Compressor scroll structure

Abstract

The utility model relates to scroll compressor technical field especially, it relates to a compressor scroll plate structure, be located inside compressor casing, and the compressor casing is connected with the air inlet pipe and the exhaust pipe, its characterized in that, include: static scroll plate, fixedly set in the compressor casing inside, and the one end of air inlet pipe passes through compressor casing and is linked with the air inlet of static scroll plate, and the one end of exhaust pipe passes through compressor casing and is linked with the exhaust port of static scroll plate, and static scroll plate is equipped with static scroll tooth, and the wall thickness of static scroll tooth gradually increases from the outer ring to the center, motor, set up in the compressor casing inside, and the output end of motor is connected with the crankshaft, dynamic scroll plate, set up in the compressor casing inside, and dynamic scroll plate is transmission connection with the one end of crankshaft away from motor, and dynamic scroll plate is equipped with the dynamic scroll tooth of meshing with static scroll tooth, and the wall thickness of dynamic scroll tooth gradually increases from the outer ring to the center.

Description

Technical Field

[0001] This utility model relates to the field of scroll compressor technology, and in particular to a compressor scroll disk structure. Background Technology

[0002] Scroll compressors are widely used in refrigeration, air conditioning, heat pumps, and aerodynamics due to their compact structure, stable operation, and high energy efficiency, playing a crucial role in industrial production and daily life. The scroll plate, as its core component, has a scroll tooth structure design that directly determines the compressor's performance, lifespan, and reliability. However, the uniform wall thickness tooth design commonly used in existing technologies cannot accommodate the stress and temperature differences from the outer ring to the center of the scroll tooth—the central region has the highest pressure and temperature. The uniform wall thickness structure leads to severe stress concentration at the tooth root in this area, which is prone to fatigue cracks under long-term complex load cycles, eventually causing scroll tooth fracture failure. This not only shortens the scroll plate's lifespan but also reduces the compressor's operational reliability, increases the risk of failure, and raises maintenance costs.

[0003] The industry's demand for high performance, long life and high reliability of scroll compressors is increasing. The existing equal wall thickness tooth design can no longer meet the requirements of practical applications. Therefore, optimizing and improving the structural design of scroll teeth to solve the failure problem caused by stress concentration has become an urgent technical problem to be solved in the field of scroll compressor technology. Utility Model Content

[0004] To address the technical problems existing in the background art, this utility model proposes a compressor scroll disk structure.

[0005] To achieve the above objectives, this utility model provides the following technical solution:

[0006] A compressor scroll structure, located inside the compressor housing, with an intake pipe and an exhaust pipe connected to the compressor housing, characterized in that it comprises:

[0007] A stationary scroll plate is fixedly installed inside the compressor housing. One end of the intake pipe passes through the compressor housing and is connected to the intake port of the stationary scroll plate. One end of the exhaust pipe passes through the compressor housing and is connected to the exhaust port of the stationary scroll plate. The stationary scroll plate is provided with stationary scroll teeth, and the wall thickness of the stationary scroll teeth gradually increases from the outer ring to the center.

[0008] The motor is located inside the compressor housing, and the output end of the motor is connected to the crankshaft;

[0009] The moving scroll is located inside the compressor housing. The moving scroll is connected to the crankshaft at the end away from the motor. The moving scroll is provided with moving scroll teeth that mesh with the stationary scroll teeth. The wall thickness of the moving scroll teeth gradually increases from the outer ring to the center.

[0010] The moving scroll and the stationary scroll cooperate to form a sealed chamber for compressing fluid, and the motor can drive the moving scroll to rotate eccentrically relative to the stationary scroll via the crankshaft.

[0011] Furthermore, the wall thickness of the stationary vortex tooth and the moving vortex tooth increases continuously and uniformly.

[0012] Furthermore, both the stationary vortex tooth and the moving vortex tooth have a rounded transition area at their tooth roots, and the radius of the rounded corner gradually increases from the outer circle to the center.

[0013] Furthermore, the exhaust port of the static vortex disk is located in its central region.

[0014] Furthermore, the crankshaft and the moving scroll are connected by an eccentric bearing.

[0015] Furthermore, a conical diffuser section is provided at the exhaust port, and the large end of the diffuser section is connected to the exhaust pipe.

[0016] Furthermore, the base plate of the static vortex disk and / or the dynamic vortex disk is provided with reinforcing ribs, and the distribution density of the reinforcing ribs gradually increases from the outer ring to the center.

[0017] Compared with the prior art, the beneficial effects of this utility model are:

[0018] Compared with existing technologies, the design of the static and dynamic scroll teeth, which gradually thickens from the outer ring to the center, precisely adapts to the differences in operating conditions, such as low pressure / low temperature on the outer ring versus high pressure / high temperature in the center. The thicker wall in the central region can withstand higher pressure and resist higher temperatures, fundamentally reducing stress concentration at the tooth root in the central region. This solves the problem of easy breakage at the center of existing teeth with uniform wall thickness, extends the service life of the scroll plate, and improves the reliability of the compressor. The continuous and uniform wall thickness variation avoids sudden changes in stress, further reducing local stress. The gradually changing radius tooth root fillet specifically disperses the stress at the central tooth root, making it more fatigue-resistant. The gradually increasing density reinforcing ribs enhance the rigidity of the base plate, prevent leakage in the sealed chamber, and further ensure the energy efficiency of the compressor. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the compressor scroll disk structure proposed in this utility model;

[0020] Figure 2 This is a top view of the compressor scroll structure proposed in this utility model;

[0021] Figure 3 This is a schematic diagram of the moving scroll plate in the compressor scroll plate structure proposed in this utility model;

[0022] Figure 4This is a schematic diagram of the diffuser section in the compressor scroll structure proposed in this utility model;

[0023] Figure 5 This is a schematic diagram of the ribs in the compressor scroll structure proposed in this utility model.

[0024] In the diagram: 1-compressor housing, 101-intake pipe, 102-exhaust pipe, 2-motor, 3-crankshaft, 4-stationary scroll plate, 401-intake port, 402-exhaust port, 403-stationary scroll teeth, 5-moving scroll plate, 501-moving scroll teeth, 6-reinforcing rib. Detailed Implementation

[0025] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0026] like Figures 1-5 As shown, this embodiment provides a compressor scroll structure located inside the compressor housing 1. The compressor housing 1 is connected to an intake pipe 101 and an exhaust pipe 102. The structure is characterized by comprising:

[0027] The stationary scroll plate 4 is fixedly installed inside the compressor housing 1. One end of the intake pipe 101 passes through the compressor housing 1 and is connected to the intake port 401 of the stationary scroll plate 4. One end of the exhaust pipe 102 passes through the compressor housing 1 and is connected to the exhaust port 402 of the stationary scroll plate 4. The stationary scroll plate 4 is provided with stationary scroll teeth 403. The wall thickness of the stationary scroll teeth 403 gradually increases from the outer ring to the center.

[0028] Motor 2 is located inside compressor housing 1, and crankshaft 3 is connected to the output end of motor 2;

[0029] The moving scroll 5 is located inside the compressor housing 1. The moving scroll 5 is connected to the end of the crankshaft 3 away from the motor 2. The moving scroll 5 is provided with moving scroll teeth 501 that mesh with stationary scroll teeth 403. The wall thickness of the moving scroll teeth 501 gradually increases from the outer ring to the center.

[0030] The moving scroll 5 and the stationary scroll 4 cooperate to form a sealed chamber for compressing fluid. The motor 2 can drive the moving scroll 5 to rotate eccentrically relative to the stationary scroll 4 through the crankshaft 3.

[0031] Overall, the compressor housing 1 has an intake pipe 101 fixedly connected to it for introducing the fluid to be compressed, and an exhaust pipe 102 for discharging the compressed fluid. The stationary scroll plate 4 is fixedly installed inside the compressor housing 1 by bolts or welding. One side of the plate has an intake port 401 adapted to the flow path of the fluid to be compressed, and the other side has an exhaust port 402 adapted to the flow path of the compressed high-pressure fluid. One end of the intake pipe 101 passes through the side wall of the compressor housing 1 and is sealed to the intake port 401 of the stationary scroll plate 4 to prevent fluid leakage. One end of the exhaust pipe 102 passes through the side wall of the compressor housing 1 and is sealed to the exhaust port 402 of the stationary scroll plate 4. The stationary scroll plate 4 has stationary scroll teeth 403 integrally formed on the side facing the moving scroll plate 5. The stationary scroll teeth 403... The wall thickness gradually increases from the outer ring to the center. The motor 2 is fixedly mounted inside the compressor housing 1 by a bracket. The output end of the motor 2 is fixedly connected to the crankshaft 3 by a coupling or key. When the motor 2 is working, it can drive the crankshaft 3 to rotate around its own axis. The moving scroll 5 is located inside the compressor housing 1 and is arranged opposite to the stationary scroll 4. The moving scroll 5 has a mounting hole on the side facing the crankshaft 3, and it is connected to the end of the crankshaft 3 away from the motor 2 through the mounting hole. The moving scroll 5 has a moving scroll tooth 501 integrally formed on the side facing the stationary scroll 4. The spiral trajectory of the moving scroll tooth 501 matches the stationary scroll tooth 403 and can mesh with the stationary scroll tooth 403. At the same time, the wall thickness of the moving scroll tooth 501 also gradually increases from the outer ring to the center.

[0032] After the moving scroll 5 and the stationary scroll 4 mesh, multiple sealed chambers for compressing fluid are formed between their scroll teeth. When the motor 2 is working, the moving scroll 5 is driven to rotate eccentrically relative to the stationary scroll 4 through the crankshaft 3, so that the sealed chambers gradually shrink from the outer ring to the center, realizing the intake, compression and discharge of fluid.

[0033] like Figures 2-3 As shown, in this embodiment, the wall thickness of the stationary vortex tooth 403 and the moving vortex tooth 501 increases continuously and uniformly.

[0034] Specifically, the wall thickness of the stationary volute 403 and the moving volute 501 increases continuously and uniformly. Through CNC milling or precision casting, the wall thickness of the stationary volute 403 and the moving volute 501 changes linearly from the outer ring starting end to the center end, and the wall thickness transition surface has no steps or abrupt changes. Compared with discontinuous wall thickness changes, continuous and uniform wall thickness gradients can make the force on the volute teeth transition smoothly from the outer ring to the center, avoiding local stress concentration points caused by abrupt changes in wall thickness, further reducing the fatigue risk of the tooth root in the central region, and ensuring the compatibility between the volute teeth and the sealing chamber, avoiding leakage of the sealing chamber due to abrupt changes in wall thickness.

[0035] like Figures 2-3As shown, in this embodiment, the root portions of both the stationary vortex tooth 403 and the moving vortex tooth 501 are provided with rounded transition areas, and the radius of the rounded corners gradually increases from the outer circle to the center.

[0036] Specifically, the feature added is that "both the root portions of the stationary vortex tooth 403 and the moving vortex tooth 501 are provided with rounded transition areas, and the radius of the rounded corners gradually increases from the outer ring to the center": The outer ring root radius of the stationary vortex tooth 403 and the moving vortex tooth 501 is 1.5mm, and the center root radius is 3mm, with the radius gradually changing from the outer ring to the center; the root is a key part of stress concentration, especially the central region where the stress is higher; increasing the radius of the rounded corners in sync with the increase of stress can more accurately disperse the concentrated stress in the central region of the root. Compared with rounded corners of equal radius, this can reduce the stress in the central region of the root and significantly improve the fatigue fracture resistance of the vortex tooth.

[0037] like Figure 2 and Figure 4 As shown, in this embodiment, the exhaust port 402 of the static vortex disk 4 is located in its central region.

[0038] Specifically, the feature of "the exhaust port 402 of the stationary vortex disk 4 being located in its central region" is added: the exhaust port 402 of the stationary vortex disk 4 is located in the central end region of the stationary vortex tooth 403, and the axis of the exhaust port 402 coincides with the central axis of the stationary vortex disk 4. The inner diameter of the exhaust port 402 is adapted to the minimum volume of the central sealing chamber. The sealing chamber shrinks from the outer ring to the center, and finally forms a high-pressure fluid in the central region. By setting the exhaust port 402 in the central region, the high-pressure fluid can be discharged directly from the end of the sealing chamber, reducing the flow path of the fluid inside the vortex disk, reducing exhaust resistance and energy loss, and at the same time avoiding additional impact of the high-pressure fluid on the vortex tooth in the non-central region, further protecting the vortex tooth structure.

[0039] like Figure 1 As shown, in this embodiment, the crankshaft 3 and the moving scroll 5 are connected by an eccentric bearing.

[0040] Specifically, the feature of "the crankshaft 3 and the moving scroll 5 being connected by an eccentric bearing" is added: the end of the crankshaft 3 away from the motor 2 is provided with an eccentric shaft section, the inner ring of the eccentric bearing is interference-fitted with the eccentric shaft section of the crankshaft 3, and the outer ring is transition-fitted with the mounting hole of the moving scroll 5, and retaining rings are provided on both sides of the eccentric bearing; the eccentric bearing can precisely control the eccentric rotation trajectory of the moving scroll 5, avoiding collisions or excessive gaps between the moving scroll 5 and the stationary scroll 4 during movement, thereby ensuring the sealing performance of the sealed chamber; at the same time, the rolling friction of the bearing replaces the traditional sliding friction, reducing the wear of the crankshaft 3 and the moving scroll 5, improving transmission efficiency, and extending the service life of both.

[0041] like Figure 4As shown, in this embodiment, a conical diffuser section is provided at the exhaust port 402, and the large end of the diffuser section is connected to the exhaust pipe 102.

[0042] Specifically, the feature added is that "a conical diffuser section is provided at the exhaust port 402, and the large end of the diffuser section is connected to the exhaust pipe 102": The diffuser section is a conical channel integrally formed in the exhaust port 402 of the static vortex disk 4. Its small end is connected to the central sealing chamber, and its large end is sealed to the exhaust pipe 102 through a flange. After the compressed high-pressure fluid enters the conical diffuser section, the flow velocity decreases as the cross-section of the channel increases, and the pressure is further increased. This can reduce the pressure loss of the fluid during the exhaust process, make the compressor exhaust pressure more stable, and at the same time reduce the noise of the fluid impacting the exhaust pipe 102, thus improving the stability of equipment operation.

[0043] like Figure 5 As shown, in this embodiment, the base plate back of the stationary vortex disk 4 and / or the moving vortex disk 5 is provided with reinforcing ribs 6, and the distribution density of the reinforcing ribs 6 gradually increases from the outer ring to the center.

[0044] Specifically, the feature of adding "the back of the base plate of the static vortex disk 4 and / or the dynamic vortex disk 5 is provided with reinforcing ribs 6, and the distribution density of the reinforcing ribs 6 gradually increases from the outer ring to the center" is added: the reinforcing ribs 6 are strip-shaped protrusions or ring-shaped protrusions perpendicular to the back of the base plate, and can be integrally cast with the base plate.

[0045] When the ribs are strip-shaped protrusions: the reinforcing ribs 6 on the back of the base plate of the stationary vortex disk 4 are radially distributed, with one rib every 30° in the outer ring area and one rib every 15° in the central area. The reinforcing ribs 6 on the back of the base plate of the moving vortex disk 5 are arranged in the same way as those of the stationary vortex disk 4.

[0046] When it is an annular protrusion: the reinforcing ribs 6 on the back of the base plate of the stationary vortex disk 4 are distributed in a ring, and the distance between two adjacent reinforcing ribs 6 gradually decreases from the outer ring to the central area; the reinforcing ribs 6 on the back of the base plate of the moving vortex disk 5 are arranged in the same way as the stationary vortex disk 4.

[0047] The reinforcing ribs 6 on the back of the base plate can enhance the rigidity of the base plate and prevent it from deforming due to pressure load during compressor operation. The base plate in the central area bears greater pressure. By increasing the distribution density of the reinforcing ribs 6, the deformation resistance of the base plate in the central area can be specifically improved, ensuring the parallelism of the static and dynamic scroll plates 5, thereby ensuring the sealing performance of the sealed chamber and preventing energy efficiency reduction caused by fluid leakage.

[0048] Of course, those skilled in the art will recognize that this invention is not limited to the details of the exemplary embodiments described above, but also includes the same or similar structures that can be implemented in other specific forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of this invention 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 included within this invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0049] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0050] The technologies, shapes, and structures not described in detail in this utility model are all known technologies.

Claims

1. A compressor scroll structure, located inside a compressor housing (1), wherein an intake pipe (101) and an exhaust pipe (102) are connected to the compressor housing (1), characterized in that, include: A stationary scroll plate (4) is fixedly installed inside the compressor housing (1). One end of the intake pipe (101) passes through the compressor housing (1) and is connected to the intake port (401) of the stationary scroll plate (4). One end of the exhaust pipe (102) passes through the compressor housing (1) and is connected to the exhaust port (402) of the stationary scroll plate (4). The stationary scroll plate (4) is provided with stationary scroll teeth (403), and the wall thickness of the stationary scroll teeth (403) gradually increases from the outer ring to the center. The motor (2) is located inside the compressor housing (1), and the output end of the motor (2) is connected to the crankshaft (3); The moving scroll (5) is located inside the compressor housing (1). The moving scroll (5) is connected to the crankshaft (3) at the end away from the motor (2). The moving scroll (5) is provided with moving scroll teeth (501) that mesh with the stationary scroll teeth (403). The wall thickness of the moving scroll teeth (501) gradually increases from the outer ring to the center. The moving scroll (5) and the stationary scroll (4) cooperate to form a sealed chamber for compressing fluid. The motor (2) can drive the moving scroll (5) to rotate eccentrically relative to the stationary scroll (4) through the crankshaft (3).

2. The compressor scroll structure according to claim 1, characterized in that, The wall thickness of the stationary vortex tooth (403) and the moving vortex tooth (501) increases continuously and uniformly.

3. The compressor scroll structure according to claim 2, characterized in that, Both the stationary vortex tooth (403) and the moving vortex tooth (501) have rounded transition areas at their tooth roots, and the radius of the rounded corners gradually increases from the outer ring to the center.

4. The compressor scroll structure according to claim 1 or 2, characterized in that, The exhaust port (402) of the static vortex disk (4) is located in its central region.

5. The compressor scroll structure according to claim 1, characterized in that, The crankshaft (3) and the moving scroll (5) are connected by an eccentric bearing.

6. The compressor scroll structure according to claim 1, characterized in that, A conical diffuser section is provided at the exhaust port (402), and the large end of the diffuser section is connected to the exhaust pipe (102).

7. The compressor scroll structure according to claim 1, characterized in that, The base plate of the static vortex disk (4) and / or the dynamic vortex disk (5) is provided with reinforcing ribs (6), and the distribution density of the reinforcing ribs (6) gradually increases from the outer ring to the center.

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