Asymmetric scroll compressor for eliminating unbalance and method for eliminating unbalance and its application

Abstract

The application belongs to the field of compression equipment, and particularly relates to an asymmetric scroll compressor for eliminating unbalance load, application and unbalance load elimination method. The static scroll disc of the scroll compressor is provided with an airflow exchange channel for connecting the second working cavity and the second working cavity. Two ports of the airflow exchange channel are respectively located at two meshing points of the profile lines of the dynamic scroll disc and the static scroll disc when the main shaft rotation angle of the compression component is 0 or 180 degrees. The shape, size and position of the two ports on the wall surface of the static scroll disc in the airflow exchange channel satisfy that when the dynamic scroll disc rotates to 0 or 180 degrees, the two ports are completely blocked by the profile lines in the dynamic scroll disc and the static scroll disc, and the airflow exchange channel is closed. The two ports are open under other rotation angles, the airflow exchange channel is conducted and the internal pressures of the first working cavity and the second working cavity are balanced. The application solves the problem that the unbalance load inherent in the asymmetric scroll compressor is difficult to be completely eliminated in the prior art.

Description

TECHNICAL FIELD

[0001] The present application belongs to the field of compression equipment, and particularly relates to an asymmetric scroll compressor eliminating eccentric load and a method for eliminating eccentric load. BACKGROUND

[0002] The scroll compressor is a kind of volumetric compression compressor, and the compression component is composed of a dynamic scroll plate and a static scroll plate. The static scroll plate is fixed on a rack, and the dynamic scroll plate is driven by an eccentric shaft and rotates around the center of the base circle of the static scroll plate with a small radius. During the rotation of the dynamic scroll plate, a working cycle of air suction, compression and air discharge is completed. In this process, air is sucked into the periphery of the static scroll plate through an air filter, and with the rotation of the eccentric shaft, the air is gradually compressed in the crescent-shaped compression cavities formed by the meshing lines of the dynamic scroll plate and the static scroll plate, and then continuously discharged through the axial hole of the central part of the static scroll plate.

[0003] The static scroll plate of the asymmetric scroll compressor is elongated by half a circle compared with the dynamic plate line, so that an air suction cavity is formed on the outside and the inside of the static scroll plate, respectively, which are called the first working cavity and the second working cavity. When the asymmetric scroll compressor sucks air, the two working cavities alternately complete air suction, and the main shaft rotation angle is different by 180°, so it is also called an asynchronous air suction scroll compressor. Compared with the general scroll compressor, the asymmetric scroll compressor has higher space utilization and avoids the problem of air suction overheating loss, which is also the advantage of the asymmetric scroll compressor. However, due to the unique structure of the asymmetric scroll compressor, the air suction and compression processes of the two groups of working cavities are not synchronized, and there is always a pressure difference between the two groups of working cavities until the air discharge moment. The mixed gas with different pressures in the cavity is discharged from the air discharge port, which increases the air discharge loss and flow loss. Based on this characteristic, the pressure in the asymmetric scroll compressor is always asymmetrically distributed in the whole working cycle. The unbalanced gas pressure causes the dynamic scroll plate to tilt unbalancedly, which causes friction on the end surface of the scroll plate, affects the stability during work, increases the power consumption and noise of the compressor, and causes the overall performance to decrease.

[0004] In order to overcome the problem of eccentric load caused by unbalanced air pressure in the working process of the asymmetric scroll compressor, the prior art provides two main means: one is to independently control the tooth head correction or cutting angle of the dynamic and static scroll plates to make the pressure of the two working cavities equal at the air discharge moment, so as to reduce the air discharge loss and instability. The second is to set two holes symmetrically with the rotation center of the dynamic scroll plate, so that the pressurized gas in the compression cavity forms two opposite torque through the two holes, so as to relieve the tilting torque of the scroll plate and increase the stability of the work.

[0005] However, the above two schemes still have some defects, for example: the asymmetric scroll compressor force imbalance caused by the partial load condition mainly appears on the outside, scheme one can only increase the stability of the center working chamber at the exhaust moment, and cannot solve the partial load condition of the asymmetric scroll compressor during operation, and the large correction angle of the dynamic and static scroll plates makes the center chamber have a large invalid volume, which increases the power, airflow pulsation and noise. Although scheme two can reduce the overturning moment through the opposite moment generated by the two holes, it can only slow down the partial load phenomenon during operation, but cannot completely eliminate the partial load phenomenon. In addition, the tooth heads of the dynamic and static scroll plates of the asymmetric scroll compressor in scheme two are not modified by equal content ratio, so the instability phenomenon and exhaust loss during the exhaust process still exist. SUMMARY

[0006] In order to solve the problem that the prior art cannot completely eliminate the inherent partial load phenomenon of the asymmetric scroll compressor, the application provides an asymmetric scroll compressor for eliminating partial load and application thereof.

[0007] The technical scheme provided by the application is as follows:

[0008] An asymmetric scroll compressor for eliminating partial load comprises a compression component composed of a dynamic scroll plate and a static scroll plate, and the compression component comprises two first working chambers and two second working chambers which are asynchronous suction. A gas flow exchange channel for communicating the first working chambers and the second working chambers is arranged in the static scroll plate. Two ports of the gas flow exchange channel are respectively located at two meshing points of the profile lines of the dynamic scroll plate and the static scroll plate when the main shaft rotation angle of the compression component is 0° or 180°. The shape, size and position of the two ports on the wall surface of the static scroll plate in the gas flow exchange channel satisfy that when the dynamic scroll plate rotates to 0° or 180°, the two ports are completely blocked by the profile lines of the dynamic scroll plate and the static scroll plate, and the gas flow exchange channel is closed. The two ports are opened and the gas flow exchange channel is kept open to balance the internal pressures of the first working chambers and the second working chambers at other rotation angles.

[0009] As a further improvement of the application, the gas flow exchange channel adopts a buried hole arranged in the static scroll plate; the two ends of the buried hole extend to the corresponding positions on the side of the static scroll plate provided with the profile line, thereby forming the required gas flow exchange channel.

[0010] As a further improvement of the application, the gas flow exchange channel adopts a V-shaped gas flow exchange channel or a U-shaped gas flow exchange channel.

[0011] As a further improvement of the application, the two ports of the gas flow exchange channel adopt circular through holes.

[0012] As a further improvement of the application, the position of the circular through hole satisfies that:

[0013] When the two meshing points of the profile lines of the orbiting scroll and the fixed scroll are located at the circular through holes at the main shaft rotation angle of 180°, the centers of the two circular through holes are arranged on two tangent directions of the base circle of the fixed scroll, and the first circle of the profile lines of the left and right fixed scrolls is tangent to the left and right circular through holes.

[0014] When the two meshing points of the profile lines of the orbiting scroll and the fixed scroll are located at the circular through holes at the main shaft rotation angle of 0°, the centers of the two circular through holes are arranged on two tangent directions of the base circle of the fixed scroll, and the second circle of the profile lines of the right fixed scroll is tangent to the right circular through hole.

[0015] As a further improvement of the present application, the distance between the outer side of the profile line of the orbiting scroll and the inner side of the second circle of the profile line of the fixed scroll at the main shaft rotation angle of 90° and 270° in the compression component is denoted as the base circle center distance r of the orbiting scroll and the fixed scroll; the tooth thickness of the profile lines of the orbiting scroll and the fixed scroll is denoted as t; and the diameter D of the circular through hole is less than or equal to the smaller value between r and t.

[0016] As a further improvement of the present application, the calculation formula of the base circle center distance r of the orbiting scroll and the fixed scroll is as follows:

[0017] ,

[0018] The calculation formula of the tooth thickness t of the profile lines of the orbiting scroll or the fixed scroll is as follows:

[0019] ;

[0020] In the above formula, a represents the base circle radius of the orbiting scroll or the fixed scroll; represents the start angle of the involute corresponding to the profile lines of the orbiting scroll and the fixed scroll.

[0021] As a further improvement of the present application, the gas flow exchange channel comprises two through holes penetrating the wall surface of the fixed scroll and an external pipe connecting the two through holes; and the pipe is arranged on the outward side of the fixed scroll.

[0022] As a further improvement of the present application, the pipe is a metal pipe; and the pipe is welded on the body of the fixed scroll or is an integral structure with the body of the fixed scroll.

[0023] The present application also includes an application of the asymmetric scroll compressor for eliminating the unbalanced load in a gas compression device, a refrigeration device or a power machine.

[0024] The present application also includes a gas compression device, a refrigeration device or a power machine, wherein the asymmetric scroll compressor for eliminating the unbalanced load is used in the above device or machine.

[0025] The application also provides a method for eliminating load imbalance of an asymmetric scroll compressor, which comprises the following steps: forming the gas flow exchange channel for communicating the first working cavity and the second working cavity in the asymmetric scroll compressor for eliminating load imbalance on the stationary scroll of the asymmetric scroll as described above, and the gas flow exchange channel can be an embedded hole or an external pipeline.

[0026] The technical scheme provided by the application has the following beneficial effects:

[0027] The asymmetric scroll compressor provided by the application can minimize load imbalance, and the two working cavities after processing can adaptively realize pressure balance in a working cycle, so that the tooth head of the dynamic scroll and the stationary scroll does not need to be separately modified and processed, and the cavitation degree of the central compression cavity is not increased.

[0028] The improvement scheme provided by the application can be applied to produce new products or modify existing equipment. The scheme does not need to make large changes to the scroll, and the bottom hole does not affect the original operation process of the scroll compressor. The new load imbalance elimination scheme does not need to add other complex valves and auxiliary accessories, and only relies on the gas flow exchange between different cavities in the operation process of the scroll compressor to achieve the expected effect.

[0029] The compression components in the compressor improved by the application not only retain the advantages of the asymmetric scroll, but also have the working characteristics of the symmetric scroll. The core components of the compressor can work continuously, and can produce effects immediately as long as there is a pressure difference between the two compression cavities. The performance is more reliable. BRIEF DESCRIPTION OF DRAWINGS

[0030] Figure 1 It is a schematic diagram of a complete working cycle of the asymmetric scroll compressor.

[0031] Figure 2 It is a schematic diagram of the asymmetric scroll compressor provided in embodiment 1 of the application and provided with the gas flow exchange channel.

[0032] Figure 3 It is a structural schematic diagram of the V-shaped gas flow exchange channel provided in embodiment 1 of the application.

[0033] Figure 4 It is a structural schematic diagram of the external pipeline type gas flow exchange channel provided in embodiment 1 of the application.

[0034] Figure 5 It is a hole opening position of the first gas flow exchange channel provided in embodiment 1 of the application; the (a) part and the (b) part respectively provide two state diagrams before and after the channel is blocked.

[0035] Figure 6This represents a complete working cycle of the compression component after adopting the first type of airflow exchange channel;

[0036] Figures (a) to (d) show the state diagrams of the dynamic and static scroll disk profiles when the spindle rotation angle is 0°, 90°, 180° and 270°, respectively.

[0037] Figure 7 The figure shows the opening position of the second type of airflow exchange channel provided in Embodiment 1 of the present invention; parts (a) and (b) in the figure respectively show two states before and after the channel is blocked.

[0038] Figure 8 This is a complete working cycle of the compression component after adopting the second type of airflow exchange channel;

[0039] Figures (a) to (d) show the state diagrams of the dynamic and static scroll disk profiles when the spindle rotation angle is 0°, 90°, 180° and 270°, respectively. Detailed Implementation

[0040] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0041] Example 1

[0042] This embodiment provides an asymmetric scroll compressor that eliminates off-center loading. The compressor's stationary scroll disk is equipped with an airflow exchange channel that adaptively switches its conduction state at corresponding stages of the compressor's complete working cycle. This airflow exchange channel allows for pressure balancing of the first and second working chambers during the intake and compression phases, thereby completely eliminating the off-center loading phenomenon caused by unbalanced pressure in the asymmetric scroll compressor.

[0043] A complete working cycle of the compression component of an asymmetric scroll compressor is as follows: Figure 1 As shown in the diagram, this work cycle includes four basic phases. Figure 1 Part (a) shows the initial positions of the stationary and moving scroll disks. After the moving scroll disk begins to rotate, it forms the first working chamber, which continuously draws in air during this process. When the moving scroll disk rotates to the position shown in the image... Figure 1 When the state shown in section (b) is reached, the first working chamber finishes intake, and the second working chamber is formed and begins intake. As the moving scroll continues to rotate to the state shown... Figure 1 When the state shown in section (c) is reached, the intake of the second working chamber ends. Next, as the moving scroll continues to rotate to the state shown... Figure 1 In the state shown in section (d), both working chambers begin to exhaust simultaneously.

[0044] The skilled in the art analyzes Figure 1 The cycle process of the asymmetric scroll compressor finds that the first working chamber and the second working chamber are two asymmetric working chambers, the volume and the suction start time of which are different, but the exhaust time of which is the same, so there is always a pressure asymmetry phenomenon in the compression process of the two working chambers, which is also the reason why the asymmetric scroll compressor will produce a load bias in the working process.

[0045] In view of this problem, as shown in Figure 2 The embodiment provides an asymmetric scroll compressor for eliminating load bias, which comprises a compression component composed of a moving scroll and a stationary scroll. The compression component comprises a first working chamber and a second working chamber which are two asynchronous suction chambers. The stationary scroll is provided with an air flow exchange channel for communicating the first working chamber and the second working chamber. The two ports of the air flow exchange channel are located at the two meshing points of the profile lines of the moving scroll and the stationary scroll when the main shaft rotation angle of the compression component is 0° or 180°. The shape, size and position of the two ports on the wall surface of the stationary scroll in the air flow exchange channel satisfy that when the moving scroll rotates to 0° or 180°, the two ports are completely blocked by the profile lines of the moving scroll and the stationary scroll, and the air flow exchange channel is closed. The two ports are open and the air flow exchange channel remains open to balance the internal pressures of the first working chamber and the second working chamber at other rotation angles.

[0046] By arranging the corresponding air flow exchange channel in the stationary scroll of the compression component, the cavity between the two working chambers formed can be adaptively communicated. When the first working chamber or the second working chamber starts to suck and the pressure in one of the working chambers is greater than that in the other working chamber, the gas in the working chamber with higher pressure will enter the other working chamber through the corresponding air flow exchange channel under the action of the pressure difference, according to the principle of gas communication device, the pressures in the two working chambers will eventually be consistent, so as to eliminate the phenomenon that the pressures of the two working chambers are not equal after the suction is completed, and the pressures of the two asymmetric working chambers are equal at all times during the compression process. In this way, the load bias phenomenon of the asymmetric scroll compressor is eliminated.

[0047] In actual application, the air flow exchange channel arranged in the compression component of the embodiment can be realized in two typical structures, one of which is shown in Figure 2 The air flow exchange channel adopts a buried hole arranged in the stationary scroll. The two ends of the buried hole extend to the corresponding positions on the side of the stationary scroll provided with the profile line, thereby forming the required air flow exchange channel. The scheme provided by the embodiment does not limit the shape of the air flow exchange channel, and in actual application, the air flow exchange channel can adopt a U-shaped air flow exchange channel as shown in Figure 2 , or a Figure 3The V-shaped gas flow exchange channel. The latter is easier to process, and can be drilled on the static scroll by simple machining equipment; it is more suitable for the modification of existing asymmetric scroll compressors to eliminate the unbalanced load problem of the corresponding products.

[0048] In order to facilitate production and processing, in addition to using the embedded hole method to form the required gas flow exchange channel, the required gas flow exchange channel can also be formed by an external pipeline. As shown in Figure 4 The gas flow exchange channel in the embodiment can also be composed of two through holes penetrating the wall surface of the static scroll and an external pipeline connecting the two through holes. The pipeline is arranged on the outer side of the static scroll. In actual application, the pipeline can be a metal pipeline; the pipeline is welded to the body of the static scroll or is an integral structure with the body of the static scroll. In actual application, the required two through holes can be machined on the corresponding position of the static scroll first, and then the required pipeline is installed at the corresponding position.

[0049] The gas flow exchange channel provided in the scheme of the embodiment only needs to be able to adaptively switch to the conducting state at the corresponding time, and does not need to limit the formation method and shape of the pipeline. In the two typical gas flow exchange channel formation methods given in the embodiment, both need to drill holes in the static scroll, and in actual application, the holes of the two ports of the gas flow exchange channel are circular through holes.

[0050] In actual application, the embodiment is designed by accurately designing the position of the hole to meet the requirement that it can be closed when the dynamic scroll rotates to 0° or 180°, and is open in other cases. In order to achieve the corresponding technical effect, the position of the circular through hole opened in the embodiment should use one of the following methods:

[0051] 1. The circular through holes are located at the two meshing points of the profile lines of the static scroll and the dynamic scroll at the main shaft angle of 180°. At this time, the centers of the two circular through holes are respectively arranged on the two tangent directions of the base circle of the static scroll in the horizontal direction, and the first circle inside the profile lines of the left and right static scrolls is tangent to the circular through holes.

[0052] 2. The circular through holes are located at the two meshing points of the profile lines of the static scroll and the dynamic scroll at the main shaft angle of 0°. At this time, the centers of the two circular through holes are respectively arranged on the two tangent directions of the base circle of the static scroll in the horizontal direction, and the second circle inside the profile lines of the right static scroll is tangent to the right side of the circular through hole.

[0053] In addition, in order to ensure that the profile lines of the static scroll and the dynamic scroll can completely close the hole of the gas flow exchange channel port when the dynamic scroll rotates to 0° or 180°, the diameter of the circular hole in the embodiment should meet:

[0054] When the spindle rotation angle in the compression component is 90° and 270°, the distance between the outer side of the profile of the moving scroll disk and the inner side of the second ring of the profile of the stationary scroll disk in the tangential direction is denoted as the base circle center distance r of the moving scroll disk and the stationary scroll disk; the tooth thickness of the profile of the moving scroll disk and the stationary scroll disk is denoted as t; the diameter D of the circular through hole is less than or equal to the smaller value between r and t.

[0055] To make the technical solution provided in this embodiment clearer, the following sections provide a detailed analysis of two typical airflow exchange channel opening positions.

[0056] Scenario 1:

[0057] Based on the working principle and meshing principle of the involute-type moving and stationary scroll plates, the meshing points M1 and M2 should be tangent to the base circles of the moving and stationary scroll plate profiles, and located outside the stationary scroll plate profile and inside the moving scroll plate profile. In the first case, the positions of the two openings (also called vents) on the stationary scroll plate in this embodiment are as follows: Figure 5 As shown, to ensure that the airflow exchange channel opening does not contact the first and second working chambers before the spindle rotation angle reaches 180°, and that the vent immediately contacts the two working chambers after the spindle rotation angle reaches 180° to generate gas exchange, the two holes are completely blocked when the moving scroll plate rotates to 180°, and open when the rotation angle is greater than 180°, thereby balancing the pressure of the two working chambers. In this embodiment, the opening position is at the two meshing points of the moving and stationary scroll plate profiles when the spindle rotation angle is 180°. Two tangents are selected along the horizontal direction of the stationary plate base circle, so that the center of the opening is on the tangent and the left side of the opening is tangent to the outer side of the first circle of the right stationary scroll plate profile.

[0058] When selecting the vent diameter D, to ensure that the moving scroll plate profile completely blocks the vent when the spindle rotation angle is 180° and does not obstruct the vent during subsequent operation as the spindle rotates, it is necessary to measure the distance between the inner side of the moving scroll plate profile and the outer side of the stationary scroll plate profile in the tangential direction at spindle rotation angles of 90° and 270°, which is the distance r between the base circles of the moving and stationary scroll plates. At this point, the distance r needs to be compared with the tooth thickness t of the moving and stationary scroll plate profiles. The formula for calculating the base circle center distance r of the moving and stationary scroll plates is as follows:

[0059] ,

[0060] The formula for calculating the profile tooth thickness t of a moving or stationary scroll disk is:

[0061] ;

[0062] In the above formula, 'a' represents the base circle radius of the moving or stationary scroll disk; represents the start angle of the involute corresponding to the dynamic scroll and the static scroll profile.

[0063] Assuming r = t, it can be calculated that , then:

[0064] (1) When r > t, that is, , only need to ensure that the vent hole D ≤ t.

[0065] (2) When r < t, that is, , only need to ensure that the vent hole D ≤ r.

[0066] (3) When r = t, that is, , only need to ensure that the vent hole D ≤ r or D ≤ t.

[0067] Based on the opening mode shown in Figure 5 , the working cycle of the compression component is as shown in Figure 6 , including the following processes:

[0068] Before the main shaft angle reaches 180°, as shown in Figure 6 (a) and Figure 6 (b) parts, the positions of the two vent holes are not in contact with the first working chamber and the second working chamber, so there is no gas exchange between the two working chambers. When the main shaft angle rotates to 180°, as shown in Figure 6 (c) part, the two vent holes are blocked by the dynamic scroll, and the gas exchange has not yet been performed. After the main shaft angle reaches 180°, the second working chamber stops inhaling, at this time, the outer first working chamber is compressed, and the second working chamber just completed inhaling forms a symmetrical situation about the center. At this time, the pressures of the two working chambers are not equal, so there is a risk of tilting of the dynamic scroll during movement. Then, with the continuous rotation of the main shaft, the first working chamber and the second working chamber are in contact with the two vent holes in the special position, and the gas exchange begins, until the exhaust is completed. This makes the pressures of the two working chambers equal, and the tilting risk of the scroll caused by the asymmetric pressure is also eliminated.

[0069] Case two:

[0070] In the second case, in order to ensure that the vent hole can be blocked by the moving dynamic disc and opened, so as to achieve the technical effect of pressure balance of the two working chambers by gas exchange at a specific position. The opening position of the embodiment makes the two holes be blocked at the initial moment, and the two holes are gradually opened to realize the pressure balance of the two working chambers with the movement of the dynamic disc.

[0071] Specifically, the opening position on the scroll disc is as shown in Figure 7As shown: the vent hole position is the meshing point of the dynamic and static scroll disc profile lines when the main shaft rotation angle is 0°, two tangent lines along the horizontal direction of the static disc base circle are selected, the center of the vent hole is on the tangent line and the right side of the vent hole is tangent to the inside of the second circle of the right static scroll disc profile line.

[0072] Correspondingly, when selecting the diameter D of the vent hole, in order to ensure that the dynamic scroll disc profile line can completely block the vent hole when the main shaft rotation angle is 0° and will not block the vent hole in the subsequent operation process with the rotation of the main shaft, the distance between the outside of the dynamic scroll disc profile line and the inside of the second circle of the static scroll disc profile line in the tangent direction when the main shaft rotation angle is 90° and 270° needs to be measured, that is, the center distance r of the dynamic and static scroll disc base circles. At this time, the distance r and the tooth thickness t of the dynamic and static scroll disc profile lines need to be compared. Wherein, the calculation formula of the center distance d of the dynamic and static scroll disc base circles is as follows:

[0073] ,

[0074] The calculation formula of the profile tooth thickness t of the dynamic scroll disc or the static scroll disc is:

[0075] ;

[0076] In the above formula, a represents the base circle radius of the dynamic scroll disc or the static scroll disc; represents the involute starting angle corresponding to the dynamic and static scroll disc profile lines.

[0077] Assuming r=t, it can be calculated that , then:

[0078] (1) When r>t, that is, , only need to ensure that the vent hole D≤t.

[0079] (2) When r , only need to ensure that the vent hole D≤r.

[0080] (3) When r=t, that is, , only need to ensure that the vent hole D≤r or D≤t.

[0081] Based on the opening mode shown in Figure 7 , the working cycle of the compression component is as shown in Figure 8 , including the following processes:

[0082] At the initial moment when the main shaft rotation angle is 0°, that is, in the (a) part of Figure 8 , the first working cavity completes suction, and the positions of the two vent holes are completely blocked by the dynamic disc. With the rotation of the main shaft to 90°, as shown in Figure 8As shown in part (b) of FIG. 1, the two vent holes start to communicate with the first working chamber and the second working chamber and gas exchange occurs, so that the pressure in the two working chambers is balanced, and then gas exchange always exists during the compression and exhaust of the two working chambers with equal pressure, and the tilting phenomenon of the orbiting scroll disappears.

[0083] Compared with case one, case two only adjusts the positions of the two vent holes, so that the timing of gas exchange of the two working chambers is changed; the working principles and the achievable technical effects are still completely consistent.

[0084] In summary, the embodiment solves the unbalanced load problem of the asymmetric scroll compressor by specific vent hole mode and position, and does not change the original structure size and operation mode. The asymmetric scroll compressor maintains high space utilization and low suction loss, and has the stable working characteristics of the symmetric scroll compressor; that is, the tooth heads of the orbiting scroll and the fixed scroll do not need to be modified to have the same volume ratio, so that the unbalanced load of the asymmetric scroll is greatly reduced, the pressures of the two asymmetric working chambers are equal, and the exhaust process is more stable. The embodiment scheme achieves unbalanced load elimination without adding auxiliary accessories and without external power driving; has high practical value, and is suitable for popularization and application.

[0085] Embodiment 2

[0086] The new asymmetric scroll compressor provided in embodiment 1 and adopting the improved gas flow exchange channel overcomes the unbalanced load problem of the existing product, and based on the new asymmetric scroll compressor, the embodiment further provides an application of the asymmetric scroll compressor for eliminating unbalanced load in a gas compression device, a refrigeration device or a power machine.

[0087] Correspondingly, the embodiment also provides a gas compression device, a refrigeration device or a power machine, and the asymmetric scroll compressor for eliminating unbalanced load as disclosed in embodiment 1 is used in the above device or machine.

[0088] Embodiment 3

[0089] On the basis of the scheme of embodiment 1, the embodiment further provides a method for eliminating unbalanced load of an asymmetric scroll compressor, and the method is to open the gas flow exchange channel for communicating the first working chamber and the second working chamber on the fixed scroll of the asymmetric scroll as disclosed in embodiment 1. In actual application, the gas flow exchange channel can adopt a built-in embedded hole or an externally connected pipeline.

[0090] The above only describes the preferred embodiments of the present application and should not be used to limit the present application, and any modification, equivalent replacement and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims

1. An asymmetric scroll compressor for eliminating off-center loading, comprising a compression component consisting of a moving scroll and a stationary scroll, the compression component including two asynchronous intake first working chambers and a second working chamber; characterized in that: An airflow exchange channel is provided in the stationary scroll plate to connect the first working chamber and the second working chamber; the two ports of the airflow exchange channel are located at the two meshing points of the profiles of the moving scroll plate and the stationary scroll plate when the main shaft rotation angle of the compression component is 0° or 180°; the two ports of the airflow exchange channel are circular through holes, and their positions are as follows: When the spindle rotation angle is 180°, at the two meshing points of the profiles of the moving scroll plate and the stationary scroll plate, the center of the circular through hole is set on the two tangent directions in the horizontal direction of the base circle of the stationary scroll plate, and the left side of the circular through hole is tangent to the inner side of the first circle of the profile of the right stationary scroll plate. Alternatively, at the two meshing points of the profiles of the moving scroll plate and the stationary scroll plate when the spindle rotation angle is 0°, the center of the circular through hole is set on the two tangent directions in the horizontal direction of the base circle of the stationary scroll plate, and the right side of the circular through hole is tangent to the inner side of the second circle of the profile of the right stationary scroll plate. Diameter of a circular through hole D Less than or equal to r and t The smaller of the two values, where the distance between the outer side of the profile of the moving scroll disk and the inner side of the second ring of the profile of the stationary scroll disk in the tangential direction when the spindle rotation angle in the compression component is 90° and 270°, is denoted as the base circle center distance between the moving scroll disk and the stationary scroll disk. r ; t Indicates the profile tooth thickness of a moving or stationary scroll disk; When the moving scroll plate rotates to 0° or 180°, the profiles in the passive scroll plate and the stationary scroll plate at both ports are completely blocked, and the airflow exchange channel is closed; at other rotation angles, the two ports are open, the airflow exchange channel is open, and the internal pressure of the first working chamber and the second working chamber is balanced.

2. The asymmetric scroll compressor for eliminating off-center loading as described in claim 1, characterized in that: The airflow exchange channel adopts a buried hole set inside the static vortex disk; the two ends of the buried hole extend to the corresponding positions on the side of the static vortex disk with the profile.

3. The asymmetric scroll compressor for eliminating off-center loading as described in claim 2, characterized in that: The airflow exchange channel adopts a V-shaped airflow exchange channel or a U-shaped airflow exchange channel.

4. The asymmetric scroll compressor for eliminating off-center loading as described in claim 1, characterized in that: The distance between the base circles of the moving and stationary scroll disks r The calculation formula is as follows: ， In the above formula, a Indicates the base circle radius of the moving or stationary scroll disk; Indicates the involute starting angle corresponding to the profiles of the moving and stationary scroll disks; Profile tooth thickness of moving or stationary scroll disk t The calculation formula is: 。 5. The asymmetric scroll compressor for eliminating off-center loading as described in claim 1, characterized in that: The airflow exchange channel includes two through holes penetrating the wall of the stationary vortex disk and an external pipe connecting the two through holes; the pipe is located on the outward-facing side of the stationary vortex disk.

6. The asymmetric scroll compressor for eliminating off-center loading as described in claim 5, characterized in that: The pipe is made of metal; the pipe is welded to the body of the stationary vortex disk or is an integral structure with the body of the stationary vortex disk.

7. The application of an asymmetric scroll compressor with off-center loading as described in any one of claims 1-6 in a gas compression device.

8. The application of an asymmetric scroll compressor with off-center loading as described in any one of claims 1-6 in a refrigeration device.

9. The application of an asymmetric scroll compressor for eliminating off-center loading as described in any one of claims 1-6 in power machinery.

10. A method for eliminating off-center load in an asymmetric scroll compressor, characterized in that: An airflow exchange channel for connecting the first working chamber and the second working chamber is formed on the stationary scroll of the asymmetric scroll compressor as described in any one of claims 1-6, wherein the airflow exchange channel adopts a built-in buried hole or an external pipe.

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