Scroll compressor

Abstract

This utility model relates to a scroll compressor, comprising: a housing; a fixed scroll disk, the fixed scroll disk being coupled to the housing and including a fixed end plate and a fixed scroll, the fixed end plate including an inlet for drawing in refrigerant and an outlet disposed further inward than the inlet for discharging the refrigerant, the fixed scroll extending from the inlet to the outlet on the fixed end plate; and a rotary scroll disk, the rotary scroll disk including a rotary end plate and a rotary scroll, the rotary end plate being configured opposite to the fixed end plate, the rotary scroll extending from the rotary end plate opposite to the fixed scroll for compressing the refrigerant; the thickness or shape of the rotary scroll being different from that of the fixed scroll opposite to the rotary scroll. According to this utility model, compression efficiency and compression volume can be improved, and the scroll scroll shape design is optimized.

Description

Technical Field

[0001] This utility model relates to a scroll compressor. More specifically, it relates to a scroll compressor with an optimized scroll shape design to improve compression efficiency and compression volume. Background Technology

[0002] Typically, a compressor, as a device used in refrigeration cycles (hereinafter referred to as refrigeration cycles) such as refrigerators or air conditioners, is a device that provides the work required for heat exchange in the refrigeration cycle by compressing the refrigerant.

[0003] Based on the method of compressing the refrigerant, compressors can be classified into reciprocating, rotary, and scroll types. Among them, a scroll compressor is a compressor that uses a rotating scroll plate to engage with a fixed scroll plate fixed in the internal space of a sealed container, thereby forming a compression chamber between the fixed scroll of the fixed scroll plate and the rotating scroll of the rotating scroll plate.

[0004] Compared to other types of compressors, scroll compressors have the following advantages: compression is achieved continuously through interlocking scroll shapes, resulting in a relatively high compression ratio; and stable torque is achieved due to the smooth transition between refrigerant intake, compression, and discharge operations. For these reasons, scroll compressors are widely used for refrigerant compression in air conditioning systems and other applications.

[0005] Traditionally, the scroll shape of a scroll compressor has been achieved using curves such as involutes or algebraic spirals. By utilizing regular formulas such as involutes or algebraic spirals, errors can be minimized even in mass production of the scrolls, thus improving the reliability of the compressor.

[0006] On the other hand, as the home appliance market expands further, compressors are increasingly used in appliances operating in cold regions with lower external temperatures. In this context, compressors installed in these regions struggle to compress refrigerants at high compression ratios compared to those in temperate regions, thus compromising compressor efficiency.

[0007] In particular, environmental and stability considerations must be taken into account for the refrigerants used in compressors, and there are increasingly more regulations recommending the use of refrigerants with low compression ratios.

[0008] Therefore, recently, even scroll compressors of the same size are being called for to overcome this problem by being able to compress more refrigerant.

[0009] However, the fundamental limitation of traditional scroll compressors with algebraic spiral or involute shapes is that they cannot maximize the use of the area of ​​the end plates such as the swirling scroll disk, and therefore cannot increase the stroke volume along the diameter of the end plates.

[0010] Therefore, existing compressors attempt to overcome this problem by increasing the height of the scroll to expand the stroke volume. However, the fundamental problem this leads to is that high-pressure refrigerants cannot be used due to the durability of the scroll, or the stability of the scroll cannot be guaranteed.

[0011] On the other hand, previous attempts have focused on further expanding the length of the cyclone scroll by eccentrically moving the center of the cyclone scroll away from the center of the end plate of the cyclone scroll. However, the fundamental problem is that vibration and noise issues, or force and energy eccentricity, can occur when the scroll compressor is driven at high RPM, making it impossible to drive the scroll compressor stably. Utility Model Content

[0012] Problems to be solved by the utility model

[0013] This invention provides a scroll compressor that can maintain the height of the scroll while increasing the stroke volume.

[0014] This invention can increase the stroke volume even without eccentrically positioning the refrigerant discharge port from the end plate of the swirling scroll or the end plate of the fixed scroll outwards.

[0015] This invention provides a scroll compressor that can both increase the stroke volume relative to the end plate area of ​​the rotary scroll plate and ensure durability and stability.

[0016] This invention provides a scroll compressor with a scroll shape that increases the stroke volume along the outer surface of the end plate of the scroll disk.

[0017] Technical solutions to the problem

[0018] To solve the above problems, this invention defines the vortex shape by mixing other formulas such as arcs into the conventional curves of existing involutes or algebraic spirals. This allows the maximum area of ​​the outer diameter of the end plate of the swirling vortex disk to be used as a compression space, thus increasing the stroke volume without increasing the vortex height under the same frame diameter.

[0019] To address the aforementioned problems, this invention offers a versatile approach to determining the scroll thickness using various formulas and ranges. Furthermore, it allows for setting different formulas for the outer path (A path) and inner path (B path) of the scroll, thus enabling the free design of the desired scroll thickness range. Therefore, by reducing scroll height and increasing scroll thickness, reliability can be ensured under high pressure ratios and overload operation.

[0020] To solve the above-mentioned problems, this utility model provides a scroll compressor that may include: a housing; a fixed scroll disk, which is coupled to the housing and includes a fixed end plate and a fixed scroll, the fixed end plate including a refrigerant intake port and a refrigerant discharge port disposed further inward than the intake port, the fixed scroll extending from the intake port to the discharge port on the fixed end plate; and a rotary scroll disk, which includes a rotary end plate and a rotary scroll, the rotary end plate being configured opposite to the fixed end plate, the rotary scroll extending from the rotary end plate opposite to the fixed scroll for compressing the refrigerant. The thickness or shape of the rotary scroll may be different from that of the fixed scroll opposite to the rotary scroll.

[0021] The swirling vortex can be formed to be thicker than the fixed vortex.

[0022] The vortex can be configured to have a thickness that increases as it approaches the outlet from the intake port.

[0023] The vortex can be configured to have a thickness that increases as it approaches the outlet from the intake port.

[0024] At the outer end of the vortex opposite the intake port, the spacing of the vortexes disposed in the first region can be set to be larger than the spacing of the vortexes disposed in regions other than the first region, the first region being equivalent to 90 degrees centered on the rotation axis.

[0025] In the swirling vortex, the spacing of the swirling vortices arranged in the second region can be formed to be the same as each other, and the second region corresponds to the opposite side of the first region with respect to the rotation axis.

[0026] In the fixed vortex, the spacing between the fixed vortexes opposite to the swirling vortexes disposed in the first region can be set to be larger than the spacing between the fixed vortexes disposed in regions other than the first region.

[0027] In the fixed vortex, the spacing between the fixed vortex and the swirling vortex disposed in the second region can be made to be the same for each other.

[0028] The swirling vortex can extend from the outer end opposite the intake port to the inner end opposite the exhaust port in a combination of arc and algebraic spiral shapes.

[0029] The swirling spiral can extend first in an arc shape at the outer end and then in an algebraic spiral shape.

[0030] The swirling spiral can extend in an arc shape of 180 degrees with respect to the rotation axis at the outer end, and then extend in an algebraic spiral shape of more than 90 degrees with respect to the rotation axis.

[0031] The swirling spiral can extend in an arc shape in a region between 180 degrees with respect to the rotation axis at the outer end, and in an algebraic spiral shape in the region outside this region.

[0032] The spacing of the swirling scrolls located at the outer ends of the swirling scrolls in a first region between 90 degrees with reference to the rotation axis can be different from the spacing of the swirling scrolls located at the ends of the first region in a third region between 90 degrees with reference to the rotation axis, the spacing of the swirling scrolls located at the ends of the third region in a second region between 90 degrees with reference to the rotation axis, and the spacing of the swirling scrolls located in a fourth region between the ends of the second region and the first region.

[0033] The spacing of the spiral vortexes located at the outer ends of the spiral vortexes in the first region between 90 degrees with reference to the rotation axis, the spacing of the spiral vortexes located at the ends of the first region between 90 degrees with reference to the rotation axis, the spacing of the spiral vortexes located at the ends of the third region between 90 degrees with reference to the rotation axis, the spacing of the spiral vortexes located at the ends of the third region between 90 degrees with reference to the rotation axis, and the spacing of the spiral vortexes located in the fourth region between the ends of the second region and the first region can all be formed differently.

[0034] The spacing of the swirling vortices configured in the first region can be made larger than the spacing of the swirling vortices configured in the third region, and the spacing of the swirling vortices configured in the third region can be made larger than the spacing of the swirling vortices configured in the second region.

[0035] Utility Model Effect

[0036] This invention provides a scroll compressor that can maintain the height of the scroll while increasing the stroke volume.

[0037] Even without eccentrically positioning the refrigerant discharge port from the end plate of the swirling scroll or the end plate of the fixed scroll outwards, this invention can still increase the stroke volume.

[0038] This invention provides a scroll compressor that can increase the stroke volume relative to the end plate area of ​​the rotary scroll plate while ensuring durability and stability.

[0039] This invention provides a scroll compressor with a scroll shape that increases the stroke volume along the outer surface of the end plate of the scroll disk. Attached Figure Description

[0040] Figure 1 This is a diagram showing the basic structure of the scroll compressor of this utility model.

[0041] Figure 2 This is a diagram showing the detailed structure of the compression section 300.

[0042] Figure 3 It is a diagram showing the specific shapes of the rotating vortex disk and the fixed vortex disk.

[0043] Figure 4 This is a diagram illustrating an embodiment of a design for a fixed scroll and a rotating scroll.

[0044] Figure 5 The diagram illustrates an embodiment of the practical design of swirling and fixed vortices based on the plurality of envelopes.

[0045] Figure 6 This is a diagram illustrating a first embodiment of the scroll design of the scroll compressor of this utility model.

[0046] Figure 7 This is a diagram illustrating a second embodiment of the scroll design of the scroll compressor of this utility model.

[0047] Figure 8 This is a diagram illustrating a third embodiment of the scroll design of the scroll compressor of this utility model.

[0048] Figure 9 This is a diagram illustrating a fourth embodiment of the scroll design of the scroll compressor of this utility model.

[0049] Figure 10 This is a diagram illustrating the fifth embodiment of the scroll design of the scroll compressor of this utility model.

[0050] Figure 11 This is a diagram illustrating the sixth embodiment of the scroll design of the scroll compressor of this utility model. Detailed Implementation

[0051] The embodiments disclosed in this specification will now be described in detail with reference to the accompanying drawings. In this specification, even different embodiments are given the same or similar reference numerals for the same or similar structures, and the first description replaces the subsequent description. Unless the context clearly indicates otherwise, the singular expressions used in this specification include the plural expressions. Furthermore, when describing the embodiments disclosed in this specification, detailed descriptions of related well-known technologies will be omitted if it is determined that such detailed descriptions might unnecessarily obscure the spirit of the embodiments disclosed in this specification. It should also be noted that the accompanying drawings are only for ease of understanding of the embodiments disclosed in this specification and should not be construed as limiting the technical concepts disclosed in this specification.

[0052] Figure 1 This is a diagram showing the basic structure of the scroll compressor of this utility model.

[0053] The scroll compressor of this invention can typically be installed in a device using a heat pump system, and can be configured to receive a fluid such as a refrigerant, compress it, and then discharge it.

[0054] For example, the scroll compressor of this invention can be applied to household appliances such as refrigerators, air conditioners, and clothing handling devices.

[0055] The scroll compressor of this invention may include: a housing 100 forming the exterior; a drive unit 200 coupled to the housing 100; a compression unit 300 that receives power from the drive unit 200 and compresses fluid; and a balance block 400 coupled to the drive unit 200 to counteract the energy generated by eccentricity.

[0056] The housing 100 may be configured as a cylinder or cylindrical shape, and may include: an inlet pipe 110 for receiving the inflow of refrigerant; and a discharge pipe 120 through which the refrigerant is discharged after being compressed to a high temperature and high pressure.

[0057] The housing 100 may have a space on one side therein, the space storing oil capable of lubricating one or more of the drive unit 200 and the compression unit 300.

[0058] The oil can be stored closer to the drive unit 200 than the compression unit 300.

[0059] The drive unit 200 may include: a stator 210 fixed to the inner wall of the housing 100 for forming a rotating magnetic field; a rotor 220 that rotates using the stator 210; and a rotating shaft 230 connected to the rotor 220 and rotating together with the rotor 220.

[0060] The rotating shaft 230 may be configured to be longer than both the rotor 220 and the stator 210. One end of the rotating shaft 230 may be combined with or connected to the compression section 300, and the other end may extend into the space where oil is stored.

[0061] The rotating shaft 230 may include: a main shaft 231 coupled to the rotor 220; a coupling shaft 232 extending from the main shaft 231 and connected to the compression section 300; and an extension shaft 233 extending from the main shaft 231 to the oil storage space.

[0062] The rotating shaft 230 may further include: an oil flow path that guides oil flowing from the extension shaft 233 to the main shaft 231 and the connecting shaft 232; and a connecting hole that connects the oil flow path to the drive unit 200 and the compression unit 300.

[0063] The scroll compressor of this utility model may include: a support frame 235, which rotatably supports the extension shaft 233; and a guide portion 234, which is combined with the support frame 235 and is used to guide the oil collected in the oil storage space to the extension shaft 233.

[0064] The guide section 234 may also be equipped with an oil pump or the like, and may be configured to communicate with the oil flow path. Thus, the oil contained in the oil storage space can be supplied to the drive section 200 and the compression section 300 along the oil flow path.

[0065] The oil can lubricate or cool the drive unit 200 and the compression unit 300.

[0066] The coupling shaft 232 can be configured to be eccentric relative to the main shaft 231. For example, the coupling shaft 232 can be configured to have a larger diameter than the main shaft 231, and the center of the coupling shaft 232 can be configured to be diametrically separated from the center of the main shaft 231.

[0067] Therefore, the structure of the compression part 300 that is coupled with the coupling shaft 232 changes when the rotating shaft 230 rotates.

[0068] The balance block 400 may include: a main balance block 410, which is coupled to the connecting shaft 232 to compensate for the eccentricity of the connecting shaft 232 relative to the main shaft 231; and a compensation balance block 420, which is coupled to the rotor 220 to compensate for the eccentricity between the main balance block 410 and the rotating shaft 230.

[0069] The compression section 300 may include: a fixed scroll plate 320 for receiving refrigerant supplied from the inlet pipe 110; a rotary scroll plate 330 configured to engage with the fixed scroll plate 320 and be coupled to the rotating shaft 230 for rotation; and a main frame 310 coupled to the fixed scroll plate 320 for accommodating the rotary scroll plate 330.

[0070] The main frame 310 is joined to the inner circumferential surface of the housing 100, and has a space on one side for accommodating the vortex disk 330.

[0071] Between the main frame 310 and the vortex disk 330, a cross-shaped slider (Oldham ring) 700 may be provided to prevent the vortex disk 330 from rotating about the rotation axis.

[0072] The cross slider 700 can be configured to be combined with both the main frame 310 and the vortex disk 330. Because of the cross slider 700, the vortex disk 330 can only revolve around the axis of rotation 230, preventing it from rotating or rotating on its own axis of rotation 230.

[0073] The swirling scroll 330 rotatably supports the connecting shaft 232. The swirling scroll 330 does not rotate with the connecting shaft 232, but rather supports the connecting shaft 232 like a bearing, allowing the connecting shaft 232 to rotate relative to it. As a result, the swirling scroll 330 can revolve around the connecting shaft 232 without rotating with it, instead utilizing the eccentricity of the connecting shaft 232.

[0074] The fixed scroll plate 320 can be configured to communicate with the inlet pipe 110 to receive the inflow of refrigerant. A compression space for compressing the refrigerant can be formed between the rotating scroll plate 330 and the fixed scroll plate 320. As the rotating scroll plate 330 revolves, the refrigerant flowing into the inlet pipe 110 can be compressed and flow.

[0075] The fixed scroll plate 320 may include a discharge section for discharging compressed refrigerant.

[0076] The areas of the fixed scroll plate 320, except for its outer peripheral surface, can be separated from the inner surface of the housing 100. That is, the discharge section can be configured at a constant interval from the housing 100. Thus, refrigerant can be discharged from the fixed scroll plate 320 and flow into the interior of the housing 100, and the refrigerant discharged from the fixed scroll plate 320 can be discharged to the discharge pipe 120 connected to the housing 100.

[0077] The refrigerant discharged from the fixed scroll plate 320 is in a high-pressure state, and the high-pressure refrigerant can keep the inside of the housing 100 in a high-pressure state before being discharged to the discharge pipe 120.

[0078] As a result, the oil stored in the housing 100 can flow along the oil flow path using the pressure difference and be discharged to a plurality of connecting holes to supply the drive unit 200 and the compression unit 300. The oil is not vaporized in the compression unit 300, but can be discharged together with the refrigerant and collected again in the oil storage space along the inner wall of the housing 100.

[0079] Although the discharge pipe 120 can be configured between the compression section 300 and the drive section 200, it can be configured at any position in the housing 100 as long as the refrigerant discharged from the fixed scroll plate 320 can be discharged.

[0080] Figure 2 This is a diagram showing the detailed structure of the compression section 300. Figure 3 It is a diagram showing the specific shapes of the rotating vortex disk and the fixed vortex disk.

[0081] The fixed scroll plate 320 may include: a fixed end plate 321, which communicates with the inflow pipe 110 to receive the supply of refrigerant; a connecting plate 322, which extends from the outer peripheral surface of the fixed end plate 321 and connects with the inner surface of the housing 100; and a fixed scroll 323, which protrudes from the fixed end plate 321 for compressing the refrigerant.

[0082] The fixed end plate 321 may include: an inlet 325, which is connected to the inflow pipe 110 to receive the supply of refrigerant; and an outlet 326, which is located further inside the inlet 325 for discharging the refrigerant.

[0083] The outlet 326 can be located at the center of the fixed end plate 321, and can be configured to extend through the fixed end plate 321 from the inside of the fixed end plate 321 in a direction away from the drive part 200.

[0084] The inlet 325 may be configured to be closer to the outer peripheral surface of the fixed end plate 321 than the outlet 326.

[0085] The fixed vortex 323 can be configured to protrude from one side of the fixed end plate 321 to the same height as the connecting plate 322, and can be configured to extend from the suction port 325 along the periphery of the fixed end plate 321 toward the discharge port 326.

[0086] The fixed spiral 323 can be configured as at least any one of the following shapes: algebraic spiral, involute, and circular arc. The fixed spiral 323 can be considered as a vortex shape.

[0087] The fixing plate 322 can extend further outward from the fixing end plate 321. The diameter of the fixing plate 322 can be set to be larger than the diameter of the fixing end plate 321. The diameter of the fixing plate 322 can be set to correspond to the inner circumferential diameter of the housing 100.

[0088] The fixed connecting plate 322 may be provided with at least one bypass hole along the rotation axis direction. As a result, even if the fixed connecting plate 322 is in contact with the inner circumferential surface of the housing 100, the refrigerant discharged from the discharge hole 326 can still be discharged to the discharge pipe 120.

[0089] The swirling scroll 330 may include: a swirling end plate 331, which is arranged parallel to the fixed end plate 321; a swirling scroll 333, which protrudes from the swirling end plate 331 in a direction that engages with or is opposite to the fixed scroll 323; and a bearing portion 332, which extends from the swirling end plate 331 and rotatably supports the rotating shaft 230.

[0090] The swirling end plate 331 can be configured to have the same diameter as or smaller than the fixed end plate 321, and the swirling scroll 333 can be configured to have a height corresponding to the height of the fixed scroll 323.

[0091] The swirling vortex 333 can extend to engage or oppose the fixed vortex 323 along the periphery of the swirling end plate 331. Consequently, the swirling vortex 333 can also extend from the intake port 325 along the periphery of the swirling end plate 331 toward the discharge port 326 with a gradually decreasing diameter. Consequently, the swirling vortex 333 can also be configured in a vortex shape.

[0092] The bearing portion 332 can be configured in any shape as long as it can rotatably support the rotating shaft 230 and withstand the force applied in the diametrical direction due to the connecting shaft 232.

[0093] The bearing portion 332 may be configured to have a smaller diameter than the connecting shaft 232 and be accommodated in the connecting shaft 232.

[0094] In this case, the coupling shaft 232 can be eccentrically disposed on the main shaft 231, but the coupling shaft 232 can also be non-eccentric relative to the main shaft 231. In this case, the bearing portion 332 accommodated in the coupling shaft 232 can be eccentrically accommodated in the coupling shaft 232.

[0095] Of course, the connecting shaft 232 may also be eccentric relative to the main shaft 231, and the bearing portion 332 may protrude from the rotary end plate 331 at the same center as the connecting shaft 232.

[0096] The main frame 310 can be mounted on the fixed connecting plate 322 and combined with the housing 100 to accommodate the vortex disk 330.

[0097] The swirling vortex disk 330 can be configured to revolve around the rotation axis 230 between the main frame 310 and the fixed vortex disk 320.

[0098] In order to continuously compress the refrigerant without leakage, the swirling scroll 333 and the fixed scroll 323 need to prevent the swirling end plate 331 from rotating around the rotation axis. For this purpose, the cross slider 700 can be set as a rigid body and disposed between the swirling scroll 330 and the main frame 310.

[0099] The cross slider 700 can be configured to slide back and forth on the rotary end plate 331 along a first direction, and can also be configured to slide back and forth on the main frame 310 along a second direction different from the first direction. For example, the second direction can be perpendicular to the first direction.

[0100] Thus, the center of the vortex disk 330 can revolve around the axis of rotation based on the movement allowed by the cross slider 700, but self-rotation is prevented.

[0101] Figure 4 Figures (a), (b), and (c) illustrate embodiments of the design of fixed and rotating scrolls.

[0102] The fixed scroll and the rotary scroll need to be designed so that the refrigerant does not flow out and is continuously compressed. In addition, since the fixed scroll and the rotary scroll are configured to have their inner and outer surfaces interlocking, there are different compression chambers on the inner and outer surfaces, respectively.

[0103] For example, with the swirling scroll 333 as a reference, a first compression chamber where the refrigerant is compressed exists on the outer surface of the swirling scroll 333 and the inner surface of the fixed scroll 323, and a second compression chamber where the refrigerant is compressed exists on the inner surface of the swirling scroll 333 and the outer surface of the fixed scroll 323. The first compression chamber and the second compression chamber are separate from each other and do not communicate. The refrigerant flowing in from the suction port 325 can be distributed to the first compression chamber and the second compression chamber, continuously compressed, and discharged to the discharge port 326.

[0104] An envelope can be formed in the first and second compression chambers along the direction of refrigerant flow, and the shapes of the swirling scroll and the fixed scroll are designed around this envelope. The envelope refers to the trajectory traced by the first and second compression chambers as they move from the suction port 325 to the discharge port 326 as the swirling scroll disk 330 revolves. By using this envelope as a reference and adjusting the swirling radius of the swirling scroll disk parallel to the outer and inner sides, the shapes of the inner surface of the fixed scroll and the outer surface of the swirling scroll, or vice versa, can be formed.

[0105] Reference Figure 4 (a) can be designed to form a pair of envelopes for the first compression chamber and the second compression chamber. In this case, the envelope corresponding to the first compression chamber can be defined as the first envelope S1, and the envelope corresponding to the second compression chamber can be defined as the second envelope S2.

[0106] Reference Figure 4 (b) The first outer envelope S1′ and the second outer envelope S2′ can be designed by offsetting the first envelope S1 and the second envelope S2 outward by a length corresponding to the gyratory radius formed when the gyratory disk 330 rotates.

[0107] Reference Figure 4 (c) The first inner envelope S1″ and the second inner envelope S2″ can be designed by offsetting the first envelope S1 and the second envelope S2 inward by a length corresponding to the gyratory radius formed when the gyratory vortex disk 330 rotates.

[0108] Figure 5 (a) and (b) are diagrams illustrating embodiments of the actual design of swirling and fixed vortices based on the envelope.

[0109] The scroll compressor of this invention can be designed such that the outer ends of both the swirling scroll and the fixed scroll are positioned adjacent to the suction port 325, and the inner ends of both the swirling scroll and the fixed scroll are positioned adjacent to the discharge port 326.

[0110] Furthermore, since the side of the swirling end plate 331 that protrudes from the swirling scroll 333 does not accommodate a rotating shaft or does not pass through a rotating shaft, the design of the swirling scroll 333 can be unaffected by the rotating shaft.

[0111] Reference Figure 5 (a) The shape and thickness of the swirling vortex 333 can be determined by extending the first inner envelope S1″ and the second outer envelope S2′.

[0112] Reference Figure 5 (b) By extending the first outer envelope S1′ and the second inner envelope S2″, the shape and thickness of the fixed vortex 323 can be determined.

[0113] Thus, if the first envelope S1 and the second envelope S2 are determined, the shape and thickness of the fixed vortex 323 and the swirling vortex 333 can be automatically determined.

[0114] Typically, the first envelope S1 and the second envelope S2 can serve as lines tracking the surface-contact movement of the refrigerant, designed identically based on specific rules, formulas, or graphics. That is, the first envelope S1 and the second envelope S2 are designed such that, although the radii of curvature at each point may differ, they are designed according to the same rules and formulas, thus having corresponding shapes. For example, the first envelope S1 and the second envelope S2 can be designed as any shape among circular arcs, algebraic spirals, and involutes. In this case, since the entire area of ​​the first envelope S1 and the second envelope S2, or at least the areas opposite each other, are formed according to the same rules, the spacing, shape, and thickness of the opposing spiral scrolls 333 and the fixed scrolls 323 can correspond to each other.

[0115] However, if the first envelope S1 and the second envelope S2, which serve as the reference for designing the swirling scroll 333 and the fixed scroll 323, are designed as any one of the shapes of an arc, an algebraic spiral, and an involute, then although the swirling scroll 333 and the fixed scroll 323 can be formed as a whole to be stable and regular, there is a problem that sufficient stroke volume cannot be guaranteed.

[0116] In other words, if the swirling scroll 333 and the fixed scroll 323 are arranged according to the same rules and shape, their diameter decreases sharply from the suction port 325 to the discharge port 326. As a result, the stroke volume of the swirling scroll 333 also decreases from the suction port 325 to the discharge port 326. In addition, considering that the smaller the stroke volume, the greater the degree of refrigerant compression, if the swirling scroll 333 is designed with a further reduced radius of curvature to enhance durability, the stroke volume may be further reduced.

[0117] Furthermore, as the diameter of the swirling scroll 333 decreases from the intake port 325 to the outlet port 326, the area in the swirling end plate 331 located at the outermost contour of the swirling scroll 333 is correspondingly wider, thus the area in the swirling end plate 331 that does not participate in compression can be wider.

[0118] This scroll design works well when the compressor compresses relatively small amounts of refrigerant. However, in applications in cold regions where it's difficult to ensure the coefficient of performance (COP) of the heat pump system, or when environmental issues necessitate the use of refrigerants with low heat transfer efficiency, there are issues with increasing the volume of the compressor section 300 or increasing the height of the fixed scroll 323 and the rotating scroll 333. In these cases, while compressor performance can be maintained, the compressor's reliability and durability cannot be guaranteed, and the compressor specifications may change, making it impossible to install the compressor in the necessary product.

[0119] In addition, although a drive method that excessively increases the rotational speed (RPM) of the drive unit 200 can be applied in existing compressors, in this case, the durability of the center of the compressor unit 300 cannot be guaranteed because the refrigerant is over-compressed, or the temperature difference between the intake and exhaust refrigerant will further increase. Therefore, there may be a problem that the thermal expansion coefficient of the inner and outer ends of the swirling scroll and the fixed scroll will further increase, resulting in deformation or damage.

[0120] Therefore, the scroll compressor of this invention makes various design modifications to the envelopes of the first and second compression chambers, so as to maintain the compressor specifications while expanding the stroke volume or ensuring the stability of the rotary and fixed scrolls. For example, the scroll compressor of this invention can use different formulas and rules to design the first and second compression chambers.

[0121] In addition, the scroll compressor of this invention not only maintains the shape of the envelope of the first compression chamber and the second compression chamber, but also increases the stroke volume or improves the durability of the scroll 333 and the fixed scroll 323 by making the thickness of at least a portion of the scroll 333 and the fixed scroll 323 variable.

[0122] As a result, the scroll compressor of this invention can perform any one of the following: changes in the first envelope S1 and the second envelope S2, or changes in the thickness of at least any portion of the swirling scroll and the fixed scroll. Consequently, it can be visually shown that at least one aspect of the thickness and shape of the swirling scroll 333 and at least one aspect of the thickness and shape of the fixed scroll 323 opposite to the swirling scroll 333 are different from each other.

[0123] Figure 6 Figures (a) and (b) are diagrams illustrating a first embodiment of the scroll design of the scroll compressor of this utility model.

[0124] Figure 6 (a) is a diagram showing the shape of the swirling vortex in the first embodiment. Figure 6 (b) is a diagram showing the shape of the fixed vortex in the first embodiment.

[0125] In the scroll compressor of this invention, the swirling scroll 333 can be formed to be thicker than the fixed scroll 323.

[0126] For example, in the thickness of the swirling scroll 333, the thickness of the first, second, third, and fourth portions from the inner outlet 326 to the outer inlet 325 may not vary significantly, but they are all thicker than the first, second, third, and fourth portions of the fixed scroll 323 opposite to the swirling scroll 333. Of course, if the fourth portion of the fixed scroll 323 is equivalent to a fixed end plate or connecting plate, then the thickness of the swirling scroll 333 can be smaller than the thickness of the fourth portion of the fixed scroll 323.

[0127] The swirling scroll 333 can be configured to be thicker than the fixed scroll 323 in all its regions. This ensures the overall durability of the swirling scroll 333, enabling more powerful refrigerant compression. Furthermore, even with a further overall expansion of the diameter or radius of curvature of the swirling scroll 333, a wider stroke volume can be achieved because the rigidity of the swirling scroll 333 can be maintained.

[0128] Figure 7 Figures (a) and (b) are diagrams illustrating a second embodiment of the scroll design of the scroll compressor of this utility model.

[0129] Figure 7 (a) is a diagram showing the shape of the swirling vortex in the second embodiment. Figure 7 (b) is a diagram showing the shape of the fixed vortex in the second embodiment.

[0130] In the compression section 300, since the pressure of the portion adjacent to the outlet 326 is higher than that of the portion adjacent to the inlet 325, the larger the volume of the compression section 300, the more refrigerant can be kept compressed.

[0131] Therefore, in the scroll compressor 333 of this invention, the thickness of the inner end adjacent to the discharge port 326 can be set to be smaller than the thickness of the outer end adjacent to the suction port 325.

[0132] Therefore, more refrigerant can be accommodated in the area adjacent to the outlet 326, thus achieving the effect of increasing the travel volume.

[0133] For example, the thickness of the swirling vortex 333 can gradually decrease from the intake port 325 to the discharge port 326.

[0134] In addition, in the swirling vortex 333, only the region inside the first part surrounding the outlet 326 is thin, while the thickness of the remaining part can be uniform.

[0135] The fixed scroll 323 may have a shape and thickness corresponding to the rotating scroll 333, or, unlike the illustration, may maintain a uniform thickness. In this case, it can compensate for the drastic reduction in the volume of the compression chamber and also ensure the durability of the fixed scroll 323.

[0136] Figure 8 Figures (a) and (b) are diagrams illustrating a third embodiment of the scroll design of the scroll compressor of this utility model.

[0137] Figure 8 (a) is a diagram showing the shape of the swirling vortex in the third embodiment. Figure 8 (b) is a diagram showing the shape of the fixed vortex in the third embodiment.

[0138] The swirling scroll 333 is not limited to any particular shape; the thinner the region opposite the intake 325, the more refrigerant can be drawn into the compression chamber. However, if the region opposite or adjacent to the outlet 326 is thin, while a wider stroke volume can be ensured, durability issues may arise.

[0139] Therefore, to compensate for this problem, the vortex scroll 333 of the scroll compressor of this invention can be configured such that the thickness of the region opposite to or adjacent to the discharge port 326 is greater than the thickness of the region opposite to or adjacent to the suction port 325. That is, the inner end of the vortex scroll 333 can be configured to be thicker than the outer end.

[0140] For example, the swirling vortex 333 can also be configured such that its thickness gradually increases from the intake port 325 to the discharge port 326, and the thickness begins to increase from the portion within the first part.

[0141] The fixed scroll 323 can be configured in the same manner as the swirling scroll 333.

[0142] For example, the fixed vortex 323 may be configured such that the thickness of the region opposite or adjacent to the outlet 326 is greater than the thickness of the region opposite or adjacent to the inlet 325. That is, the inner end of the fixed vortex 333 may be configured to be thicker than the outer end.

[0143] For example, the fixed vortex 323 can be configured to gradually increase in thickness from the inlet 325 to the outlet 326, or it can be configured to increase in thickness from the portion within the first part.

[0144] Figure 9This is a diagram illustrating a fourth embodiment of the scroll design of the scroll compressor of this utility model.

[0145] In the scroll compressor of this invention, unlike the change in scroll thickness, the first envelope S1 and the second envelope S2 can be designed to be different from each other. The shapes of the first envelope S1 and the second envelope S2 can be designed to be different from each other based on the overall shape extending from the outer end to the inner end.

[0146] By designing each part of the first envelope S1 and the second envelope S2 according to different formulas, even if a portion of the regions opposite each other is set with the same formula, regions opposite each other at a position further outward or further inward can be set with completely different formulas. For example, in the third region a3 in the figure, the inner region of the first envelope S1 and the outermost region of the second envelope S2 can be set as an arc shape, set with the same shape or formula. However, although the outermost region of the first envelope S1 is opposite to the second envelope S2 which is set as an arc shape, it can be set with a different shape or formula than the arc-shaped second envelope S2 because it is set as an algebraic spiral or involute shape.

[0147] For example, at least one of the following regions of the first envelope S1, located at 90 degrees relative to the axis of rotation at the outer end adjacent to the inlet 325, and the third region a3, located at 90 degrees relative to the axis of rotation at the end of the first region, can extend as an arc, and at least one of the following regions of the first envelope S1, located at 90 degrees relative to the axis of rotation at the end of the third region, and the fourth region a4, located at 90 degrees relative to the axis of rotation at the end of the second region, can extend as an algebraic spiral.

[0148] The second region a2 can be a region located symmetrically or oppositely to the first region a1, with the center O of the rotation axis or the outlet 326 as a reference.

[0149] As a result, the travel volume can be further expanded compared to when the first envelope S1 and the second envelope S2 are configured with the same shape. For example, the first envelope S1 and the second envelope S2 can be configured as a combination of involute, algebraic spiral, and circle. Thus, the portions of the first envelope S1 and the second envelope S2 extending from the intake port 325 to the discharge port 326 extend with different radii of curvature to achieve the effect of further expanding the first envelope S1 and the second envelope S2.

[0150] Figure 10 This is a diagram illustrating the fifth embodiment of the scroll design of the scroll compressor of this utility model.

[0151] The outermost part of the first region a1 corresponds to the region furthest from the center O from the first envelope S1 and the second envelope S2, and the outermost part of the fourth region a4 corresponds to the region closest to the center O from the first envelope S1 and the second envelope S2.

[0152] Therefore, the scroll compressor of this invention expands the stroke volume by designing the interval between the first envelope S1 and the second envelope S2 in the first region a1 to be larger than in other regions.

[0153] For example, in the scroll compressor of this invention, the intervals A, B, C, and D between the first envelope S1 and the second envelope S2 in the first region a1 can be larger than the intervals a, b, and c between the first envelope S1 and the second envelope S2 in the second region opposite to the first region. This allows for the scroll 333 or the fixed scroll 323 to further expand from the center O towards the outer periphery of the scroll end plate 331 in the first region a1, and achieves the same effect as the center O shifting eccentrically to one side from the scroll end plate 331.

[0154] Furthermore, the intervals a, b, and c between the first envelope S1 and the second envelope S2 in the second region are the same. This allows for a further increase in the travel volume of the first region a1, thereby increasing the overall rate of expansion of the travel volume.

[0155] Furthermore, the interval D between the innermost first envelope S1 and the second envelope S2 and the interval A between the outermost first envelope S1 and the second envelope S2 in the first region a1 can be set to be larger than at least either the interval B or the interval C between the first envelope S1 and the second envelope S2 disposed between A and D.

[0156] As a result, the stroke volume can be further increased compared to the case where the swirling scroll 333 and the fixed scroll 323 are configured with the same spacing or set with the same formula.

[0157] Figure 11 This is a diagram illustrating the sixth embodiment of the scroll design of the scroll compressor of this utility model.

[0158] This invention can expand the travel volume by designing different intervals between the first envelope S1 and the second envelope S2 in each region. For example, the interval of the spiral scroll arranged at the outer end of the spiral scroll in the first region a1, which is located between 90 degrees with respect to the rotation axis, can be formed to be different from at least any one of the intervals of the spiral scroll arranged at the end of the first region, which is located between 90 degrees with respect to the rotation axis, the spiral scroll arranged at the end of the third region a3, which is located between 90 degrees with respect to the rotation axis, the spiral scroll arranged at the end of the third region a3, which is located between 90 degrees with respect to the rotation axis, and the spiral scroll arranged in the fourth region a4, which is located between the end of the second region a2 and the first region.

[0159] That is, the intervals A, B, C, and D of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the first region a1 can be different from at least any one of the intervals i, ii, iii, iv of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the third region, the intervals a, b, and c of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the second region, and the intervals v, vi, and vii of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the fourth region.

[0160] This invention expands the travel volume by designing different intervals between the first envelope S1 and the second envelope S2 of each region. For example, the intervals of the spiral scrolls located at the outer ends of the spiral scrolls in the first region a1, which is positioned between 90 degrees with respect to the rotation axis, the intervals of the spiral scrolls located at the ends of the first region a3, which is positioned between 90 degrees with respect to the rotation axis, the intervals of the spiral scrolls located at the ends of the third region a3, which is positioned between 90 degrees with respect to the rotation axis, and the intervals of the spiral scrolls located at the ends of the second region a2, which is positioned between 90 degrees with respect to the rotation axis, and the intervals of the spiral scrolls located at the ends of the second region a2 and the first region a4 can all be made different.

[0161] That is, the intervals A, B, C, and D of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the first region a1, the intervals i, ii, iii, and iv of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the third region, the intervals a, b, and c of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the second region, and the intervals v, vi, and vii of the first envelope S1 and the second envelope S2 arranged in the order from the outermost to the innermost in the fourth region can all be different.

[0162] On the other hand, the spacing of the spiral scrolls disposed in the first region a1 can be made larger than the spacing of the spiral scrolls disposed in the third region a3, and the spacing of the spiral scrolls disposed in the third region a3 can be made larger than the spacing of the spiral scrolls disposed in the second region a2. As a result, by expanding the spacing between the outermost first envelope S1 and the second envelope S2, the area occupied by the entire envelope can be expanded, and the stroke volume can be increased relative to the area of ​​the same spiral endplate.

[0163] This utility model can be implemented in various forms and modifications; therefore, the scope of this utility model is not limited to the above-described embodiments. Thus, if a modified embodiment includes elements within the scope of the claims of this utility model, it should be considered to fall within the scope of this utility model.

Claims

1. A scroll compressor characterized by, include: case; A fixed scroll plate is attached to the housing and includes a fixed end plate and a fixed scroll. The fixed end plate includes an intake port for drawing in refrigerant and an outlet port disposed further inside the intake port for discharging the refrigerant. The fixed scroll extends from the intake port to the outlet port on the fixed end plate. as well as A swirling scroll disk, comprising a swirling end plate and a swirling scroll, wherein the swirling end plate is configured to face a fixed end plate, and the swirling scroll extends from the swirling end plate to face the fixed scroll, for compressing the refrigerant; The thickness or shape of the swirling vortex is formed to be different from the thickness or shape of the fixed vortex opposite to the swirling vortex.

2. The scroll compressor according to claim 1, characterized in that, The swirling vortex is formed to be thicker than the fixed vortex.

3. The scroll compressor according to claim 1, characterized in that, The vortex is configured to increase in thickness as it approaches the outlet from the intake port.

4. The scroll compressor according to claim 1, characterized in that, The vortex is configured such that its thickness decreases as it approaches the outlet from the intake port.

5. The scroll compressor according to claim 1, characterized in that, It also includes a drive unit, which includes a rotating shaft supported by the swivel end plate and rotatable, causing the swivel end plate to rotate relative to the fixed end plate. At the outer end of the vortex opposite the intake port, the spacing of the vortexes disposed in the first region is set to be larger than the spacing of the vortexes disposed in regions other than the first region, the first region being equivalent to 90 degrees centered on the axis of rotation.

6. The scroll compressor according to claim 5, characterized in that, In the swirling vortex, the swirling vortices arranged in the second region are spaced equally, and the second region corresponds to the opposite side of the first region with respect to the rotation axis.

7. The scroll compressor according to claim 5, characterized in that, In the fixed vortex, the spacing between the fixed vortexes opposite to the swirling vortexes disposed in the first region is set to be larger than the spacing between the fixed vortexes disposed in regions other than the first region.

8. The scroll compressor according to claim 6, characterized in that, In the fixed vortex, the spacing between the fixed vortex and the swirling vortex disposed in the second region is formed to be the same for each other.

9. The scroll compressor according to claim 1, characterized in that, The swirling vortex extends from the outer end opposite the intake port to the inner end opposite the exhaust port in a combination of arc and algebraic spiral shapes.

10. The scroll compressor according to claim 9, characterized in that, The swirling spiral extends first in an arc shape at its outer end and then in an algebraic spiral shape.

11. The scroll compressor according to claim 9, characterized in that, It also includes a drive unit, which includes a rotating shaft supported by the swivel end plate and rotatable, causing the swivel end plate to rotate relative to the fixed end plate. The swirling spiral extends in a 180-degree arc shape at its outer end with respect to the rotation axis, and then extends in an algebraic spiral shape of more than 90 degrees with respect to the rotation axis.

12. The scroll compressor according to claim 9, characterized in that, It also includes a drive unit, which includes a rotating shaft supported by the swivel end plate and rotatable, causing the swivel end plate to rotate relative to the fixed end plate. The swirling spiral extends in an arc shape within a 180-degree region at the outer end with respect to the axis of rotation, and extends in an algebraic spiral shape outside this region.

13. The scroll compressor according to claim 1, characterized in that, It also includes a drive unit, which includes a rotating shaft supported by the swivel end plate and rotatable, causing the swivel end plate to rotate relative to the fixed end plate. The spacing of the vortex arranged at the outer end of the vortex adjacent to the inlet in the first region with respect to the rotation axis and located in a first region at 90 degrees is different from the spacing of the vortex arranged at the end of the first region with respect to the rotation axis and located in a third region at 90 degrees, the spacing of the vortex arranged at the end of the third region with respect to the rotation axis and located in a second region at 90 degrees, and the spacing of the vortex arranged in a fourth region located between the end of the second region and the first region.

14. The scroll compressor according to claim 13, characterized in that, The spacing of the vortexes arranged at the outer ends adjacent to the intake port in the vortex, in the first region with the rotation axis as a reference and located in a 90-degree range; the spacing of the vortexes arranged at the end of the first region with the rotation axis as a reference and located in the third region with the rotation axis as a reference and located in a 90-degree range; the spacing of the vortexes arranged at the end of the third region with the rotation axis as a reference and located in the second region with the rotation axis as a reference and located in the second region with the fourth region located between the end of the second region and the first region are all formed differently.

15. The scroll compressor according to claim 14, characterized in that, The spacing of the swirling vortices configured in the first region is larger than the spacing of the swirling vortices configured in the third region, and the spacing of the swirling vortices configured in the third region is larger than the spacing of the swirling vortices configured in the second region.

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