Anti-axial movement structure of compressor shaft and scroll compressor

Abstract

This invention provides a shaft anti-runaway structure for a compressor and a scroll compressor. The shaft anti-runaway structure includes a crankshaft, a moving scroll, a main support, a secondary support, an oil supply channel, and a thrust block. The moving scroll is equipped with a moving plate bearing, the main support is equipped with a main bearing, and the secondary support is equipped with a secondary bearing. The crankshaft is sequentially connected to the moving plate bearing, the main bearing, and the secondary bearing. The oil supply channel connects the compressor's exhaust chamber, the main bearing, the secondary bearing, and the moving plate bearing. The thrust block is disposed between the end face of the crankshaft and the secondary support. The shaft anti-runaway structure of this invention uses high-pressure oil return from the exhaust chamber as power to apply a fixed-directional axial load to the shaft, causing it to rotate close to the end face of the thrust block, thereby preventing axial runaway during compressor operation and improving operational stability and overall operating efficiency.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a compressor shaft anti-runaway structure and a scroll compressor. Background Technology

[0002] Ideally, when the rotor and stator are in the same axial position, the shaft system is not subject to axial force. However, due to factors such as the precision of component manufacturing and assembly, as well as the influence of vibration and swaying during vehicle operation, the shaft system will inevitably bear axial loads, and the direction of the load is uncertain. This uncertain axial movement will cause the shaft system to axially move, leading to increased vibration and collisions with other components, thus increasing the risk of failure.

[0003] A scroll compressor has three bearings inside: a main bearing and a secondary bearing for support, and a moving disc bearing for power transmission. Traditional scroll compressors mostly use rolling bearings. Sliding bearings have almost unlimited lifespan under sufficient oil film lubrication conditions, and their operating noise is much lower than that of compressors using rolling bearings. At the same time, they also have a significant cost advantage over rolling bearings.

[0004] However, since sliding bearings cannot withstand axial loads, the usual practice is to use rolling bearings to bear axial loads in the main or auxiliary bearings. When the axial load is large, angular thrust bearings or even thrust bearings are required, which will greatly increase the manufacturing cost of the compressor.

[0005] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of the present invention, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0006] To address the problems in the prior art, the present invention aims to provide a compressor shaft anti-axial movement structure and a scroll compressor. This compressor shaft anti-axial movement structure effectively prevents axial movement during compressor operation, thereby improving operational stability and overall operating efficiency.

[0007] The first aspect of the present invention provides a compressor shaft anti-runaway structure, including a crankshaft, a moving scroll plate, a main support, a secondary support, an oil supply channel, and a thrust block;

[0008] The moving scroll plate is equipped with a moving plate bearing, the main support is equipped with a main bearing, and the auxiliary support is equipped with an auxiliary bearing;

[0009] The crankshaft is connected in sequence to the moving disc bearing, the main bearing, and the auxiliary bearing;

[0010] The oil supply channel connects the compressor's exhaust chamber, the main bearing, the auxiliary bearing, and the moving disc bearing;

[0011] The thrust block is disposed between the end face of the crankshaft and the sub-support; and

[0012] The outer diameter of the moving disc bearing is d. 动 The outer diameter of the secondary bearing is d. 副 ,satisfy:

[0013] d 动 >d 副 .

[0014] According to a first aspect of the invention, the thrust block has a groove structure on the side facing the crankshaft end face.

[0015] According to a first aspect of the invention, the groove structure is at least partially in communication with the secondary bearing cavity accommodating the secondary bearing.

[0016] According to a first aspect of the invention, the groove structure is cross-shaped.

[0017] According to a first aspect of the invention, the main bearing, the secondary bearing, and / or the moving disc bearing are sliding bearings.

[0018] According to a first aspect of the invention, the outer diameter of the moving disc bearing is d. 动 The outer diameter of the secondary bearing is d. 副 , satisfying: d 动 With d 副 The difference is between 0.5mm and 3.0mm.

[0019] A second aspect of the present invention provides a scroll compressor, including the aforementioned compressor shaft anti-runaway structure.

[0020] The shaft anti-axial movement structure of the present invention uses the high-pressure return oil in the exhaust chamber as power to apply a fixed-directional axial load to the shaft system, causing it to rotate close to the end face of the thrust block, thereby preventing axial movement during compressor operation and improving operational stability and overall operating efficiency. Attached Figure Description

[0021] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. Other features, objects, and advantages of the invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings. It is obvious that the drawings described below are merely some embodiments of the invention, and those skilled in the art can obtain other drawings based on these drawings without inventive effort. Furthermore, the drawings are merely illustrative diagrams of this disclosure and are not necessarily drawn to scale. The same reference numerals in the drawings denote the same or similar parts, and therefore repeated descriptions of them will be omitted. Some block diagrams shown in the drawings are functional entities and do not necessarily correspond to physically or logically independent entities.

[0022] Figure 1 This is a schematic diagram of a compressor shaft anti-tracking structure according to an embodiment of the present invention; and

[0023] Figure 2 This is a schematic diagram of the thrust block according to an embodiment of the present invention. Detailed Implementation

[0024] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the examples set forth herein; rather, they are provided so that this disclosure will be more comprehensive and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The described features, structures, or characteristics may be combined in any suitable manner in one or more embodiments.

[0025] In this specification, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics represented in connection with that embodiment or example, which are included in at least one embodiment or example of this specification. Furthermore, the specific features, structures, materials, or characteristics represented may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples represented in this specification, as well as the features of different embodiments or examples.

[0026] Throughout this specification, when it is said that a device is "connected" to another device, this includes not only "direct connection" but also "indirect connection" by placing other components in between. Terms indicating relative space, such as "front," "back," "up," and "down," are used to more easily explain the relationship of one device relative to another illustrated in the figures. These terms refer not only to their meaning in the figures but also to other meanings or operations of the device in use. For example, if the device in the figures is flipped, a device previously described as "below" another device may now be described as "above" another device. Therefore, the exemplary term "down" includes both "up" and "below." The device may be rotated 90° or other angles, and the terms representing relative space are interpreted accordingly.

[0027] Although the terms first, second, etc., are used in some instances herein to refer to various elements, these elements should not be limited by these terms. These terms are used only to distinguish one element from another. For example, first interface and second interface, etc., are used. Furthermore, as used herein, the singular forms “a,” “an,” and “the” are intended to also include the plural forms unless the context indicates otherwise. It should be further understood that the terms “comprising,” “including,” indicate the presence of the stated feature, step, operation, element, component, item, kind, and / or group, but do not exclude the presence, occurrence, or addition of one or more other features, steps, operations, elements, components, items, kinds, and / or groups. The terms “or” and “and / or” as used herein are interpreted as inclusive, or mean any one or any combination thereof. Thus, “A, B, or C” or “A, B, and / or C” means “any one of the following: A; B; C; A and B; A and C; B and C; A, B, and C.” Exceptions to this definition will only occur if the combination of elements, functions, steps, or operations is inherently mutually exclusive in some way.

[0028] Undefined terms, including technical and scientific terms used herein, shall have the same meaning as commonly understood by one of ordinary skill in the art to which this specification pertains. Terms defined in commonly used dictionaries shall be further interpreted as having a meaning consistent with relevant technical literature and the content of this present instruction, and shall not be over-interpreted as having an ideal or overly formulaic meaning unless otherwise defined.

[0029] To address the existing technical problems, this invention provides a compressor shaft anti-runaway structure and a scroll compressor. The shaft anti-runaway structure includes a crankshaft, a moving scroll, a main support, a secondary support, an oil supply channel, and a thrust block. The moving scroll is equipped with a moving disc bearing, the main support with a main bearing, and the secondary support with a secondary bearing. The crankshaft is sequentially connected to the moving disc bearing, the main bearing, and the secondary bearing. The oil supply channel connects the compressor's exhaust chamber, the main bearing, and the secondary bearing. The thrust block is disposed between the end face of the crankshaft and the secondary support. This invention's shaft anti-runaway structure uses high-pressure oil return from the exhaust chamber as power to apply a fixed-directional axial load to the shaft, causing it to rotate close to the end face of the thrust block, thereby preventing axial runaway during compressor operation and improving operational stability and overall operating efficiency.

[0030] The following description, in conjunction with the accompanying drawings and specific embodiments, further illustrates the compressor shaft anti-runaway structure and the structure of the scroll compressor of the present invention. It should be understood that the specific embodiments are not intended to limit the scope of protection of the present invention.

[0031] Figure 1 This is a schematic diagram of a compressor shaft anti-jamming structure according to an embodiment of the present invention. Specifically, the compressor shaft anti-jamming structure includes a crankshaft 1, a moving scroll 2, a main support 3, a secondary support 4, and an oil supply channel. The moving scroll 2 has a moving scroll bearing seat 21 on the side facing away from the scroll, and the moving scroll bearing seat 21 can accommodate a moving scroll bearing 6. The main support is provided with a main bearing 5, and the secondary support is provided with a secondary bearing 7. The crankshaft 1 is sequentially connected to the moving scroll bearing 6, the main bearing 5, and the secondary bearing 7. The oil supply channel connects the compressor's exhaust chamber, the main bearing 5, the moving scroll bearing 6, and the secondary bearing 7. The thrust block 8 is disposed between the end face of the crankshaft 1 and the secondary support 4. Of course, wear-resistant shims 9 can be provided between the moving scroll 2 and the main support 3, which will not be elaborated here. The main bearing 5, the secondary bearing 7, and / or the moving scroll bearing 6 can all be sliding bearings. The advantages of sliding bearings are that they use surface contact, resulting in high load-bearing capacity, fewer parts affecting accuracy, and the ability to achieve very high rotational accuracy. Through the oil supply channel, each bearing can be lubricated with oil, meaning that an oil film on the working surface of each bearing provides vibration damping, buffering, and noise reduction. Therefore, the operation is smooth, with low noise, and the bearings, operating under fluid friction conditions, have a low coefficient of friction, minimal wear, and a long service life. It should be noted that the outer diameter d of the moving disc bearing 6 of this invention... 动 The outer diameter d of the secondary bearing 7 is greater than 副 .

[0032] The following is further... Figure 1The embodiment illustrates the structure of the oil supply channel, which includes a first channel 31 passing through the main support 3, a second channel 51 passing through the main bearing 5, a crankshaft radial oil hole 11, a first crankshaft axial oil hole 12, and a second crankshaft axial oil hole 13; the first channel 31, the second channel 51, and the crankshaft radial oil hole 11 are sequentially connected, and the crankshaft radial oil hole 11, the first crankshaft axial oil hole 12, and the second crankshaft axial oil hole 13 are interconnected. The first crankshaft axial oil hole 12 and the second crankshaft axial oil hole 13 are both axial oil holes disposed inside the crankshaft 1. In the first embodiment, the crankshaft radial oil hole 11, the first crankshaft axial oil hole 12, and the second crankshaft axial oil hole 13 are T-shaped. It should be noted that the first crankshaft axial oil hole 12 is connected to the moving plate bearing 6; the second crankshaft axial oil hole 13 is connected to the auxiliary bearing 7. The first and second are used to define different oil holes connected to the moving plate bearing 6 and the auxiliary bearing 7. In some embodiments, the first crankshaft axial oil hole 12 and the second crankshaft axial oil hole 13 can be an extended oil hole. After the high-pressure return oil from the exhaust chamber returns from the stationary plate return oil hole, it enters the second channel 51 of the main bearing 5 through the first channel 31 on the main support 3, and then connects with the first crankshaft axial oil hole 12 and the second crankshaft axial oil hole 13 through the crankshaft radial oil hole 11 of the crankshaft 1. When the return oil enters the second channel 51 of the main bearing 5 and the crankshaft radial oil hole 11 of the crankshaft 1, a portion of the oil lubricates the gap between the crankshaft 1 and the main bearing 5 at the connection between the two. Since both sides of the main bearing 5 are low-pressure areas, the return oil in the gap between the crankshaft 1 and the main bearing 5 will be throttled and depressurized, causing another portion of the oil to flow out to both sides, that is, through the first crankshaft axial oil hole 12 and the second crankshaft axial oil hole 13, respectively, to lubricate the moving disc bearing 651 and the auxiliary bearing 7. Of course, the structure of the oil supply channel is not limited to the above description; the structures of the main bearing 5, the moving disc bearing 6, and the auxiliary bearing 7 are all acceptable.

[0033] Since the oil supply channel connects the compressor's exhaust chamber, the main bearing 5, the moving disc bearing 6, and the auxiliary bearing 7, when the outer diameter d of the moving disc bearing 6... 动 The outer diameter d of the secondary bearing 7 is greater than 副 The high-pressure oil in the back pressure chamber of the bearing housing of the moving disc bearing 6, located within the moving scroll disc 2, generates a rightward axial thrust on the shaft system, while the back pressure chamber of the auxiliary bearing generates a leftward axial thrust on the shaft system. The outer diameter of the moving disc bearing 6 is d. 动 The outer diameter of the secondary bearing 7 is d. 副 d 副 Design value ratio d 动 Slightly smaller, with:

[0034] F=(Ps-Pd)*π((d 动 / 2) 2 -(d副 / 2) 2 ).

[0035] F is the thrust along the axis, Pd is the exhaust chamber pressure, and Ps is the intake chamber pressure. Since d 动 >d 副 This generates axial thrust.

[0036] Preferably, the outer diameter d of the moving disc bearing 动 and the outer diameter d of the secondary bearing 副 Satisfy: d 动 With d 副 The difference is between 0.5mm and 3.0mm. This invention utilizes the high-pressure oil return from the exhaust chamber and the difference in outer diameter between the moving bearing and the auxiliary bearing to generate an axial thrust in the fixed direction of the shaft system, thereby preventing axial movement during compressor operation and improving operational stability.

[0037] Furthermore, in some embodiments, the thrust block 8 has a groove structure 81 on the side facing the crankshaft 1 end face. The groove structure can at least partially communicate with the secondary bearing cavity accommodating the secondary bearing, such as the groove structure 81 being in the shape of a straight line or a cross. Figure 2 This is a schematic diagram of the thrust block structure according to an embodiment of the present invention. The groove structure 81 is cross-shaped. When the lubricating oil passes through the groove structure 81, part of the lubricating oil enters the gap between the contact surface of the crankshaft 1 and the thrust block 8, thereby forming a lubricating oil film and reducing wear. Another part of the lubricating oil enters the mating gap between the crankshaft 1 and the secondary bearing 7 through the groove structure 81, thereby lubricating the secondary bearing 7.

[0038] The present invention also provides a scroll compressor, including the compressor shaft anti-axial movement structure, wherein the high-pressure oil return from the exhaust chamber and the outer diameter difference between the moving bearing and the auxiliary bearing are used to form an axial thrust in the fixed direction of the shaft system, thereby preventing axial movement during compressor operation and improving operational stability.

[0039] The above description, in conjunction with specific preferred embodiments, provides a further detailed explanation of the present invention and should not be construed as limiting the specific implementation of the invention to these descriptions. It will be apparent to those skilled in the art that this application is not limited to the details of the above exemplary embodiments, and that the application can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of this application is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be embraced within this application. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A compressor shaft anti-tracking structure, characterized in that, This includes the crankshaft, moving scroll plate, main support, auxiliary support, oil supply channel, and thrust block; The moving scroll plate is equipped with a moving plate bearing, the main support is equipped with a main bearing, and the auxiliary support is equipped with an auxiliary bearing; The crankshaft is connected in sequence to the moving disc bearing, the main bearing, and the auxiliary bearing; The oil supply channel connects the compressor's exhaust chamber, the main bearing, the auxiliary bearing, and the moving disc bearing; The thrust block is disposed between the end face of the crankshaft and the sub-support. The thrust block has a groove structure on the side facing the crankshaft end face, and the groove structure communicates at least partially with the sub-bearing cavity accommodating the sub-bearing. The outer diameter of the moving disc bearing is d. 动 The outer diameter of the secondary bearing is d. 副 ,satisfy: d 动 ﹥d 副 ; d 动 With d 副 The difference is between 0.5mm and 3.0mm.

2. The compressor shaft anti-tracking structure according to claim 1, characterized in that, The groove structure is cross-shaped.

3. The compressor shaft anti-tracking structure according to claim 1, characterized in that, The main bearing, the secondary bearing, and / or the moving disc bearing are sliding bearings.

4. A scroll compressor, characterized in that, The compressor shaft anti-slip structure includes any one of claims 1 to 3.

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