diagram of the state of the vortex core before disengagement in a specific embodiment of the present invention.

FIG. 5 a is a diagram showing the instant when the pressure relief groove begins to communicate with the central cavity.

FIG. 5 b is a diagram showing a state where the pressure relief groove is fully connected to the central cavity.

FIG5c is a diagram showing the instantaneous state of the pressure relief groove and the central cavity being closed.

Figure 5d is a diagram showing the exhaust disengagement state at the moment.

FIG. 6 is a schematic diagram of the state of the vortex core after disengagement in a specific embodiment of the present invention.

FIG. 6 a is a schematic diagram showing the case where the main shaft continues to rotate ∠E after the second compression chamber is connected to the central compression chamber.

FIG6b is a schematic diagram showing the case where the main shaft continues to rotate ∠F after the second compression chamber is connected to the central compression chamber.

In the figure: 1, movable scroll; 2, fixed scroll; 11, movable scroll base circle; 21, fixed scroll base circle; A, fixed scroll pressure relief groove; B, movable scroll pressure relief groove; C, angle between the end end of the pressure relief groove and the disengagement point; D, angle between the starting end of the pressure relief groove and the disengagement point; E/F, main shaft rotation angle after disengagement; L, groove depth of the pressure relief groove; H, vortex tooth height; h, pressure relief groove height; N, gap between the outer arc of the movable scroll core and the inner arc of the fixed scroll core; P, movable scroll disengagement point; Q, fixed scroll disengagement point; S, exhaust hole; U, exhaust hole contour line; V, movable vortex core vortex line.

DETAILED DESCRIPTION

It should be noted that, in the absence of conflict, the embodiments of the present invention and the features in the embodiments can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit exemplary embodiments according to the present invention. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprising" and/or "including" are used in this specification, it indicates the presence of features, steps, operations, devices, components and/or combinations thereof.

Unless otherwise specifically stated, the relative arrangement of the parts and steps described in these embodiments, the numerical expressions and numerical values do not limit the scope of the present invention. At the same time, it should be clear that, for ease of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. The technology, methods and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be regarded as part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar numbers and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

In the description of the present invention, it is necessary to understand that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention: the directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below their position devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. If not otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

As shown in Figures 1 to 6, a scroll compressor scroll profile structure includes a fixed scroll 2, a movable scroll 1, a pressure relief groove and an exhaust hole S; the fixed scroll profile of the fixed scroll 2 and the movable scroll profile of the movable scroll 1 are both composed of an inner involute, a core transition line and an outer involute.

The involute angle of the fixed vortex profile is the same as the involute angle of the movable vortex profile (symmetrical compression chamber), or the involute angle of the fixed vortex profile is greater than the involute angle of the movable vortex profile (asymmetrical compression chamber); in this specific embodiment, the involute angle of the fixed vortex profile is the same as the involute angle of the movable vortex profile.

The pressure relief groove is opened in the center of the fixed scroll 2 and/or the movable scroll 1, which is a groove machined on the side wall near the starting point of the outer involute; the solution adopted in this embodiment is that both the fixed scroll 2 and the movable scroll 1 have pressure relief grooves, which are the fixed scroll pressure relief groove A and the movable scroll pressure relief groove B respectively.

The pressure relief tank is set up as follows:

As shown in FIG2 , the disengagement point of the outer involute of the fixed scroll 2 is Q, and the disengagement point of the outer involute of the movable scroll 1 is P; the opening positions of the movable scroll pressure relief groove A and the movable scroll pressure relief groove B are within the range of the involute expansion angle ∠C to ∠D° starting from the Q point and the P point; ∠C is the angle between the end end of the pressure relief groove and the disengagement point; ∠D is the angle between the starting end of the pressure relief groove and the disengagement point, ∠D is generally 10° to 120°, ∠C is generally 10° to 120°, and is less than the ∠D value;

The height of the pressure relief groove is h, and the height of the vortex teeth of the fixed scroll and the movable scroll is H, 0＜h≤H, as shown in Figure 1. The groove depth of the pressure relief groove is L, 0＜L≤0.2mm, as shown in Figure 2.

The shape of the pressure relief groove is shown in Figures 1 and 2, and the intersection line between it and the side wall of the volute tooth is a narrow and long strip of equal width;

Or the shape of the pressure relief groove is shown in Figures 3 and 4, and the intersection line between it and the side wall of the volute tooth is an arc shape; of course, there can be other shapes, which will not be listed one by one.

As shown in Figure 5a, when the fixed scroll 2 and the movable scroll 1 are compressing, when the movable scroll 1 moves to the point where the starting end of the movable scroll pressure relief groove B contacts the inner wall of the movable scroll 1, and the starting end of the fixed scroll pressure relief groove A contacts the inner wall of the fixed scroll 2, the fixed scroll pressure relief groove A and the movable scroll pressure relief groove B begin to connect with the central cavity in an instant. At this time, the main shaft angle is within the range of ∠D before the disengagement points P and Q (not to ∠C), and ∠D is generally 10° to 120°. At this time, the pressure relief groove connects the central cavity with the second compression cavity, and the high-pressure gas flows to the low-pressure gas through the narrow pressure relief groove, which can avoid sudden changes in gas pressure.

As shown in FIG5b , the movable scroll 1 continues to move, achieving a state in which the fixed scroll pressure relief groove A and the movable scroll pressure relief groove B are fully connected with the central cavity.

As shown in Figure 5c, the movable scroll 1 continues to move. When the terminal end of the movable scroll pressure relief groove B contacts the inner wall of the movable scroll 1 and the terminal end of the fixed scroll pressure relief groove A contacts the inner wall of the fixed scroll 2, the fixed scroll pressure relief groove A and the movable scroll pressure relief groove B are closed to the central cavity. At this time, the main shaft angle is within the ∠C range before the disengagement points P and Q. ∠C is generally 10°~120° and is smaller than the ∠D value.

As shown in Figure 5d, the movable scroll 1 continues to move and is in the exhaust disengagement moment state. The central cavity begins to communicate with the second compression cavity. At this time, the vortex teeth at the core of the movable scroll cover the exhaust hole S, and the exhaust hole contour line U does not cross the vortex line V at the core of the movable scroll.

The exhaust hole S is opened on the back plate of the fixed scroll 2 and is connected to the exhaust passage of the high pressure chamber. The position of the exhaust hole S meets the following conditions:

1) At the moment when the main shaft rotation angle turns to the exhaust angle, the movable scroll 1 and the fixed scroll 2 begin to disengage, the second compression chamber formed by the movable scroll 1 and the fixed scroll 2 is connected to the central compression chamber, and the core vortex teeth of the movable scroll 1 cover the exhaust hole S, and the exhaust hole S does not cross the core vortex line V of the movable scroll 1, as shown in Figure 5d.

2) After the second compression chamber is connected with the central compression chamber, when the main shaft angle continues to rotate ∠E (∠E is 20°~40°), the core vortex teeth of the movable scroll 1 still cover the exhaust hole S, and the exhaust hole S will not cross the core vortex line V of the movable scroll 1. At this time, the gap N between the outer arc of the core of the movable scroll 1 and the inner arc of the core of the fixed scroll 2 does not exceed 0.2mm, reducing the pressure change at the moment of exhaust, as shown in Figure 6a.

3) When the main shaft angle continues to rotate by ∠F (∠F＞∠E), the core vortex line (outer side) V of the movable scroll 1 passes through the exhaust hole contour line U, and the exhaust hole S is connected to the second compression chamber, as shown in FIG6b.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims (5)

1. The vortex molded line structure of the vortex compressor is characterized by comprising a fixed vortex, an movable vortex, a pressure relief groove and an exhaust hole;

The fixed scroll molded line of the fixed scroll and the movable scroll molded line of the movable scroll are composed of an inner involute, a central transition line and an outer involute;

The involute expansion angle of the fixed scroll molded line is the same as the involute expansion angle of the movable scroll molded line, or the involute expansion angle of the fixed scroll molded line is larger than the involute expansion angle of the movable scroll molded line;

The pressure relief groove is a groove which is formed in the center of the fixed scroll and/or the movable scroll and is close to the side wall near the starting point of the outer involute;

the exhaust hole is a back plate arranged on the fixed vortex and is communicated with an exhaust channel of the high-pressure cavity;

The exhaust hole is round or special-shaped.

2. The scroll compressor scroll profile structure of claim 1, wherein the point of disengagement of the outer involute of the fixed scroll is Q and the point of disengagement of the outer involute of the orbiting scroll is P;

the pressure relief groove is arranged at a position which is within a range of 10-120 degrees along an involute from a point P or a point Q.

3. The scroll compressor scroll profile structure of claim 1, wherein the height of the relief groove is H, and the heights of the fixed scroll and the movable scroll are H,0 < h.ltoreq.h.

4. The scroll compressor scroll line structure according to claim 1, wherein the groove depth of the pressure relief groove is L, and L is more than 0 and less than or equal to 0.2mm.

5. A scroll compressor scroll type line structure according to claim 1, wherein the position of the discharge hole satisfies the following condition:

1) At the moment that the main shaft rotates to an exhaust angle, the movable vortex and the fixed vortex start to be disengaged, a second compression cavity formed by the movable vortex and the fixed vortex is communicated with a central compression cavity, a central vortex tooth of the movable vortex is covered on the exhaust hole, and the exhaust hole does not cross a central vortex line of the movable vortex;

2) After the second compression cavity is communicated with the central compression cavity, when the main shaft rotation angle continues to rotate for 20-40 degrees, the central vortex teeth of the movable vortex are still covered on the exhaust holes, the exhaust holes cannot cross the central vortex line of the movable vortex, and at the moment, the gap between the circular arc at the outer side of the central part of the movable vortex and the circular arc at the inner side of the central part of the fixed vortex is not more than 0.2mm;

3) And after the second compression cavity is communicated with the central compression cavity, when the rotation angle of the main shaft continuously rotates for more than 20-40 degrees, the vortex line at the outer side of the central part of the movable vortex passes through the exhaust hole, and the exhaust hole is communicated with the second compression cavity.