Scroll compressor

Abstract

The present application provides a scroll compressor, which comprises a compression mechanism, a driving shaft, a main bearing seat, a bushing, and a counterweight component, the counterweight component comprising a base installed to or integrally formed with the bushing and a counterweight part extending from the base, the counterweight part being located in a concave cavity and revolving around a rotation axis with the rotation of the driving shaft to have an oil stirring surface as a windward surface, the oil stirring surface comprising a lower surface adjacent to the base and an upper surface away from the base, wherein the oil stirring surface is configured such that a projection area of the upper surface projected to a projection reference surface in a revolving direction of the counterweight component is greater than a projection area of the lower surface projected to the projection reference surface in the revolving direction, the scroll compressor of the present application can provide better motion balance, achieve better oil stirring and oil conveying effects, significantly reduce the power consumption of oil stirring, and has a simple structure, easy processing and manufacturing, and high cost efficiency.

Description

Technical Field

[0001] This invention relates to a scroll compressor. Background Technology

[0002] This section provides background information related to the present invention, which does not necessarily constitute prior art.

[0003] Scroll compressors can be used in applications such as refrigeration systems, air conditioning systems, and heat pump systems. A scroll compressor includes a compression mechanism for compressing a working fluid (e.g., refrigerant). This compression mechanism comprises a moving scroll and a stationary scroll. During operation, the drive shaft drives the moving scroll to revolve relative to the stationary scroll, maintaining a dynamic engagement between the moving and stationary scrolls. This creates a series of compression chambers between the moving and stationary scrolls to compress the working fluid.

[0004] To achieve the circumferential motion of the moving scroll relative to the stationary scroll, scroll compressors incorporate an anti-rotation mechanism and an eccentric pin at the drive shaft. This eccentricity allows the moving scroll to perform circular translation relative to the stationary scroll. However, this eccentric configuration can lead to imbalances in the moving parts, increasing noise and unnecessary friction. To mitigate these imbalances, counterweights are typically placed at the drive shaft and other locations in the scroll compressor for balancing. Furthermore, some specific counterweights include an oil-agitating surface. As the counterweight rotates with the drive shaft, this surface agitates nearby lubricating oil, promoting its flow to surrounding moving parts and their relative contact surfaces for improved lubrication.

[0005] In practical applications, in order to reduce the churning resistance of the churning surface and thus reduce power consumption, the churning surface needs to be set with a large inclination. However, this inclined surface design will significantly change the position of the counterweight's center of mass. In particular, the inclined surface design at certain angles will cause the center of mass of the counterweight to move along the longitudinal axis and deviate from the center of mass of the drive bushing that mates with the eccentric pin. This may result in a large deflection torque and cause relative misalignment and wear between the bushing and the drive bearing, which is detrimental to operational stability. Therefore, the counterweight needs to be improved in order to ensure dynamic balance and further improve churning efficiency and reduce churning power consumption while avoiding relative misalignment and wear between the bushing and the drive bearing. Summary of the Invention

[0006] This section provides a general overview of the invention, rather than a full disclosure of the invention's complete scope or all its features.

[0007] The object of this invention is to improve upon one or more of the technical problems mentioned above. In general, this invention provides a scroll compressor comprising:

[0008] A compression mechanism adapted to compress a working fluid and including a moving vortex having a drive coupling;

[0009] A drive shaft adapted to drive the compression mechanism, the drive shaft including a drive portion, the drive portion being droningly engaged with the drive coupling portion such that the drive shaft can drive the moving vortex;

[0010] Main bearing housing, adapted to support the compression mechanism and the drive shaft, the main bearing housing defining a cavity in which lubricating oil accumulates and has a normal oil level; and

[0011] A bushing, the bushing being disposed between the drive coupling and the drive unit; and

[0012] A counterweight component, defining a rotation axis, is rotatable about the rotation axis. The counterweight component includes a base mounted to or integrally formed with the bushing and a counterweight portion extending from the base. The counterweight portion is located in the cavity and rotates about the rotation axis as the drive shaft rotates, thereby having an oil-stirring surface as an air-facing surface.

[0013] The oil-stirring surface includes a lower surface adjacent to the base and an upper surface away from the base, with the dividing line corresponding to the normal oil level as the boundary. The oil-stirring surface is constructed such that the projected area of ​​the upper surface along the rotation direction of the counterweight member onto the projection reference plane is greater than the projected area of ​​the lower surface along the rotation direction onto the projection reference plane. The projection reference plane is a virtual plane parallel to the rotation axis of the counterweight member and passing through the intersection line of the oil-stirring surface and the top surface of the base.

[0014] The purpose of this configuration is to raise the center of mass of the counterweight upwards and appropriately reduce the area of ​​the lower part of the churning surface that is usually in the lubricating oil, so as to reduce the churning resistance and the power consumption of churning.

[0015] According to a preferred embodiment of the present invention, the oil stirring surface is constructed such that the ratio of the projected area of ​​the upper surface to the projected area of ​​the lower surface is greater than or equal to 1.15.

[0016] According to a preferred embodiment of the present invention, the oil stirring surface is constructed such that the ratio of the projected area of ​​the upper surface to the projected area of ​​the lower surface is greater than or equal to 1.3.

[0017] According to a preferred embodiment of the invention, the scroll compressor further includes an oil discharge path adapted to discharge lubricating oil in the cavity to the outside of the main bearing housing, the oil discharge path including an opening disposed on the peripheral wall of the main bearing housing, and the normal oil level being aligned with the opening.

[0018] According to a preferred embodiment of the present invention, the counterweight has an upper end portion away from the base and a lower end portion adjacent to the base, the upper end portion protruding forward relative to the lower end portion toward the front of the counterweight in the direction of rotation.

[0019] This configuration can raise the center of mass of the counterweight, thereby preventing the center of mass of the counterweight from moving downward along the longitudinal axis and deviating from the center of mass of the bushing. Therefore, it can avoid generating a large deflection torque in the bushing, improve operational stability, and the churning surface of this inclined design can also significantly reduce churning resistance, thereby improving churning efficiency and reducing churning power consumption.

[0020] According to a preferred embodiment of the present invention, the angle between each part of the oil stirring surface and the lower edge of the counterweight is greater than 90°.

[0021] According to a preferred embodiment of the present invention, the oil stirring surface includes a convex arc surface, a concave arc surface, a plane, a stepped surface, or a combination thereof.

[0022] According to a preferred embodiment of the present invention, the base is an annular mounting portion, which is sleeved on the outside of the bushing to be fixedly installed with the bushing.

[0023] According to a preferred embodiment of the present invention, at least one oil inlet is provided on the oil stirring surface, at least one oil outlet is provided on the top end face of the counterweight, and at least one oil passage is provided inside the counterweight extending from the at least one oil inlet to the at least one oil outlet.

[0024] By setting the oil inlet, oil outlet, and oil passage of the above configuration, the lubricating oil can be churned and then delivered to a specific location—the thrust surface—in a targeted manner, so that the counterweight component can play the role of churning and delivering oil at the same time.

[0025] According to a preferred embodiment of the present invention, the at least one oil passage extends along the direction of the rotation axis of the counterweight member.

[0026] According to a preferred embodiment of the present invention, the height of the counterweight is set such that, in the installed state of the counterweight member, in the direction of the rotation axis of the counterweight member, the distance between the at least one oil outlet and the thrust surface of the main bearing housing that is in sliding contact with the moving vortex is less than or equal to 5.5 mm.

[0027] Specifically, when lubricating oil exits from the outlet, the oil droplets are flung out along the direction of rotation. Subsequently, because they are no longer subject to rotational force, the droplet height essentially stops increasing. When the distance between the outlet and the thrust surface is too large, a significant amount of oil is flung onto the inner wall of the main bearing cover plate instead of reaching the thrust surface. Experiments show that a distance of less than or equal to the distance between the outlet and the thrust surface is optimal, ensuring sufficient lubricating oil is delivered to the thrust surface, improving lubrication and reducing wear. When the distance is greater than this, only a small amount of lubricating oil reaches the thrust surface, offering no benefit in improving lubrication or reducing wear.

[0028] According to a preferred embodiment of the invention, the counterweight is configured such that the at least one oil outlet is located radially inside the thrust surface.

[0029] In summary, the scroll compressor according to the present invention provides at least the following beneficial technical effects: the scroll compressor according to the present invention can provide better motion balance for the movement of the internal components of the scroll compressor, and can achieve better oil stirring and oil conveying effects, while significantly reducing oil stirring power consumption, and has a simple structure and is easy to process and manufacture, and has high cost-effectiveness. Attached Figure Description

[0030] The foregoing and other features and characteristics of the invention will become clearer from the following detailed description with reference to the accompanying drawings, which are by way of example only and are not necessarily drawn to scale. The same reference numerals are used in the drawings to indicate the same parts, in which:

[0031] Figure 1 A longitudinal cross-sectional view of a scroll compressor according to the present invention is shown;

[0032] Figure 2a and Figure 2b A first embodiment of the scroll compressor according to the present invention is shown, wherein, Figure 2a A three-dimensional view of the counterweight components is shown. Figure 2b A front view of the counterweight component is shown;

[0033] Figures 3a to 3c A second embodiment of the scroll compressor according to the present invention is shown, wherein, Figure 3a A three-dimensional view of the counterweight assembly is shown. Figure 3b A side view of the counterweight assembly is shown. Figure 3c A front view of the counterweight component is shown;

[0034] Figure 4a and Figure 4b An example of a prior art scroll compressor is shown, wherein, Figure 4a A three-dimensional view of the counterweight assembly is shown. Figure 4b A side view of the counterweight assembly is shown;

[0035] Figures 5a to 5c A third embodiment of the scroll compressor according to the present invention is shown, wherein, Figure 5a A three-dimensional view of the counterweight components is shown. Figure 5b The front view of the counterweight component is shown. Figure 5c A perspective view showing the counterweight assembly mounted on the drive shaft of the scroll compressor; and

[0036] Figures 6a to 6d A fourth embodiment of the scroll compressor according to the present invention is shown, wherein, Figure 6a A three-dimensional view of the counterweight assembly is shown. Figure 6b A side view of the counterweight assembly is shown. Figure 6c The front view of the counterweight component is shown. Figure 6d A perspective view showing the counterweight assembly installed on the drive shaft of the scroll compressor.

[0037] Reference tag list

[0038] Scroll compressor 1; housing 12; stator 14; rotor 15; drive shaft 16;

[0039] Main bearing housing 40; compression mechanism CM; cover 26; base 28; oil sump O

[0040] High-pressure space A2; Low-pressure space A1; Partition 19; Exhaust pipe 17; Dynamic vortex 24

[0041] Fixed vortex 22; Fixed vortex end plate 221; Fixed vortex scroll S2; Moving vortex 24

[0042] Moving scroll end plate 241; Moving scroll S4; Hub 240; Exhaust port C; Bushing 51

[0043] Main bearing cover plate 420; thrust surface 422; rotation axis L; counterweight assembly 5

[0044] Counterweight component 50; Annular mounting part 501; Counterweight part 502; Oil stirring surface 5022

[0045] Upper end 5024; Lower end 5026; Lower edge 5021; Top end face 5023

[0046] The existing counterweight component P5; the existing oil stirring surface P5022

[0047] The prior art's counterweight part P502; the prior art's lower edge P5021

[0048] Prior art bushing P51

[0049] Oil inlet 5027; Oil outlet 5028; Lower surface F2; Upper surface F1

[0050] Boundary line D; Step section T; Oil drainage path 11. Detailed Implementation

[0051] Now we will combine the appendix Figure 1-6d The preferred embodiments of the present invention will be described in detail below with reference to existing technologies. The following description is exemplary in nature and is not intended to limit the invention or its application or use.

[0052] For ease of description, such as Figure 1 The scroll compressor shown is exemplarily illustrated as a low-pressure side scroll compressor—that is, the electric motor is located in the low-pressure space. However, the scroll compressor according to the invention is not limited to this type, and the invention is also applicable to other suitable types of scroll compressors, such as high-pressure side scroll compressors—where the electric motor is located in the high-pressure space.

[0053] Figure 1 A longitudinal cross-sectional view of the scroll compressor 1 according to the present invention is shown. First, referring to... Figure 1 The overall structure of the scroll compressor 1 according to the present invention is described in summary.

[0054] like Figure 1 As shown, the scroll compressor 1 includes a generally cylindrical housing 12, an electric motor (including a stator 14 and a rotor 15), a drive shaft 16, a main bearing housing 40, and a compression mechanism CM adapted to compress a working fluid (e.g., a refrigerant).

[0055] A cover 26 located at the top of the housing 12 and a base 28 located at the bottom of the housing 12 can be mounted to the housing 12, thereby defining the internal volume of the scroll compressor 1. For example, lubricant such as lubricating oil can be stored in an oil sump O at the bottom of the internal volume for lubricating the various components of the scroll compressor 1. Specifically, for example, an oil supply passage (not specifically shown) is provided in the drive shaft 16 extending upward from the oil sump O to the upper end of the drive shaft 16, thereby facilitating further supply of lubricating oil to the main bearing housing 40 and the compression mechanism CM for lubrication.

[0056] The scroll compressor 1 also includes a partition 19 disposed between the top cover 26 and the housing 12 to divide the internal space of the scroll compressor 1 into a high-pressure space A2 and a low-pressure space A1. Specifically, the partition 19 and the cover 26 form the high-pressure space A2, while the partition 19, the housing 12, and the base 28 form the low-pressure space A1. An inlet pipe 18 for introducing low-pressure working fluid to be compressed is provided on the housing 12 in the low-pressure space A1, and an exhaust pipe 17 for discharging the high-temperature, high-pressure fluid to be compressed to the outside of the scroll compressor 1 is provided in the high-pressure space A2. As described above, Figure 1 The embodiment shown takes a low-pressure side scroll compressor as an example, therefore, as Figure 1 As shown, the motor and the compression mechanism CM are located in the low-pressure space A1.

[0057] The compression mechanism CM includes a moving scroll 24 and a fixed scroll 22. The fixed scroll 22 includes a fixed scroll end plate 221 and a fixed scroll S2; the moving scroll 24 includes a moving scroll end plate 241, a moving scroll S4 extending from a first side of the moving scroll end plate 241, and a hub 240 extending from a second side of the moving scroll end plate 241 (the hub corresponds to the drive connection portion according to this disclosure). The compression mechanism CM is formed by the engagement of the fixed scroll S2 and the moving scroll S4 to include: an open intake chamber in fluid communication with the outside of the compression mechanism CM, the intake port of which is in fluid communication with the low-pressure space A1 within the housing 12 to introduce the working fluid to be compressed in the low-pressure space A1 into the compression mechanism CM; and a series of compression chambers (including a central compression chamber capable of communicating with the exhaust port C described below) whose volume gradually decreases from the radially outer side to the radially inner side. In addition, the compression mechanism CM also includes an exhaust port C located at the radial center of the fixed vortex end plate 221. The exhaust port C can be in fluid communication with the high-pressure space A2 inside the housing 12 and discharge the compressed high-temperature and high-pressure fluid into the high-pressure space A2.

[0058] Conversely, for high-pressure scroll compressors, the motor and compression mechanism CM are located in a high-pressure space. For example, the compression mechanism CM directly introduces low-pressure working fluid from the outside through a suction fluid pipe and discharges the compressed high-temperature and high-pressure fluid into the internal volume of the casing, thus making the entire internal volume a high-pressure space. Therefore, the operating principles of high-pressure scroll compressors and low-pressure scroll compressors are largely the same, with the main difference being the different pressures in the space where the compression mechanism CM is located, which will not be elaborated further.

[0059] A portion of the drive shaft 16 is supported by a main bearing disposed in the main bearing housing 40. An eccentric crank pin (not specifically shown) is formed at the upper end of the drive shaft 16, which engages with the hub 240 of the moving scroll 24 via a bushing (e.g., an unloading bushing) 51 to drive the moving scroll 24. It should be noted that the eccentric crank pin corresponds to the drive portion according to this disclosure.

[0060] The main bearing housing 40 includes a main bearing cover plate 420 serving as a thrust plate. The main bearing cover plate 420 can be fixed to the body of the main bearing housing 40 by a fixing device. A space is formed between the body of the main bearing housing 40 and the main bearing cover plate 420 (or, the main bearing housing 40 defines a cavity). The back side (second side) of the moving scroll 24 is supported by the main bearing cover plate 420, and the annular end face of the main bearing cover plate 420 for supporting the moving scroll 24 is a thrust surface 422. During operation of the scroll compressor 1, the thrust surface 422 remains in contact with the back side of the moving scroll 24 and slides relative to each other.

[0061] The electric motor includes a stator 14 and a rotor 15. The rotor 15 drives a drive shaft 16 to rotate about its axis of rotation L. The drive shaft 16 is connected to a moving scroll 24 to drive the moving scroll 24. Specifically, a fixed scroll 22 is mounted to a main bearing housing 40, for example, using mechanical fasteners to restrict the radial and circumferential movement of the fixed scroll 22, but allowing a certain degree of axial translation. The moving scroll 24 is driven by the electric motor via the drive shaft 16, thereby enabling it to perform translational rotation relative to the fixed scroll 22—that is, rotation about the axis (i.e., the axis of the moving scroll 24 revolves around the axis of the fixed scroll 22, but the moving scroll 24 itself does not rotate about its axis—that is, it rotates on its own axis) by means of, for example, a cross slip ring. This results in a series of compression cavities whose volume gradually decreases from the radially outer to the radially inner side by the engagement of the fixed scroll S2 and the moving scroll S4.

[0062] To avoid or reduce motion imbalance, and to reduce the contact force between the side surface of the fixed scroll S2 of the fixed scroll 22 and the side surface of the moving scroll S4 of the moving scroll 24, the scroll compressor 1 is provided with a counterweight assembly 5 according to an embodiment of the present invention. Figure 1 As shown, the counterweight assembly 5 can be mounted to the upper end of the drive shaft 16 (in particular, the eccentric crank pin) and located in the space (cavity) defined by the main bearing housing 40. The counterweight assembly 5 is configured to rotate with the drive shaft 16 and the centrifugal force caused by the rotation of the counterweight assembly 5 acts on the drive shaft 16 to improve dynamic balance and force balance.

[0063] Additionally, as mentioned earlier, lubricating oil can be supplied via oil passages in the drive shaft 16 to the space defined by the main bearing housing 40 where the counterweight assembly 5 is located. Normally, lubricating oil accumulates in this space, causing the counterweight assembly 5 to agitate the lubricating oil during rotation (specifically, the windward side of the counterweight portion of the counterweight assembly 5 agitates the lubricating oil). Therefore, the windward side of the counterweight assembly 5 is also called the oil-agitating surface. Figure 1 (Not shown in detail below) As the counterweight assembly 5 rotates with the drive shaft 16, the oil-stirring surface agitates the surrounding lubricating oil to agitate oil droplets and oil mist, so that the lubricating oil can be more fully dispersed to the surrounding moving parts—such as the moving scroll end plate of the scroll mechanism CM—and the contact surfaces of the parts that come into contact with the moving parts, especially the thrust surface 422 of the main bearing cover plate 420 for supporting the moving scroll 24, thereby providing better lubrication.

[0064] Preferably, in various embodiments of the present invention, the counterweight assembly 5 is defined as including the aforementioned bushing 51 and a counterweight member 50 mounted to or integrally formed with the bushing 51. It should be understood that in some applications, the counterweight assembly 5 may not include the bushing 51, that is, it may be manufactured and used independently without being limited by the structure of the bushing 51 itself.

[0065] The following will be combined with the appendix Figures 2a to 6d A preferred embodiment of the scroll compressor according to the present invention is described in detail.

[0066] Figure 2a and Figure 2b A first embodiment of the scroll compressor 1 according to the present invention is shown, wherein, Figure 2a A perspective view of the counterweight component 50 is shown. Figure 2b A front view of the counterweight member 50 is shown. The counterweight member 50 includes: a base—preferably configured as an annular mounting portion 501 as shown in the figure, the annular mounting portion 501 being fitted over the outside of the bushing 51 for fixed installation; and a counterweight portion 502 extending to one side from the base—the annular mounting portion 501. In particular, the counterweight portion 502 may be configured to extend radially outward to one side and then axially upward. One side of the counterweight portion 502 is configured as an oil-stirring surface 5022, as shown... Figure 2bAs best shown, the oil-stirring surface 5022 of the counterweight 502 includes a lower surface F2 adjacent to the base (annular mounting part 501) and an upper surface F1 away from the base. Preferably, the oil-stirring surface 5022 is configured such that the projected area of ​​the upper surface F1 along the circumferential direction of the counterweight member 50 is greater than the projected area of ​​the lower surface F2 along the circumferential direction. It should be noted that the projected areas of the upper surface F1 and the lower surface F2 along the circumferential direction (i.e., the rotation direction / self-rotation direction) of the counterweight member 50 refer to the projected area of ​​the upper surface along the rotation direction of the counterweight member onto the projection reference plane and the projected area of ​​the lower surface along the rotation direction onto the projection reference plane. The projection reference plane can be a virtual plane parallel to the rotation axis of the counterweight member and passing through the intersection line of the oil-stirring surface and the top surface of the base. When the oil-stirring surface rotates, each point on the oil-stirring surface will pass perpendicularly through this projection reference plane. Furthermore, in the example where the entire churning surface extends vertically, parallel to the rotation axis of the counterweight member and facing forward in the direction of rotation, the projection reference plane coincides with the churning surface; that is, the entire churning surface lies on the projection reference plane. In this case, the projected areas of the upper and lower surfaces are maximized and equal to their actual areas, respectively. Preferably, the ratio of the projected area of ​​the upper surface F1 along the circumferential direction of the counterweight member 50 to the projected area of ​​the lower surface F2 along the circumferential direction is greater than or equal to 1.15; more preferably, the ratio is greater than or equal to 1.3. This configuration aims to further raise the center of mass of the counterweight 502 upwards and appropriately reduce the area of ​​the lower surface F2, which is normally immersed in the lubricating oil, within the churning surface 5022, thereby reducing churning resistance and churning power consumption. The boundary between the upper surface F1 and the lower surface F2 can be defined such that the upper surface F1 and the lower surface F2 correspond to the oil level of the lubricating oil accumulated in the space defined by the main bearing housing 40 under normal circumstances. The oil level under normal circumstances is generally fixed for a specific scroll compressor, and may vary only depending on the different actual operating conditions of that specific scroll compressor (such as high speed / low speed operation) or some unexpected conditions (such as unexpected oil shortage).

[0067] Now, let's revisit... Figure 1As shown in the view of the scroll compressor 1, the scroll compressor 1 also includes an oil drain path 11 to discharge the lubricating oil accumulated in the space of the main bearing housing 40 to the outside and return it to the oil sump O. The opening of the oil drain path 11 located on the peripheral wall of the main bearing housing 40 is approximately aligned with the position of the counterweight 502. Therefore, in this specific case where an oil drain path 11 is provided for draining oil from the space (cavity) of the main bearing housing, the oil level under normal conditions is aligned with the opening of the oil drain path 11. Consequently, according to this embodiment, the boundary line between the upper surface F1 and the lower surface F2 is aligned with the opening of the oil drain path 11.

[0068] like Figure 2b As best shown, the boundary line D between the upper surface F1 and the lower surface F2 is located slightly above the step T of the oil-stirring surface 5022. It is also conceivable that the boundary line D coincides exactly with the step T, or even more preferably, in some cases, the boundary line D is located below the step T. Specifically, by appropriately setting the axial position of the step T in the oil-stirring surface 5022, and / or by appropriately adjusting the axial position of the counterweight assembly 5 when installed in the scroll compressor 1, the step T of the oil-stirring surface 5022 is roughly aligned with the opening of the oil discharge path 11, so that the portion above the step T becomes the upper surface F1 and the portion below the step T becomes the lower surface F2. In this way, the projected area of ​​the upper surface F1 can be sufficiently larger than the projected area of ​​the lower surface F2. Furthermore, as... Figure 2b Preferably, as shown, the upper surface F1 has a larger (radial) thickness in most of the axial direction (i.e., from the dividing line D to the top end face 5023), while the lower surface F2 has a smaller thickness in most of the distance from the base (annular mounting portion 501) to the dividing line D. In this way, it is ensured that the projected area of ​​the upper surface F1 is larger than the projected area of ​​the lower surface F2.

[0069] Figures 3a to 3c A second embodiment of the scroll compressor 1 according to the present invention is shown, wherein, Figure 3a A perspective view of counterweight component 5 is shown. Figure 3b A side view of the counterweight assembly 5 is shown. Figure 3cA front view of the counterweight member 50 is shown. The second embodiment has a configuration substantially the same as the first embodiment described above, but with further improvements. The difference lies in that, based on the configuration of the first embodiment, in the second embodiment, the upper end portion 5024 of the counterweight 502 protrudes forward relative to the lower end portion 5026 towards the circumferential direction of the counterweight 502 (i.e., the rotation direction of the counterweight 502). Preferably, in this embodiment, the oil-stirring surface 5022 is constructed as a plane obtusely inclined relative to the lower edge 5021 of the counterweight 502 (the lower edge 5021 can be considered as being on a plane perpendicular to the rotation axis L of the drive shaft 16), that is, the angle formed by the oil-stirring surface 5022 and the lower edge 5021 of the counterweight 502 at all points is greater than 90°, and more preferably less than 150°. This configuration can raise the center of mass of the counterweight 502 upwards, thereby preventing the center of mass of the counterweight 502 from moving downwards along the longitudinal axis L and deviating from the center of mass of the bushing 51 (e.g., ...). Figure 4a and Figure 4b (As shown in the case of the counterweight assembly P5 of the prior art scroll compressor), a large deflection torque can be avoided in the bushing 51, improving operational stability. Furthermore, the churning surface 5022 with this inclined design can significantly reduce churning resistance, thereby improving churning efficiency and reducing churning power consumption.

[0070] Specifically, Figure 4a and Figure 4b An example of a counterweight assembly P5 of a prior art scroll compressor is shown, wherein, Figure 4a A perspective view of counterweight component P5 is shown. Figure 4b A side view of the counterweight assembly P5 is shown. As shown, in the prior art, the churning surface P5022 of the counterweight assembly P5 is typically constructed as a plane inclined at an acute angle relative to the lower edge P5021 of the counterweight P502. This is completely contrary to the above-described embodiment of the present invention. This design of the churning surface P5022 causes the center of mass of the counterweight P502 to shift downward along the longitudinal axis L, deviating from the center of mass of the bushing P51. This results in a large deflection torque in the bushing P51, causing it to shift relative to the drive bearing disposed between the bushing P51 and the hub 240 of the moving volute 24. The above-described configuration of the present invention avoids this problem in the prior art while ensuring high churning efficiency.

[0071] Although the oil-stirring surface 5022 is constructed as a planar shape in the above embodiments of the present invention, the present invention is not limited thereto. The oil-stirring surface 5022 may include a convex arc surface, a concave arc surface, a plane, a stepped surface (a surface composed of multiple planes with different inclination angles) or any combination thereof. As long as it can be ensured that the upper end portion 5024 of the counterweight portion 502 protrudes forward relative to the lower end portion 5026 in the circumferential direction of the counterweight portion 502 (i.e., the rotation direction of the counterweight portion 502), it can be avoided that the center of mass of the counterweight portion 502 moves downward along the longitudinal axis L and deviates from the center of mass of the bushing 51.

[0072] Furthermore, although in the above embodiment, the base of the counterweight member 50 is constructed as an annular mounting portion 501, which is sleeved on the outside of the bushing 51 for fixed installation with the bushing 51, the present invention is not limited to this. For example, the base of the counterweight member 50 may also be integrally formed with the bushing 51.

[0073] Figures 5a to 5c A third embodiment of the scroll compressor 1 according to the present invention is shown, wherein, Figure 5a A perspective view of the counterweight component 50 is shown. Figure 5b The front view of the counterweight component 50 is shown. Figure 5c A perspective view is shown of the counterweight assembly 5 installed on the drive shaft 16 of the scroll compressor 1. The third embodiment has a configuration that is substantially the same as the first embodiment described above, but with further improvements. The difference is that, based on the configuration of the first embodiment, the second embodiment has two oil inlets 5027 on the oil stirring surface 5022 of the counterweight part 502, two oil outlets 5028 on the top end face 5023 of the counterweight part 502, and two separate oil passages (not shown in the figure) extending from the two oil inlets 5027 to the two oil outlets 5028 respectively inside the counterweight part 502. Therefore, when the counterweight assembly 5 rotates with the drive shaft 16, lubricating oil can reach the two oil outlets 5028 through the two oil inlets 5027 and two separate oil passages, thereby supplying lubricating oil from the lower end 5026 of the counterweight 502 to the upper end 5024 (top end face 5023), so as to reach other components and surfaces located near the top end face 5023, such as the thrust surface 422 of the main bearing cover plate 420, as in Figure 5cAs shown, when the counterweight assembly 5 is installed in the scroll compressor 1, the counterweight assembly 5 is installed in the space defined by the main bearing housing 40, and the top end face 5023 of the counterweight part 502 is adjacent to the thrust surface 422 of the main bearing cover plate 420, and the oil outlet 5028 is located radially inside the thrust surface 422. Therefore, through the two oil inlets 5027, two separate oil passages and two oil outlets 5028, lubricating oil can be supplied to the thrust surface 422 of the main bearing cover plate 420 to provide lubrication for the frictional sliding contact between the thrust surface 422 and the moving scroll 24. Preferably, in this embodiment, the counterweight assembly 5 is configured such that, when the counterweight assembly 5 is installed in the scroll compressor 1, the distance between the oil outlet 5028 and the thrust surface 422 in the direction of the longitudinal axis (rotation axis) of the counterweight assembly 5 (i.e., the direction of the longitudinal axis L of the scroll compressor 1) is less than or equal to 5.5 mm, thereby enabling more efficient supply of lubricating oil to the thrust surface 422. Specifically, when the lubricating oil exits from the oil outlet 5028, the oil droplets are thrown out along the rotation direction, and subsequently, because they are no longer subject to rotational force, the height of the oil droplets does not continue to increase. When the distance between the oil outlet 5028 and the thrust surface 422 is too large, a large amount of oil is thrown onto the inner wall of the main bearing cover plate 420 and cannot reach the thrust surface 422. Experiments show that when the distance between the oil outlet 5028 and the thrust surface 422 is less than or equal to 5.5 mm, it is optimal, ensuring that sufficient lubricating oil is delivered to the thrust surface 422, which can improve the lubrication of the thrust surface 422 and reduce wear. When it is greater than 5.5 mm, only a small amount of lubricating oil reaches the thrust surface 422, which does not help to improve the lubrication of the thrust surface 422 or reduce wear.

[0074] Furthermore, preferably, in this embodiment, the counterweight assembly 5 is configured such that the oil passage extends vertically upward along the longitudinal axis of the counterweight assembly 5 (i.e., the direction of the longitudinal axis L of the scroll compressor 1). When the counterweight assembly 5 rotates, the lubricating oil flows upward in the oil passage to the top end face 5023 through the action of centrifugal force, and then reaches the thrust surface 422. This configuration of the oil passage is easy to manufacture using various methods known in the prior art. Furthermore, it should be understood that the two oil circuits mentioned above are not necessarily completely independent of each other; they can also partially overlap or intersect. For example, based on the two oil inlets 5027 and the two oil outlets 5028, it is entirely possible to set up only one oil circuit, which branches only at the two oil inlets 5027 and the two oil outlets 5028 to connect the two oil inlets 5027 and the two oil outlets 5028 respectively. Moreover, the oil circuit is not limited to extending in a straight line along the longitudinal axis of the counterweight component 5, but can extend in any direction and can be arc-shaped, broken-line-shaped, wave-shaped, stepped, or other irregular shapes, etc. Different configurations of oil circuits can be set according to actual needs. Furthermore, the number of oil inlets and outlets, as well as the corresponding number of oil circuits, can be arbitrary and can be set according to actual needs.

[0075] By combining the oil stirring surface 5022 of the above configuration with the oil inlet, oil outlet and oil passage of the above configuration, it is possible to achieve efficient oil stirring and reduce oil stirring power consumption, and further deliver the lubricating oil to a specific location - the thrust surface 422, so that the counterweight component 5 can play the role of oil stirring and oil delivery at the same time.

[0076] Figures 6a to 6d A fourth embodiment of the scroll compressor 1 according to the present invention is shown, wherein, Figure 6a A perspective view of counterweight component 5 is shown. Figure 6b A side view of the counterweight assembly 5 is shown. Figure 6c The front view of the counterweight component 50 is shown. Figure 6dA perspective view is shown of the counterweight assembly 5 installed on the drive shaft 16 of the scroll compressor 1. The fourth embodiment includes features of the aforementioned embodiments according to the present invention and is a combination of the aforementioned embodiments. As shown, one side of the counterweight 502 is configured as an oil-stirring surface 5022. The upper end portion 5024 of the counterweight 502 protrudes forward relative to the lower end portion 5026 toward the circumferential direction (i.e., the rotation direction of the counterweight 502) of the counterweight 502, such that the oil-stirring surface 5022 is configured as a plane inclined at an obtuse angle relative to the lower edge 5021 of the counterweight 502. Two oil inlets 5027 are provided on the oil-stirring surface 5022 of the counterweight 502, and two oil outlets 5028 are provided on the top end face 5023 of the counterweight 502. Two separate oil passages are provided inside the counterweight 502, extending from the two oil inlets 5027 to the two oil outlets 5028, respectively, to supply lubricating oil to the thrust surface 422 (see Figure 1). Figure 6d As shown), and preferably, the distance between the oil outlet 5028 and the thrust surface 422 is less than or equal to 5.5 mm. Further, refer to... Figure 6c The ratio of the projected area of ​​the upper surface F1 of the oil stirring surface 5022 along the circumferential direction of the counterweight component 5 to the projected area of ​​the lower surface F2 along the circumferential direction is preferably greater than or equal to 1.3.

[0077] By combining the structural features of the above embodiments, the beneficial technical effects of achieving dynamic balance of the counterweight component 5, efficient oil stirring and lubricating oil delivery, and reducing oil stirring power consumption can be optimally achieved, thereby improving the overall operating performance of the scroll compressor 1.

[0078] Those skilled in the art should understand that the above features can be appropriately varied and modified, and the combination of them can be arbitrary, and is not limited to the specific embodiments described above.

[0079] Although exemplary embodiments of the scroll compressor according to the present invention have been described in the foregoing embodiments, the present invention is not limited thereto, and various modifications, substitutions and combinations can be made without departing from the scope of protection of the present invention.

[0080] It is evident that by combining or modifying different implementation methods and various technical features in different ways, various different implementation methods can be designed.

[0081] The scroll compressor according to a preferred embodiment of the present invention has been described above with reference to specific embodiments. It is understood that the above description is merely exemplary and not restrictive, and various modifications and variations can be conceived by those skilled in the art with reference to the above description without departing from the scope of the invention. These modifications and variations are also included within the scope of protection of the present invention.

Claims

1. A scroll compressor, the scroll compressor (1) comprising: a compression mechanism (CM) adapted to compress a working fluid and including an orbiting scroll (24) having a driving coupling portion (240); a drive shaft (16) adapted to drive the compression mechanism, the drive shaft including a driving portion drivingly engaged with the driving coupling portion such that the drive shaft can drive the orbiting scroll; a main bearing housing (40) adapted to support the compression mechanism and the drive shaft, the main bearing housing defining a recess in which lubricating oil is accumulated to have a normal oil level; and a bushing (51) provided between the driving coupling portion and the driving portion; and a weight member (50) defining a rotation axis about which the weight member can spin, the weight member including a base mounted to or integrally formed with the bushing and a weight portion (502) extending from the base, the weight portion being located in the recess and spinning about the rotation axis as the drive shaft rotates to have a oil stirring surface (5022) as a windward surface, characterized in that, with a boundary line (D) corresponding to the normal oil level as a boundary, the oil stirring surface includes a lower surface (F2) adjacent to the base and an upper surface (F1) away from the base, wherein the oil stirring surface is configured such that a projected area of the upper surface projected to a projection reference surface in a spinning direction of the weight member is greater than a projected area of the lower surface projected to the projection reference surface in the spinning direction, the projection reference surface being a virtual plane parallel to the rotation axis of the weight member and passing through an intersection line of the oil stirring surface and a top surface of the base. The oil stirring surface is configured such that a ratio of the projected area of the upper surface to the projected area of the lower surface is greater than or equal to 1.

15. The oil stirring surface is configured such that a ratio of the projected area of the upper surface to the projected area of the lower surface is greater than or equal to 1.

3. The scroll compressor further includes a drain path (11) adapted to drain the lubricating oil in the recess to an outside of the main bearing housing, the drain path including an opening provided at a peripheral wall of the main bearing housing, and the normal oil level is aligned with the opening. The weight portion has an upper end portion (5024) away from the base and a lower end portion (5026) adjacent to the base, the upper end portion (5024) protruding toward a front side in the spinning direction of the weight portion relative to the lower end portion (5026). Each portion of the oil stirring surface forms an angle greater than 90° with a lower edge (5021) of the weight portion. The oil stirring surface includes a convex curved surface, a concave curved surface, a flat surface, a stepped surface, or a combination thereof. The base is a ring-shaped mounting portion (501) sleeved on an outside of the bushing to be fixedly mounted with the bushing.

2. The scroll compressor of claim 1, wherein ​ 3. The scroll compressor of claim 1, wherein ​ 4. The scroll compressor of claim 1, wherein ​ 5. The scroll compressor according to any one of claims 1 to 4, wherein ​ 6. The scroll compressor of claim 5, wherein, ​ 7. The scroll compressor of claim 5, wherein ​ 8. The scroll compressor of claim 1, wherein, ​ 9. The scroll compressor according to any one of claims 1 to 4, wherein At least one oil inlet (5027) is provided on the oil stirring face, at least one oil outlet (5028) is provided on the top end face of the counterweight part, and at least one oil passage (5029) extending from the at least one oil inlet to the at least one oil outlet is provided inside the counterweight part.

10. The scroll compressor of claim 9, wherein, The at least one oil passage extends along the direction of the rotation axis of the counterweight member.

11. The scroll compressor of claim 9, wherein, The height of the counterweight part is set such that, in the installed state of the counterweight member, the distance of the at least one oil outlet from the thrust face (422) of the main bearing housing (40) with which the orbiting scroll is in sliding contact is less than or equal to 5.5 mm in the direction of the rotation axis of the counterweight member.

12. The scroll compressor of claim 11, wherein, The counterweight member is configured such that the at least one oil outlet is located radially inside the thrust face (422).

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