Compressor and air conditioner

Abstract

A compressor and an air conditioner. The compressor comprises a compressor body, a gas-liquid separator and two brackets, wherein the compressor body comprises a first housing; the gas-liquid separator is arranged outside the first housing; the two brackets are symmetrically arranged, and are configured to connect the first housing and a second housing of the gas-liquid separator; and any one of the two brackets comprises a bracket part I, a bracket part II, a bracket part III and a bracket part IV, which are connected in sequence, the bracket part I and the bracket part III being located on the same side of the bracket part II, the bracket part II and the bracket part IV being located on different sides of the bracket part III, the bracket part II being adapted to the outer contour of the second housing and being fixedly connected to the second housing, the bracket part I and the bracket part III extending between the first housing and the second housing, the bracket part I and the bracket part IV being fixedly connected to the first housing, the length of the bracket part I being greater than that of the bracket part III, and the two bracket parts IV of the two brackets being close to each other.

Description

Compressors and air conditioners

[0001] This application claims priority to Chinese patent application No. 202421482964.X, filed on June 26, 2024; Chinese patent application No. 202421480423.3, filed on June 26, 2024; Chinese patent application No. 202421479969.7, filed on June 26, 2024; Chinese patent application No. 202421480001.6, filed on June 26, 2024; and Chinese patent application No. 202421482929.8, filed on June 26, 2024. Priority claims to Chinese patent applications filed on June 26, 2024, No. 202421480559.4, No. 202421480052.9, No. 202421479892.3, No. 202421482924.5, and No. 202421479904.2, all the contents of which are incorporated herein by reference. Technical Field

[0002] This disclosure relates to the field of air conditioning technology, and more particularly to a compressor and an air conditioner. Background Technology

[0003] Air conditioners execute their cooling and heating cycles using a compressor, condenser, expansion valve, and evaporator. In a rotary compressor, the compressor consists of a compressor body and a gas-liquid separator. The gas-liquid separator is configured to separate the liquid refrigerant from the gaseous refrigerant to prevent liquid refrigerant from entering the compression chamber of the compressor body and causing compressor malfunction.

[0004] Summary of the Invention

[0005] On one hand, a compressor is provided. The compressor includes a compressor body, a gas-liquid separator, and two supports. The compressor body includes a first housing, within which a compression mechanism is disposed, configured to compress refrigerant. The gas-liquid separator is disposed outside the first housing and configured to provide gaseous refrigerant to the compression chamber of the compression mechanism. The two supports are symmetrically arranged and configured to connect the first housing and the second housing of the gas-liquid separator. Each of the two supports includes a first support, a second support, a third support, and a fourth support connected sequentially. The first support and the third support are located on the same side of the second support, and the second support and the fourth support are located on opposite sides of the third support. The second support is adapted to and fixedly connected to the outer contour of the second housing. The first support and the third support extend between the first housing and the second housing, respectively, and the first support and the fourth support are fixedly connected to the first housing. The length of the first support is greater than the length of the third support. The two fourth supports of the two supports are close to each other.

[0006] On the other hand, an air conditioner is provided. The air conditioner includes a compressor, an evaporator, a condenser, and a throttling device. The compressor is the compressor described above. Attached Figure Description

[0007] Figure 1 is a structural diagram of a compressor according to some embodiments;

[0008] Figure 2A is a side view of a compressor according to some embodiments;

[0009] Figure 2B is a cross-sectional view of a compressor according to some embodiments;

[0010] Figure 3 is a top view of a compressor according to some embodiments;

[0011] Figure 4 is a structural diagram of a bracket according to some embodiments;

[0012] Figure 5 is another structural diagram of the bracket according to some embodiments;

[0013] Figure 6 is another top view of a compressor according to some embodiments;

[0014] Figure 7 is another structural diagram of the bracket according to some embodiments;

[0015] Figure 8 is a structural diagram of a bracket and a circumferential housing according to some embodiments;

[0016] Figure 9 is a cross-sectional view of a gas-liquid separator according to some embodiments;

[0017] Figure 10 is a structural diagram of the floating part after it floats according to some embodiments;

[0018] Figure 11 is a structural diagram of the floating part after it has been lowered according to some embodiments;

[0019] Figure 12 is a structural diagram of a floating part according to some embodiments;

[0020] Figure 13 is a structural diagram of a compressor body according to some embodiments;

[0021] Figure 14 is a structural diagram of an upper housing according to some embodiments;

[0022] Figure 15 is a cross-sectional view of a first housing according to some embodiments;

[0023] Figure 16A is a magnified view of a portion of circle A in Figure 15;

[0024] Figure 16B is a magnified view of the area circled B in Figure 15;

[0025] Figure 17 is a cross-sectional view of the upper housing according to some embodiments;

[0026] Figure 18 is a structural diagram of a lower housing according to some embodiments;

[0027] Figure 19 is a structural diagram of the lower housing and adsorption part according to some embodiments;

[0028] Figure 20 is a structural diagram of an adsorption section according to some embodiments;

[0029] Figure 21 is a cross-sectional view of a compression mechanism according to some embodiments;

[0030] Figure 22 is a structural diagram of a third sub-silencer according to some embodiments;

[0031] Figure 23 is another structural diagram of the third sub-silencer according to some embodiments;

[0032] Figure 24 is a structural diagram of a fourth sub-silencer according to some embodiments;

[0033] Figure 25 is a cross-sectional view of an eccentric crankshaft, a second bearing, a second cylinder, and a second piston according to some embodiments;

[0034] Figure 26 is a structural diagram of an exhaust valve plate and a lift limiter according to some embodiments;

[0035] Figure 27 is another structural diagram of the exhaust valve plate and the lift limiter according to some embodiments;

[0036] Figure 28 is a structural diagram of an exhaust valve plate according to some embodiments;

[0037] Figure 29 is a structural diagram of a compressor body, exhaust pipe, and muffler according to some embodiments;

[0038] Figure 30 is a structural diagram of a muffler according to some embodiments;

[0039] Figure 31 is a structural diagram of an eccentric crankshaft according to some embodiments. Detailed Implementation

[0040] The following description, in conjunction with the accompanying drawings, clearly and completely describes some embodiments of this disclosure. Obviously, the described embodiments are merely some, not all, of the embodiments of this disclosure. All other embodiments obtained by those skilled in the art based on the embodiments provided in this disclosure are within the scope of protection of this disclosure.

[0041] Unless the context otherwise requires, throughout the specification and claims, the term "comprise" and its other forms, such as the third-person singular "comprises" and the present participle "comprising," are interpreted as open-ended and encompassing, meaning "including, but not limited to." In the description of the specification, terms such as "one embodiment," "some embodiments," "exemplary embodiments," "example," "specific example," or "some examples," etc., are intended to indicate that a particular feature, structure, material, or characteristic associated with that embodiment or example is included in at least one embodiment or example of this disclosure. The illustrative representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics mentioned may be included in any suitable manner in any one or more embodiments or examples.

[0042] Hereinafter, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of embodiments of this disclosure, unless otherwise stated, "a plurality of" means two or more.

[0043] In describing some embodiments, the terms "coupled" and "connected," and their derivative expressions, may be used. The term "connected" should be interpreted broadly; for example, a "connection" can be a fixed connection, a detachable connection, or an integral part; it can be a direct connection or an indirect connection through an intermediate medium. The term "coupled" indicates that two or more components have direct physical or electrical contact. The term "coupled" or "communicatively coupled" may also refer to two or more components that do not have direct contact with each other but still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the content of this document.

[0044] "At least one of A, B and C" has the same meaning as "at least one of A, B or C", both including the following combinations of A, B and C: only A, only B, only C, combinations of A and B, combinations of A and C, combinations of B and C, and combinations of A, B and C.

[0045] "A and / or B" includes the following three combinations: A only, B only, and a combination of A and B.

[0046] The use of “applies to” or “configured to” in this article implies an open and inclusive language that does not preclude applicability to or configuration to devices that perform additional tasks or steps.

[0047] As used herein, “about,” “approximately,” or “approximately” includes the stated value and the average value within an acceptable range of deviation from the given value, wherein the acceptable range of deviation is determined by a person skilled in the art taking into account the measurement under discussion and the error associated with the measurement of the given quantity (i.e., the limitations of the measurement system).

[0048] As used herein, “parallel,” “perpendicular,” and “equal” include the described situation and situations that are similar to the described situation, within an acceptable range of deviation, which is determined by those skilled in the art taking into account the measurement under discussion and the error associated with the measurement of a particular quantity (i.e., the limitations of the measurement system). For example, “parallel” includes absolute parallelism and approximate parallelism, where an acceptable range of deviation for approximate parallelism may be, for example, within 5°; “perpendicular” includes absolute perpendicularity and approximate perpendicularity, where an acceptable range of deviation for approximate perpendicularity may also be, for example, within 5°; “equal” includes absolute equality and approximate equality, where an acceptable range of deviation for approximate equality may be, for example, a difference between the two equals being less than or equal to 5% of either one.

[0049] [Air conditioner]

[0050] In some embodiments, an air conditioner performs a cooling or heating cycle by using a compressor, a condenser, an expansion valve, and an evaporator. The cooling or heating cycle includes a series of processes involving compression, condensation, expansion, and evaporation to cool or heat an indoor space.

[0051] Low-temperature, low-pressure refrigerant enters the compressor, which compresses it into a high-temperature, high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the surrounding environment through the condensation process.

[0052] The expansion valve expands the high-temperature, high-pressure liquid refrigerant that condenses in the condenser into a low-pressure liquid refrigerant. The evaporator evaporates the expanded refrigerant in the expansion valve and returns the low-temperature, low-pressure refrigerant gas to the compressor. The evaporator achieves its cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material being cooled. Throughout the cycle, the air conditioner regulates the temperature of the indoor space.

[0053] The outdoor unit of an air conditioner refers to the part of the refrigeration cycle that includes the compressor and the outdoor heat exchanger. The indoor unit of an air conditioner includes the indoor heat exchanger, and the expansion valve can be provided in either the indoor or outdoor unit.

[0054] The indoor and outdoor heat exchangers function as either condensers or evaporators. When the indoor heat exchanger is used as a condenser, the air conditioner operates in heating mode; when it is used as an evaporator, the air conditioner operates in cooling mode.

[0055] The outdoor unit also includes a four-way valve, which is configured to allow the indoor and outdoor heat exchangers to switch between acting as condensers or evaporators.

[0056] The working principle of an air conditioner is as follows: The compressor operates to bring the indoor heat exchanger (which is the evaporator in the indoor unit) to an ultra-low pressure state. The liquid refrigerant in the indoor heat exchanger evaporates rapidly and absorbs heat. The air blown out by the indoor fan is cooled by the indoor heat exchanger coil and then blown into the room as cold air. The vaporized refrigerant is pressurized by the compressor and then condenses into a liquid state in the high-pressure environment of the outdoor heat exchanger (which is the condenser in the outdoor unit), releasing heat. The heat is then dissipated into the atmosphere by the outdoor fan. This cycle achieves the cooling effect.

[0057] The heating principle of an air conditioner is as follows: Gaseous refrigerant is pressurized by the compressor, becoming a high-temperature, high-pressure gas. This gas enters the indoor heat exchanger (which acts as a condenser), where it condenses and liquefies, releasing heat and becoming a liquid. Simultaneously, it heats the indoor air, thus raising the indoor temperature. The liquid refrigerant is then depressurized by a throttling device and enters the outdoor heat exchanger (which acts as an evaporator). There, it evaporates and absorbs heat, becoming a gas. Simultaneously, it absorbs heat from the outdoor air (making the outdoor air cooler), becoming a gaseous refrigerant again, which then re-enters the compressor to begin the next cycle.

[0058] [Compressor Body]

[0059] In some embodiments of this disclosure, the compressor is a rolling rotor compressor. Referring to Figures 1 and 2A, the compressor includes a compressor body 1. The compressor body 1 includes a first housing 11, within which a closed inner cavity is formed. A motor 13 and a compression mechanism 14 are disposed within the inner cavity. The motor 13 provides power to the compressor mechanism. The compression mechanism 14 is configured to compress the refrigerant. The motor 13 is located above the compression mechanism 14. Figure 21 is a cross-sectional view of the compression mechanism 14.

[0060] In some embodiments, referring to FIG13, the first housing 11 includes an upper housing 410, a circumferential housing 430, and a lower housing 420. The circumferential housing 430 is disposed between the upper housing 410 and the lower housing 420. The upper housing 410 is disposed at the top of the circumferential housing 430, and the lower housing 420 is disposed at the bottom of the circumferential housing 430. The upper housing 410, the circumferential housing 430, and the lower housing 420 form the inner cavity of the compressor body 1.

[0061] In some embodiments, the motor 13 includes a stator and a rotor, with the stator fixedly connected to the inner wall of the first housing 11 to achieve fixed installation of the motor 13 in the compressor cavity.

[0062] In some embodiments, referring to FIG21, the compression mechanism 14 includes an eccentric crankshaft 110, a cylinder, a piston, a bearing, a muffler, etc.

[0063] In some embodiments, referring to FIG31, the eccentric crankshaft 110 includes a first shaft section 111 (upper shaft section), an eccentric shaft section, and a second shaft section 115 (lower shaft section). The first shaft section 111 is fixedly connected to the rotor. A piston is provided in the compression chamber of the cylinder, and the piston is sleeved on the eccentric shaft section. A bearing is fixedly connected to the cylinder, and a bearing exhaust hole is provided on the bearing, which communicates with the compression chamber. A sliding vane groove is provided on the cylinder, and a sliding vane is provided in the sliding vane groove. The eccentric crankshaft 110 drives the piston to make circumferential movements in the compression chamber, and the sliding vane reciprocates along the sliding vane groove. The sliding vane always abuts against the piston, and the sliding vane and the piston divide the compression chamber into a high-pressure chamber and a low-pressure chamber.

[0064] The working principle of the compressor is as follows: After the stator of motor 13 is energized, it generates magnetic pull. The rotor of motor 13 rotates under the action of the magnetic pull of the stator, and drives the eccentric crankshaft 110 to rotate together. The rotation of the eccentric crankshaft 110 drives the piston sleeved on its eccentric shaft section to make eccentric circular motion in the compression chamber of the cylinder. The sliding vane makes reciprocating motion in the sliding vane groove. The sliding vane and the piston divide the compression chamber of the cylinder into a high-pressure chamber and a low-pressure chamber. When the eccentric crankshaft 110 drives the piston to rotate one revolution, it draws in air from the low-pressure chamber and exhausts air from the high-pressure chamber to complete one exhaust cycle, realizing the compression of gas by the compressor. The compressed gas is discharged through the bearing exhaust port.

[0065] In some disclosed embodiments, the compressor is a dual-cylinder rolling rotor compressor. Referring to FIG21, the compression mechanism 14 specifically includes an eccentric crankshaft 110, two cylinders (a first cylinder 122 (upper cylinder) and a second cylinder 121 (lower cylinder) respectively), two bearings (a first bearing 152 (upper bearing) and a second bearing 151 (lower bearing) respectively), two pistons (a first piston 132 (upper piston) and a second piston 131 (lower piston) respectively), a partition plate 160, and two mufflers (a first sub-muffler 142 (upper muffler) and a second sub-muffler 141 (lower muffler) respectively).

[0066] In some embodiments, referring to FIG31, the eccentric crankshaft 110 includes, from top to bottom, a first shaft segment 111, a first eccentric shaft segment 112 (upper eccentric shaft segment), a connecting shaft segment 113, a second eccentric shaft segment 114 (lower eccentric shaft segment), and a second shaft segment 115.

[0067] In some embodiments, the compression chamber of the first cylinder 122 is provided with a first piston 132 capable of eccentric movement, and the first piston 132 is sleeved on the first eccentric shaft section 112; the compression chamber of the second cylinder 121 is provided with a second piston 131 capable of eccentric movement, and the second piston 131 is sleeved on the second eccentric shaft section 114; a partition plate 160 is sleeved on the connecting shaft section 113, and the partition plate 160 is located between the first cylinder 122 and the second cylinder 121; a first bearing 152 is sleeved on the first shaft section 111 and is simultaneously connected to the first cylinder 122; a second bearing 151 is sleeved on the second shaft section 115 and is simultaneously connected to the second cylinder 121.

[0068] The first eccentric shaft section 112 and the second eccentric shaft section 114 are arranged at a relative angle of 180°. The first piston 132 and the second piston 131 rotate eccentrically at the same time. The compressed air in the compression chamber of the first cylinder 122 is discharged through the exhaust port on the first bearing 152, and the compressed air in the compression chamber of the second cylinder 121 is discharged through the exhaust port on the second bearing 151.

[0069] Referring to Figure 21, a first sub-muffler 142 is provided on the first bearing 152. The first sub-muffler 142 covers the exhaust port of the first bearing 152. The compressed air in the first cylinder 122 is first discharged through the exhaust port of the first bearing 152 into the space enclosed by the first sub-muffler 142 and the first bearing 152, and then discharged through the exhaust port of the first sub-muffler 142 into the inner cavity of the compressor.

[0070] A second sub-muffler 141 is provided on the second bearing 151. The second sub-muffler 141 covers the exhaust port of the second bearing 151. The compressed air in the second cylinder 121 is first discharged through the exhaust port on the second bearing 151 to the space enclosed by the second sub-muffler 141 and the second bearing 151.

[0071] In some embodiments, unlike related technologies, the second sub-muffler 141 in FIG21 does not have an exhaust port. Multiple vertically penetrating airflow channels 170 are provided on the walls of the first bearing 152, the first cylinder 122, the partition plate 160, the second cylinder 121, and the second bearing 151. Compressed air in the second bearing 151 and the second sub-muffler 141 is discharged upwards through the airflow channels 170 into the space enclosed by the first bearing 152 and the first sub-muffler 142, and then discharged into the compressor cavity through the exhaust port of the first sub-muffler 142.

[0072] [Gas-Liquid Separator]

[0073] In some embodiments, referring to FIG1, the compressor further includes a gas-liquid separator 2. The gas-liquid separator 2 is disposed outside the compressor body 1 and configured to supply gaseous refrigerant to the compression chamber of the compression mechanism 14. The gas-liquid separator 2 performs the separation of liquid refrigerant and gaseous refrigerant to prevent liquid refrigerant from entering the compression chamber of the compressor body 1 and causing compressor malfunction.

[0074] In some embodiments, referring to Figures 1 and 9, the gas-liquid separator 2 includes a second housing 21, and an outlet pipe 22 is provided at the bottom of the second housing 21. One end of the outlet pipe 22 extends into the inner cavity of the second housing 21, and the other end of the outlet pipe 22 is connected to the compression mechanism 14 to provide gaseous refrigerant to the compression mechanism 14.

[0075] [Connection structure between the compressor body and the gas-liquid separator]

[0076] Currently, the gas-liquid separator 2 is fixedly mounted on the outside of the compressor body 1 via a bracket 200. During compressor operation, the compressor body 1 and the gas-liquid separator 2 are prone to low-frequency resonance, generating low-frequency noise. Therefore, it is necessary to increase the natural frequency of the upper rotation of the gas-liquid separator 2 to avoid low-frequency resonance between the compressor body 1 and the gas-liquid separator 2 during operation. In related technologies, the natural frequency of the gas-liquid separator 2 is relatively low, making it prone to generating low-frequency noise during compressor operation.

[0077] To address the aforementioned issues, this disclosure includes improvements to the connection structure between the gas-liquid separator 2 and the compressor body 1, thereby increasing the natural frequency of the gas-liquid separator 2 and preventing low-frequency noise from being generated during compressor operation.

[0078] The following describes an embodiment of the connection structure between the gas-liquid separator 2 and the compressor body 1.

[0079] [An embodiment of the connection structure between the compressor body and the gas-liquid separator]

[0080] In some embodiments, referring to Figures 3 to 5, the compressor includes two symmetrically arranged supports 200, which are configured to connect a first housing 11 and a second housing 21.

[0081] Each of the two supports 200 includes a first support 210, a second support 220, a third support 230, and a fourth support 240 connected sequentially. The first support 210 and the third support 230 are located on the same side of the second support 220, while the second support 220 and the fourth support 240 are located on different sides of the third support 230. The second support 220 is adapted to and fixedly connected to the outer contour of the second housing 21, for example, by welding. The first support 210 and the third support 230 extend between the first housing 11 and the second housing 21, respectively. The first support 210 and the fourth support 240 are fixedly connected to the first housing 11, for example, by welding. The length of the first support 210 is greater than the length of the third support 230, and the two fourth supports 240 are close to each other.

[0082] For each bracket 200, it is fixed to the first housing 11 at two points by welding bracket part 210 and bracket part 240 together. When two brackets 200 are used together, there are four points of fixation on the first housing 11, which improves the connection stability between the bracket 200 and the first housing 11. For example, when two brackets 200 are used together, the two bracket parts 220 together clamp the gas-liquid separator 2, which improves the connection stability between the bracket 200 and the second housing 21.

[0083] In some embodiments, referring to FIG5, an opening is provided on a bracket portion 210, namely a first opening 250. The first opening 250 extends along the length direction of the bracket portion 210. The width of the first opening 250 is H, and the length of the first opening 250 is L, where H / L = (0, 0.82).

[0084] By changing the size of the first opening 250, the connection stiffness of the gas-liquid separator 2 can be changed, which is beneficial for obtaining the required natural frequency.

[0085] In some embodiments, referring to Figures 3 and 4, the width of the support portion 220 is W3, the outer radius of the second housing 21 is R2, and the range of W3 / R2 is [1.4, 2.2]. Within this range, it helps to increase the natural frequency of the gas-liquid separator 2.

[0086] In some embodiments, referring to FIG3, the radius of the arc-shaped structure where the second bracket 220 is located is R3, and the outer contour radius of the second housing 21 is R2, where R3-R2 = [0.5mm, 2mm]. Within this range, it is beneficial to achieve welding, installation, and positioning between the two.

[0087] In some embodiments, referring to FIG3, the arc α of the second part 220 of the support is greater than 39°, which helps to improve the clamping reliability of the support 200 on the gas-liquid separator 2.

[0088] In some embodiments, referring to FIG3, the distance from the junction of the first bracket 210 and the second bracket 220 to the plane of symmetry of the two brackets 200 is W1, the distance from the third bracket 230 to the plane of symmetry of the two brackets 200 is W2, the outer contour radius of the second housing 21 is R2, the outer contour radius of the first housing 11 is R1, and (W1 / R2)×(W2 / R1)>0.3. Within the above range, the double torsional frequency of the gas-liquid separator 2 tends to stabilize, and the fixed frequency is increased to above 510Hz, which is suitable for a twin-cylinder compressor with a maximum speed of 180rpm.

[0089] In some embodiments, referring to Figures 3 and 4, the bracket part 210 includes a bracket part section 211 and a bracket part section 212 with an integral structure. The bracket part section 211 extends obliquely outward from the first end of the bracket part section 212. The bracket part section 211 is adapted to and fixedly connected to the first housing 11. The second end of the bracket part section 212 intersects and connects with the bracket part 220.

[0090] The angle β between the line connecting the second end of the first section 212 of the bracket and the end of the first section 211 of the bracket and the second section 212 of the bracket is 2°.

[0091] In some embodiments, the number of weld points between the bracket part 210 and the first housing 11 is greater than 2, for example, 4, and the number of weld points between the bracket part 240 and the first housing 11 is also greater than 2, for example, 4. This can improve the connection reliability between the bracket part 210 and the first housing 11, as well as the connection reliability between the bracket part 240 and the first housing 11.

[0092] In some embodiments, referring to FIG2A, the height of the compressor body 1 is H1, specifically the distance between the bottom of the lower housing 420 and the top of the exhaust pipe 12. The height of the bracket 200 from the bottom of the compressor body 1 (referring to the bottom of the lower housing 420) is H2, where H2 / H1 = [0.49, 0.71]. Within this range, it helps to reduce the radial vibration of the gas-liquid separator 2, which is beneficial to reducing compressor noise.

[0093] In some embodiments, referring to FIG3, the distance between the connection positions of the two bracket portions 210 and the first housing 11 is D2, the outer diameter of the first housing 11 is D1, and D2 / D1 = [0.06, 0.9]. Within this range, it helps to reduce the radial vibration of the gas-liquid separator 2, which is beneficial to reducing compressor noise.

[0094] In some embodiments, referring to Figures 6 and 7, the compressor includes a bracket 200 configured to connect a first housing 11 and a second housing 21.

[0095] The bracket 200 includes a bracket body 260, with bracket extensions 270 symmetrically arranged at opposite ends of the bracket body 260. The bracket body 260 is adapted to and fixedly connected to the outer contour of the first housing 11, for example, by welding. The bracket extensions 270 are integrally structured and include an extension section 271 and an extension section 272. The extension section 271 is connected between the bracket body 260 and the extension section 272. The extension section 272 is fixedly connected to the outer contour of the second housing 21, for example, by welding.

[0096] Referring to Figure 6, for example, the outer radius of the first housing 11 is R1, the outer radius of the second housing 21 is R2, and the distance between the extension section 271 and the plane of symmetry of the support 200 is W4, where 2W4 / (R1+R2) = [0.35, 0.55]. Within this range, it helps to reduce the vibration of the gas-liquid separator 2.

[0097] In some embodiments, referring to FIG7, the distance between the weld point 280 between the main body 260 of the bracket and the first housing 11 and the plane of symmetry of the bracket 200 is W5, and W5 / W4 > 0.75. The larger W5 / W4 is, the better. When it is greater than 0.75, the vibration increase of the gas-liquid separator 2 is not obvious.

[0098] In some embodiments, referring to FIG7, the extension section 272 is welded to the second housing 21, the distance between two adjacent weld points 280 along the height direction of the extension section 272 is H3, the height of the extension section 272 is H4, and H3 / H4 = [0.75, 0.85].

[0099] Two welding holes 290 are provided on each extension section 272. The distance between two adjacent welding holes 290 is equal to the distance between two welding points 280, which is also H3. It should be noted that the distance between two adjacent welding holes 290 also meets the above range setting, which helps to reduce the vibration of the gas-liquid separator 2.

[0100] In some embodiments, referring to FIG7, the height of the support body 260 is H4, and referring to FIG8, the distance between the support body 260 and the outlet pipe 22 of the gas-liquid separator 2 is H5, where H4 / H5 = [0.2, 0.35]. Within this range, it helps to reduce the vibration of the gas-liquid separator 2.

[0101] In some embodiments, referring to FIG6, the angle θ between the vertical line connecting the two extension segments 272 and the axis of the second housing 21 is in the range of [90°, 140°]. This range helps to reduce the vibration of the gas-liquid separator 2 and increase the torsional frequency of the gas-liquid separator 2.

[0102] In some embodiments, referring to FIG2A, a foot 15 is provided on the side of the first housing 11, the radius of the foot 15 is R8, the outer contour radius of the first housing 11 is R9, and R8 / R9>0.15. Within this range, the compressor body 1 has better stability and lower vibration.

[0103] In some embodiments, referring to FIG2A, the height of the first housing 11 is H1. The distance between the motor 13 and the top of the first housing 11 is H15, where H15 / H1 = [0.25-0.35].

[0104] There is a certain cavity volume between the upper part of the motor 13 and the upper housing 410. The larger the cavity, the better the oil separation effect and the lower the oil discharge rate. Since the cavity volume is also related to the compressor noise level, setting the above range helps to reduce compressor noise.

[0105] [Gas outlet pipe of the gas-liquid separator]

[0106] In some embodiments, the liquid is stored at the bottom of the gas-liquid separator 2, and an oil return hole 2201 is provided on the outlet pipe 22 of the gas-liquid separator 2. When the compressor body 1 is superheated during suction, the separated liquid is refrigeration oil, and the oil return hole 2201 needs to be as large as possible to allow the refrigeration oil to flow back to the compressor body 1 quickly through the oil return hole 2201. When the compressor body 1 is not superheated, the separated liquid is liquid refrigerant. In this case, in order to reduce the rate at which the liquid refrigerant enters the compressor body 1 through the oil return hole 2201, a smaller oil return hole 2201 is required.

[0107] In related technologies, the size of the oil return hole 2201 is fixed and cannot be adjusted according to the operating conditions of the compressor body 1. It cannot balance accelerating the return of refrigeration oil when overheating and reducing the return of liquid refrigerant when there is no overheating.

[0108] In some embodiments, the outlet pipe 22 is improved to accelerate the return of refrigeration oil and reduce the rate at which liquid refrigerant enters the compressor body 1, thereby improving compressor efficiency.

[0109] For example, referring to Figures 9 to 12, the vent pipe 22 located within the cavity has multiple oil return holes 2201, which are spaced apart along the height of the vent pipe 22. For instance, the vent pipe 22 may have two oil return holes 2201 arranged at intervals, one above the other.

[0110] The gas-liquid separator 2 includes a floating part 300, which is sleeved on the gas outlet pipe 22 and located inside the cavity. The floating part 300 is configured to move along the height direction of the gas outlet pipe 22.

[0111] In some embodiments, referring to FIG11, when the compressor intake is overheated, the floating part 300 descends to the first position, at which time the plurality of oil return holes 2201 are in an open state, thereby increasing the oil return rate.

[0112] Referring to Figure 10, when the compressor does not overheat during intake, the liquid level inside the gas-liquid separator 2 will rise rapidly. The floating part 300 floats to the second position under the buoyancy of the liquid in the cavity, and part of the oil return hole 2201 is blocked, reducing the rate at which liquid refrigerant flows into the compressor body 1 and preventing liquid slugging.

[0113] Taking the setting of two oil return holes 2201 as an example, when the floating part 300 descends to the first position, both oil return holes 2201 are in an open state. When the floating part 300 rises to the second position, the floating part 300 blocks the upper oil return hole 2201 and opens the lower oil return hole 2201.

[0114] In some embodiments, referring to Figures 9 and 12, the floating part 300 includes a floating main body 310, which is sleeved on the vent pipe 22. A gap 350 for liquid flow is provided between the floating main body 310 and the vent pipe 22. An opening, a second opening 340, is provided on the floating main body 310, communicating with the gap 350. Liquid enters the gap 350 through the second opening 340 and then flows out through the oil return hole 2201.

[0115] The combination of the second opening 340 and the gap 350 ensures that when the floating part 300 rotates along the air outlet pipe 22, the liquid can still flow smoothly out along the oil return hole 2201.

[0116] A folding part 320 is provided at the bottom of the floating main body 310. The folding part 320 folds inward towards the inside of the floating main body 310 and is sleeved on the air outlet pipe 22. The gap between the folding part 320 and the air outlet pipe 22 is small, and the two are in clearance fit, which does not affect the up and down movement of the floating part 300 along the air outlet pipe 22. Furthermore, when the folding part 320 is directly opposite the oil return hole 2201, the folding part 320 acts to block the oil return hole 2201.

[0117] The folding part 320 is configured to block part of the oil return hole 2201 when the floating part 300 is in the second position. In other words, taking the example of having two oil return holes 2201, when the floating part 300 floats to the second position, the folding part 320 is directly opposite the upper oil return hole 2201, and the folding part 320 blocks the upper oil return hole 2201.

[0118] The folding portion 320 is also configured to move away from the oil return hole 2201 when the floating portion 300 is in the first position, so that the oil return hole 2201 is open. In other words, taking the example of providing two oil return holes 2201, when the floating portion 300 descends to the first position, the folding portion 320 is offset from the oil return hole 2201, so that all oil return holes 2201 are in an open state.

[0119] In some embodiments, the floating main body 310 and the folding part 320 are integrally formed, and the floating main body 310 and the folding part 320 are connected by an arc transition. A step part 2202 is provided on the air outlet pipe 22, and the step part 2202 is configured to limit the descent position of the floating part 300.

[0120] The step portion 2202 on the vent pipe 22 restricts the downward displacement of the floating portion 300, preventing the floating portion 300 from hitting the bottom wall of the gas-liquid separator 2.

[0121] In some embodiments, the second opening 340 extends along the height direction of the floating body portion 310 to improve the smoothness of liquid flow and reduce liquid flow resistance.

[0122] In some embodiments, the floating body 310 is provided with a plurality of second openings 340, which are arranged at intervals to further increase the total area of ​​the second openings 340 and facilitate liquid flow.

[0123] In one specific embodiment, two second openings 340 are provided on the floating main body 310.

[0124] In some embodiments, referring to FIG9, a fixing part 23 is provided inside the cavity of the gas-liquid separator, and the gas outlet pipe 22 passes through the fixing part 23. The fixing part 23 is provided with mounting holes for installing the gas outlet pipe 22. The fixing part 23 is also provided with multiple through holes for gas and liquid to flow through.

[0125] The floating part 300 is located below the fixed part 23, and the fixed part 23 is configured to limit the upward movement of the floating part 300. In other words, the floating part 300 stops moving upward when it comes into contact with the fixed part 23.

[0126] The floating part 300 is limited by the existing fixed part 23 inside the gas-liquid separator 2, so there is no need to set up an additional limiting structure.

[0127] In some embodiments, referring to FIG12, a flange 330 is provided on the top of the floating part 300, and the flange 330 extends toward the outer periphery of the floating part 300. The flange 330 is configured to abut against the fixing part 23 to limit the upward position of the floating part 300.

[0128] The flange 330 increases the contact area with the fixing part 23 and reduces the stress on the fixing part 23.

[0129] In some embodiments, two oil return holes 2201 are provided on the vent pipe 22, and the two oil return holes 2201 are arranged at intervals along the height direction of the vent pipe 22.

[0130] When the floating part 300 descends to the first position, both oil return holes 2201 are open.

[0131] When the floating part 300 floats to the second position, the folding part 320 is directly opposite the oil return hole 2201 located above, blocking the oil return hole 2201.

[0132] In some embodiments, the compressor body 1 is a dual-cylinder rotary type, and the gas-liquid separator 2 includes two outlet pipes 22, each of which is provided with a floating part 300. The two outlet pipes 22 are respectively arranged corresponding to two cylinders in the compression mechanism 14 to provide gaseous refrigerant to the corresponding cylinder cavity.

[0133] [Compressor housing]

[0134] The gaseous refrigerant, compressed and discharged by the compression mechanism 14, flows into the space between the motor 13 and the upper housing, and is then discharged through the exhaust pipe 12.

[0135] In some embodiments, improvements to the upper housing 410 can improve vibration and noise reduction, reduce oil discharge rate, increase oil supply, and enhance fatigue strength.

[0136] In some embodiments, the small space between the motor 13 and the upper housing 410 results in a low oil discharge rate. Furthermore, when the gaseous refrigerant flows upward through the motor 13 into the upper space, it impacts the upper housing 410, which can easily cause the airflow to resonate with the upper housing 410, increasing the compressor noise.

[0137] In some embodiments, referring to Figures 13 to 17, an upper housing 410 is disposed on top of a circumferential housing 430. The upper housing 410 includes a circumferential wall and an arcuate top wall, denoted as a circumferential wall 412 and an upper arcuate top wall 411, respectively. The upper arcuate top wall 411 is disposed on top of the circumferential wall 412, and the circumferential wall 412 is connected to the circumferential housing 430.

[0138] In some embodiments, the upper arc-shaped top wall 411 is formed by sequentially connecting a plurality of first arc-shaped top walls 41101 and a plurality of second arc-shaped top walls 41102, with the plurality of first arc-shaped top walls 41101 and the plurality of second arc-shaped top walls 41102 arranged alternately along the circumference of the upper arc-shaped top wall 411.

[0139] It should be noted that the radius of the circumference where the first arc-shaped top wall 41101 is located is greater than the radius of the circumference where the second arc-shaped top wall 41102 is located, and the platform part for mounting devices is provided on the first arc-shaped top wall 41101.

[0140] In some embodiments, the upper arc-shaped top wall 411 makes the upper housing 410 a hemispherical structure, which helps to increase the resonant frequency, avoid the pump body airflow frequency from resonating with the upper housing 410, and improve the vibration reduction and noise reduction effect; at the same time, the increased cavity volume is beneficial to the oil discharge rate design; in addition, it also helps to improve the fatigue strength of the upper housing 410.

[0141] It should be noted that the upper arc-shaped top wall 411 is formed by the staggered arrangement of the first arc-shaped top wall 41101 and the second arc-shaped top wall 41102, and the two have different radii. This can increase the cavity volume, and a height difference is formed between the first arc-shaped top wall 41101 and the second arc-shaped top wall 41102. When the device is installed on the first arc-shaped top wall 41101, the second arc-shaped top wall 41102, which is in a lower position, can avoid it.

[0142] The design platform department is responsible for installing components such as junction box 18, temperature sensor 117, welding electrodes, and hooks to facilitate component installation.

[0143] In some embodiments, referring to FIG17, the radius of the circumferential wall 412 is R4, the radius of the circumference where the second arc-shaped top wall 41102 is located is R5, and the height of the upper shell 410 is H6. Within this range, it is beneficial to reduce resonance phenomena.

[0144] In some embodiments, the upper housing 410 generally needs to be equipped with components such as junction box 18 and temperature sensor 117, so an installation platform needs to be set in the upper housing 410. The installation platform will reduce the space between the motor 13 and the upper housing 410.

[0145] In some embodiments, referring to Figures 13 and 14, a first platform portion 413 is provided on the first arc-shaped top wall 41101. The first platform portion 413 is configured to mount a junction box 18. A portion of the bottom surface of the junction box 18 contacts the first platform portion 413, while the other portion does not contact the adjacent second arc-shaped top wall 41102. The lower second arc-shaped top wall 41102 avoids the junction box 18, facilitating the installation of the junction box 18.

[0146] In some embodiments, referring to FIG17, a first mounting hole 417 is provided on the first platform portion 413, and the wiring terminal 1801 of the junction box 18 is disposed in the first mounting hole 417. The fitting gap between the wiring terminal 1801 and the first mounting hole 417 is in the range of [0.1mm, 0.8mm], which helps to improve the installation reliability of the wiring terminal 1801.

[0147] In some embodiments, a second platform portion 414 is provided on the first arc-shaped top wall 41101. The second platform portion 414 is configured to install the hoisting portion 20, which is configured to be used for hoisting the compressor body 1 when it is moving on the production line.

[0148] The mating area between the second platform section 414 and the hoisting section 20 is greater than 766mm. 2 This range helps to improve the structural strength of the hoisting section 20, thereby improving the hoisting reliability of the compressor body 1.

[0149] In some embodiments, referring to FIG13, a third platform portion 415 is provided on the first arcuate top wall 41101, and a connector 19 is provided on the third platform portion 415. The connector 19 is inclined. An inclined limiting cavity is formed between the connector 19 and the third platform portion 415, and the limiting cavity is configured to install a temperature sensor 117.

[0150] The temperature sensor 117 is installed and limited by the connector 19. The connector 19 is angled to facilitate the downward insertion of the temperature sensor 117 and prevent the temperature sensor 117 from falling out.

[0151] In some embodiments, a second mounting hole 418 is provided at the top of the upper arc-shaped top wall 411, through which the exhaust pipe 12 passes. A fourth platform portion 416 is provided on the upper arc-shaped top wall 411, surrounding the second mounting hole 418. The fourth platform portion 416 is configured to mate with a welding electrode used when installing the exhaust pipe 12, facilitating the welding operation of the exhaust pipe 12.

[0152] In some embodiments, referring to Figures 15 and 16A, the circumferential wall 412 includes a first circumferential wall section 41201 and a second circumferential wall section 41202. The first circumferential wall section 41201 is located below the second circumferential wall section 41202. The thickness of the first circumferential wall section 41201 is less than the thickness of the second circumferential wall section 41202. A step is formed between the first circumferential wall section 41201 and the second circumferential wall section 41202.

[0153] One of the upper circumferential wall sections 41201 is inserted into the top of the circumferential housing 430. The height of the upper circumferential wall section 41201 is E1, for example, E1 can be 12±0.2mm. This helps to ensure the reliability of the insertion between the upper housing 410 and the circumferential housing 430. The lower part of the upper circumferential wall section 41201 is an inclined wall, which facilitates insertion into the circumferential housing 430.

[0154] In some embodiments, the upper end of the eccentric crankshaft 110 passes through the motor 13, and the distance between the bottom end of the exhaust pipe 12 and the top end of the crankshaft ranges from [5, 20] mm. This position is a low-pressure area, and the oil baffle plate rotates with the eccentric crankshaft 110, causing oil to be thrown onto the housing wall. Extending the exhaust pipe 12 to this position range helps to prevent oil spillage.

[0155] [Oil sump adsorption section of the compressor body]

[0156] In some embodiments, during compressor operation, wear-related iron filings are generated by the friction pairs. If these iron filings are not effectively controlled, they can cause three-dimensional wear of the friction pairs, reducing compressor performance and potentially damaging the compressor. A common method is to place magnets in the oil sump at the bottom of the compressor to attract the iron filings. However, a larger magnet outer diameter leads to higher costs, while a smaller magnet outer diameter results in lower magnet adsorption and poorer iron filings adsorption.

[0157] In addition, the magnet is set on the bottom casing of the compressor. The space between the bottom casing and the compression mechanism 14 is usually small, resulting in a limited oil sump volume, which is not conducive to oil supply design. The lower casing is prone to resonance with the airflow, increasing the compressor noise.

[0158] This embodiment improves the magnets in the compressor bottom casing and oil sump to achieve the effects of increasing iron filings adsorption rate, reducing cost, reducing vibration and noise, and increasing oil supply.

[0159] In some embodiments, referring to Figures 15, 18 to 20, the housing includes a circumferential housing 430 and a lower housing 420. The lower housing 420 is disposed at the bottom of the circumferential housing 430. The lower housing 420 includes a circumferential wall and an arcuate bottom wall 621, referred to as the lower circumferential wall 422 and the lower arcuate bottom wall 421, respectively. The lower arcuate bottom wall 421 is disposed at the bottom of the lower circumferential wall 422, and the lower circumferential wall 422 is connected to the circumferential housing 430. A flat portion 423 is provided at the bottom of the lower arcuate bottom wall 421.

[0160] The lower arc-shaped bottom wall 421 makes the lower housing 420 a hemispherical structure, which increases the resonance frequency and avoids the resonance between the pump body airflow frequency and the lower housing 420; at the same time, the cavity volume is increased and the bottom oil pool volume is increased, which is beneficial to the oil supply design.

[0161] The lower housing features a 420 spherical design, which reduces the planar area. The smaller the area, the higher the hydraulic reciprocating fatigue strength and water pressure resistance.

[0162] An adsorption part 500 is provided on the flat part 423. The adsorption part 500 is located in the oil bath and is configured to adsorb iron filings. A through hole 520 is provided on the adsorption part 500, and the through hole 520 extends along the height direction of the adsorption part 500. The adsorption part 500 is, for example, a magnet.

[0163] By providing through holes 520 on the adsorption part 500, the outer diameter of the adsorption part 500 is ensured to be large enough, while also helping to reduce costs and improve the adsorption effect of iron filings.

[0164] In some embodiments, referring to FIG18, the outer diameter of the inner wall of the lower circumferential wall 422 is D4, and referring to FIG20, the outer diameter of the adsorption part 500 is D5, and D4 / D5 = [3, 6].

[0165] The inner diameter of the through hole 520 is D6, and D5 / D6 = [1.5, 3]. The thickness of the adsorption part 500 is t, and D5 / t = [6, 15].

[0166] The above settings meet the requirements for high-speed impurity adsorption and low cost.

[0167] In some embodiments, referring to FIG18, the height of the lower housing 420 is H7, the radius of the planar portion 423 is R6, and the radius of the circumference of the lower arc-shaped bottom wall 421 is R7. Within this range, the increase in resonant frequency is not significant.

[0168] In some embodiments, referring to FIG19, a connecting portion 510 is provided on the planar portion 423. The connecting portion 510 includes a base 511, which is fixedly disposed on the planar portion 423. A folding 512 is provided on the side edge of the base 511. The folding 512 is configured to press and limit the adsorption portion 500 toward the base 511, thereby realizing the fixed installation of the adsorption portion 500 on the connecting portion 510.

[0169] The adsorption unit 500 is limited by the flip-down 512, which facilitates the installation of the adsorption unit 500.

[0170] In some embodiments, an inclined extension 513 is provided on one side edge of the base 511. The inclined extension 513 extends obliquely upward in a direction away from the adsorption part 500, and plays a guiding role in the assembly and disassembly of the adsorption part 500.

[0171] In some embodiments, referring to Figures 15 and 16B, the lower circumferential wall 422 includes a lower circumferential wall section 42201 and a lower circumferential wall section 42202. The lower circumferential wall section 42201 is located above the lower circumferential wall section 42202. The thickness of the lower circumferential wall section 42201 is less than the thickness of the lower circumferential wall section 42202. A step is formed between the lower circumferential wall section 42201 and the lower circumferential wall section 42202.

[0172] The lower circumferential wall section 42201 is inserted into the bottom of the circumferential housing 430. The upper part of the lower circumferential wall section 42201 is an inclined wall, which facilitates the insertion and installation between the lower circumferential wall section 42201 and the circumferential housing 430.

[0173] The height of the lower circumferential wall section 42201 is E2, which is 12±0.2mm. Within this range, it helps to ensure the reliability of the insertion between the lower housing 420 and the circumferential housing 430.

[0174] [The second sub-silencer of the compressor body]

[0175] In related technologies, the second sub-muffler is a single-layer structure, with limited noise reduction effect and poor oil leakage prevention. This embodiment improves the second sub-muffler to enhance noise reduction and reduce oil leakage rate. In some embodiments, referring to Figures 21, 22, and 24, the second sub-muffler 141 has an inner and outer double-layer structure, including a third sub-muffler 610 (inner muffler) and a fourth sub-muffler 620 (outer muffler). An oil supply channel is provided inside the eccentric crankshaft 110. The second bearing 151 includes a vertical portion 1511 and a horizontal portion 1512 of integral structure, with the eccentric crankshaft 110 passing through the vertical portion 1511. The lower shaft end passes through the vertical portion 1511.

[0176] The third sub-muffler 610 is disposed at the bottom of the second bearing 151, and a first silencing cavity 631 is formed between the third sub-muffler 610 and the second bearing 151. The fourth sub-muffler 620 is disposed at the bottom of the third sub-muffler 610, and a second silencing cavity 632 is formed between the fourth sub-muffler 620 and the third sub-muffler 610.

[0177] The gas discharged from the second bearing 151 first enters the first silencing chamber 631 for the first silencing. The gas in the first silencing chamber 631 then flows into the second silencing chamber 632 for the second silencing. It then returns to the first silencing chamber 631 and is discharged to the top side of the compression mechanism 14 through the airflow channel 170 inside the compression mechanism 14.

[0178] The double-layer design of the second sub-silencer 141 extends the gas flow path, which helps to improve the noise reduction effect.

[0179] In some embodiments, Figures 22 and 23 are structural diagrams of two different forms of the third sub-silencer 610. The third sub-silencer 610 has a first through hole 611, through which a vertical portion 1511 passes. A vent is formed between the inner wall of the first through hole 611 and the peripheral wall of the vertical portion 1511. The vent connects the first silencing chamber 631 and the second silencing chamber 632, allowing gas to flow through.

[0180] Figure 24 is a structural diagram of the fourth sub-muffler 620. The fourth sub-muffler 620 is provided with a second through hole 623, and the bottom oil suction port of the oil supply channel is directly opposite the second through hole 623 to ensure normal oil supply to the oil suction port.

[0181] The bottom of the fourth sub-silencer 620 contacts and seals with the bottom end of the vertical part 1511 to prevent gas leakage from this point.

[0182] In some embodiments, referring to FIG22, the inner diameter of the first through hole 611 is larger than the outer diameter of the vertical portion 1511. The vertical portion 1511 passes through the first through hole 611, and a gap for gas flow is formed between the outer peripheral wall of the vertical portion 1511 and the inner peripheral wall of the first through hole 611. This gap should be understood as the vent described above.

[0183] The difference between the inner diameter of the first through hole 611 and the outer diameter of the vertical part 1511 is greater than 3mm, which helps to ensure smooth gas flow.

[0184] In some embodiments, referring to FIG23, the first through hole 611 includes a first sub-through hole 612 (main through hole) and a second sub-through hole 613 (secondary through hole). The first sub-through hole 612 communicates with the second sub-through hole 613, and the second sub-through hole 613 extends to the outer periphery of the first sub-through hole 612. The vertical portion 1511 passes through the first sub-through hole 612, and the second sub-through hole 613 communicates the first silencing cavity 631 and the second silencing cavity 632. That is, the second sub-through hole 613 allows gas to flow, which can be understood as the vent described above.

[0185] For example, the second through hole 613 is a semi-circular hole design, and the opening position is determined according to the sound loss design.

[0186] It should be noted that the difference between the sound power level incident on the inlet of the silencer and the sound power level transmitted out of the outlet of the silencer is called the transmission loss, or simply sound loss.

[0187] In some embodiments, referring to FIG23, two second sub-through holes 613 are provided, and the two second sub-through holes 613 are arranged symmetrically with respect to the first sub-through hole 612.

[0188] In some embodiments, a protrusion is provided on the inner side of the bottom wall 621 of the fourth sub-muffler 620. The protrusion extends circumferentially along the second through hole 623 and abuts against the bottom end face of the vertical part 1511. The interference fit design achieves a seal with the second bearing 151.

[0189] In some embodiments, the area of ​​the vent is S1, the area of ​​the exhaust port on the transverse portion 1512 is S2, and S1 / S2 > 0.9.

[0190] The larger the S1 / S2 ratio, the better. A larger S1 results in lower pressure loss and correspondingly lower sound loss. When S1 / S2 > 0.9, the pressure loss and sound loss are relatively stable. It should be noted that pressure loss, or pressure drop for short, refers to the phenomenon of pressure reduction during fluid or gas flow due to friction, bending, expansion, contraction, etc.

[0191] In some embodiments, referring to Figures 21 to 23, the bottom wall of the third sub-muffler 610 is an arc-shaped wall 614, the circumferential edge of the arc-shaped wall 614 is connected to a circumferential wall, referred to as the first circumferential wall 615, the first circumferential wall 615 extends upward, the top of the first circumferential wall 615 is connected to a flange 616, the flange 616 extends to the outer periphery of the first circumferential wall 615, and the flange 616 is connected to the transverse portion 1512.

[0192] The radius of the circumference of the outer contour of the flange 616 is R10, and the radius of the circumference of the arc-shaped wall 614 is R11. R10 and R11 satisfy the relationship: R10 / R11 > 0.3. The third sub-silencer 610 has a hemispherical design, which helps to increase the resonant frequency and reduce noise.

[0193] In some embodiments, referring to FIG24, the fourth sub-muffler 620 includes a bottom wall 621 and a second circumferential wall 622, the inner sidewall of the second circumferential wall 622 abutting against the outer circumferential wall of the transverse portion 1512.

[0194] The third sub-muffler 610 has an internal mounting hole 617, and the fourth sub-muffler 620 has an external mounting hole 624. A connector, such as a bolt, passes through the external mounting hole 624 and the internal mounting hole 617 to connect with the transverse part 1512. That is, the third sub-muffler 610 and the fourth sub-muffler 620 are fixedly installed through the same connector, which facilitates installation and improves installation efficiency.

[0195] [The mating structure between the second bearing, the second piston, and the second cylinder in the compression mechanism]

[0196] In related technologies, there is friction between the bottom surface of the second piston 131 and the top surface of the second bearing 151, which affects the compressor efficiency.

[0197] In some embodiments, the fit structure between the second bearing 151, the second piston 131, and the second cylinder 121 is improved to balance low wear and high performance of the compressor.

[0198] In some embodiments, referring to FIG25, a first annular groove 1513 is provided at the top of the transverse portion 1512. The first annular groove 1513 surrounds the shaft hole of the second bearing 151. An inner wall 1514 of the first annular groove is formed between the first annular groove 1513 and the shaft hole of the second bearing 151. The top of the inner wall 1514 of the first annular groove is lower than the top of the transverse portion 1512.

[0199] The second cylinder 121 is located at the top of the transverse section 1512. The second piston 131 is located in the compression chamber of the second cylinder 121 and is sleeved on the second eccentric shaft section 114. When the second piston 131 moves eccentrically with the eccentric crankshaft 110, the bottom end face of the second piston 131 rubs against the top end face of the transverse section 1512.

[0200] By setting the top of the inner wall 1514 of the first annular groove to be lower than the top of the transverse portion 1512, the friction between the second piston 131 and the transverse portion 1512 is reduced, thereby helping to reduce compressor wear and improve performance.

[0201] In some embodiments, referring to FIG25, the outer diameter of the second shaft segment 115 is D14, the outer diameter of the vertical portion 1511 is D15, and the height of the vertical portion 1511 is H10. Referring to FIG21, the height of the second bearing 151 is H11. D14, D15, H10, and H11 satisfy the following relationship: This helps reduce frictional losses in the compressor.

[0202] In some embodiments, referring to FIG25, the distance between the bottom end of the first annular groove 1513 and the top surface of the second bearing 151 is H12, and the distance between the bottom end of the first annular groove 1513 and the top of the inner wall 1514 of the first annular groove is H13. H12 and H13 satisfy the relationship: 0.2mm≤H12-H13≤2mm, which helps to prevent radial deformation of the annular groove.

[0203] In some embodiments, referring to FIG25, the outer peripheral wall diameter of the first annular groove 1513 is D16, the inner peripheral wall diameter of the first annular groove 1513 is D17, the outer diameter of the second shaft segment 115 is D14, and (D16-D17) / D14=0.08-0.22, which helps to reduce the frictional loss of the second bearing 151.

[0204] In some embodiments, referring to FIG25, the outer peripheral wall diameter of the first annular groove 1513 is D16, the inner peripheral wall diameter of the first annular groove 1513 is D17, and the distance between the bottom end of the first annular groove 1513 and the top of the inner wall 1514 of the first annular groove is H13. D16, D17 and H13 satisfy the relationship: 0.2≤(D16-D17) / H13≤0.5. In this way, the second bearing 151 experiences less radial force and less deformation, which helps to reduce wear and improve the reliability of the second bearing 151.

[0205] In some embodiments, a second annular groove is provided at the top of the transverse portion 1512, the second annular groove surrounds the outer periphery of the first annular groove 1513, and a lubrication portion is provided inside the second annular groove.

[0206] During compressor operation, the lower thrust surface of the eccentric crankshaft 110 contacts and moves relative to the surface of the second bearing 151, forming a friction pair. At the initial startup stage of the compressor, the refrigerant oil has not yet circulated at this friction pair. By creating a second annular groove and providing a lubrication point within it, wear between the thrust surface of the eccentric crankshaft 110 and the second bearing 151 can be reduced, improving reliability.

[0207] In some embodiments, the lubrication part is a steel ring, the upper surface of which is coated with a Teflon coating to provide self-lubrication.

[0208] In some embodiments, referring to FIG25, the thickness of the partition plate 160 is t2, and the height of the second cylinder 121 is H14. t2 and H14 satisfy the relationship: 0.22≤t2 / H14≤0.35. This is beneficial to improving the energy conversion efficiency (COP) of the compressor.

[0209] [Exhaust valve plate]

[0210] In related technologies, the opening of the exhaust valve is influenced by the coupling of back pressure, airflow thrust, and elasticity, while closing relies solely on the valve's own elasticity. The opening and closing of the valve are significantly affected by operating conditions, making accurate opening and closing impossible. This often results in problems such as failure to open properly at low frequencies and delayed closing at high frequencies, thus impacting compressor performance. In some embodiments, the compressor's exhaust mechanism is improved to ensure the exhaust valve opens normally without vibration at low frequencies and closes promptly at high frequencies, thereby improving compressor performance.

[0211] In some embodiments, a vent hole is provided on the bearing. A vent valve 720 is provided on the bearing and configured to open or close the vent hole. A lift limiter 710 is provided on the bearing and configured to limit the displacement of the vent valve 720.

[0212] Referring to Figures 26 to 28, an electromagnetic suction part 730 is provided on the lift limiter 710. The electromagnetic suction part 730 is configured to be energized when the compression mechanism 14 exhausts to attract the exhaust valve plate 720.

[0213] A reset element 740, such as a spring, is provided between the exhaust valve plate 720 and the lift limiter 710. The reset element 740 is configured to apply a force to the exhaust valve plate 720 to move the exhaust valve plate 720 toward the exhaust port.

[0214] When the compressor needs to start discharging, the electromagnetic suction unit 730 is energized. The electromagnetic suction unit 730 attracts the discharge valve plate 720, enabling the discharge valve plate 720 to open quickly. Furthermore, the attraction force during opening prevents vibration, thus avoiding pressure loss caused by the vibration of the discharge valve plate 720. At this time, the reset member 740 is compressed.

[0215] Before the exhaust is finished, the electromagnetic suction unit 730 is de-energized, and the exhaust valve plate 720 and the reset member 740 are used to realize the rapid closing of the exhaust valve plate 720, thus avoiding the problem of delayed closing of the exhaust valve plate 720.

[0216] By reducing exhaust resistance losses and reducing high-pressure gas backflow, the compressor's capacity can be significantly improved, thereby enhancing energy efficiency.

[0217] In some embodiments, referring to Figures 26 and 28, the exhaust valve plate 720 includes a valve plate head 721, a valve plate tail 722, and a connecting section 723, which connects the valve plate head 721 and the valve plate tail 722. The valve plate tail 722 is connected to a bearing, and the valve plate head 721 is configured to open or close the exhaust port. An electromagnetic suction part 730 faces the valve plate head 721, enhancing the attraction of the electromagnetic suction part 730 on the valve plate head 721.

[0218] In some embodiments, the reset member 740 is disposed between the valve head 721 and the lift limiter 710, so that the reset member 740 can apply a more reliable reset force to the valve head 721.

[0219] In some embodiments, referring to FIG27, the effective length of the exhaust valve plate 720 is L1, the lift height of the exhaust valve plate 720 is H9, the radius of curvature of the exhaust valve plate 720 is R12, and the thickness of the exhaust valve plate 720 is t1. L1, R12, t1 and H9 satisfy the relationship: 1.5 < (L1 / R12) × t1 + H9 < 3.0.

[0220] The effective length of the exhaust valve plate 720 starts at the point where the valve plate is tangent to the lift limiter 710 and ends at the center of the valve plate head 721.

[0221] This disclosure determines the airflow thrust of the exhaust valve plate 720 under high-frequency operation through theoretical calculations, and uses this as the design boundary in its computer-aided engineering (CAD) process. In the finite element simulation of CAE (Computer Engineering), the height H, effective length L, radius of curvature R, and thickness T of the exhaust valve plate 720 were designed through multi-objective design. After multiple iterations, combined with the SN curve of the exhaust valve plate 720, it was determined that when 1.5 < (L1 / R12)×t1+H9 < 3.0, the stress at the head of the exhaust valve plate 720 is within the permissible range. Theoretically, the exhaust valve plate 720 can be used indefinitely. Although the stress of the exhaust valve plate 720 also meets the requirements when the value of the relationship (L1 / R12)×t1+H9 is below 1.5, its low value results in a low effective flow area, which will seriously affect the compressor performance. Therefore, in summary, when the relationship satisfies 1.5 < (L1 / R12)×t1+H9 < 3.0, it is beneficial to ensure the service life of the exhaust valve plate 720 and to achieve accurate opening and closing of the exhaust valve plate 720.

[0222] In some embodiments, referring to FIG28, the diameter of the valve head 721 is D11 and the diameter of the exhaust port is D12. D11 and D12 satisfy the relationship: 0.7 < D11 / D12 < 0.8, which is beneficial to ensuring the reliability of the exhaust valve 720.

[0223] In some embodiments, the cylinder inner diameter is D13, and D12 and D13 satisfy the relationship: 0.2 < D12 / D13 < 0.3.

[0224] It should be noted that the size of the cylinder, cylinder bore, and exhaust port significantly affect the airflow velocity. Excessive airflow velocity can also cause a large impact on the exhaust valve plate 720. When the relationship satisfies 0.2 < D12 / D13 < 0.3, the impact force on the exhaust valve plate 720 can be reduced as much as possible while ensuring low pressure loss.

[0225] In some embodiments, referring to FIG26, the lift limiter 710 has a copper wire on the side away from the exhaust valve plate 720. The copper wire is connected to the controller. When the copper wire is energized, it forms an electromagnetic suction part 730. The structure is simple and easy to implement.

[0226] In some embodiments, the electromagnetic suction part 730 is disposed on the lift limiter 710, and the electromagnetic suction part 730 is configured to be energized to attract the exhaust valve plate 720 when the compression mechanism 14 is venting, and the electromagnetic part is configured to be de-energized when the compression mechanism 14 is not venting.

[0227] The reset member 740 is disposed between the exhaust valve plate 720 and the lift limiter 710. The reset member 740 is configured to retract when the electromagnetic suction part 730 attracts the exhaust valve plate 720. The reset member 740 is configured to apply a force to the exhaust valve plate 720 to move the exhaust valve plate 720 toward the exhaust port.

[0228] [Muffler on the exhaust pipe]

[0229] Noise inside an air conditioner typically originates from wind noise and refrigerant pulsation. Wind noise is generally broadband white noise and often does not cause discomfort to customers. It should be noted that white noise refers to noise whose power spectral density is constant across the entire frequency domain. Random noise with the same energy density at all frequencies is called white noise.

[0230] However, refrigerant pulsation noise is mostly pure tone, and it varies with the compressor's operating frequency and the indoor-outdoor temperature difference. Since refrigerant pulsation noise mainly originates from the compressor, silencers are usually placed at the compressor's exhaust port to reduce abnormal noise. However, traditional expansion silencers can provide some noise suppression for a small band of high or low frequencies, but when the compressor's operating frequency or refrigerant pressure changes significantly, they fail to provide adequate noise reduction, leading to the appearance of pure tone components indoors and causing customer complaints.

[0231] In some embodiments, the silencing structure at the compressor exhaust port is improved to effectively reduce refrigerant pulsation noise and avoid pure sound components on the indoor side of the air conditioner.

[0232] For example, referring to Figures 29 and 30, a sensor 17 is provided on the exhaust pipe 12, and the sensor 17 is configured to detect the vibration frequency of the exhaust pipe 12.

[0233] A muffler 800 is provided on the exhaust pipe 12. The muffler 800 is located downstream of the sensor 17 along the gas flow direction inside the exhaust pipe 12.

[0234] The muffler 800 includes a connecting pipe section. The inner diameter of the connecting pipe section is larger than the inner diameter of the exhaust pipe 12.

[0235] The muffler 800 also includes a flexible pipe section 830. The inner diameter of the flexible pipe section 830 is larger than the inner diameter of the exhaust pipe 12.

[0236] The muffler 800 also includes a drive unit 860, which is configured to drive the flexible pipe section 830 to extend and retract along the length of the exhaust pipe 12 according to the vibration frequency of the exhaust pipe 12.

[0237] For example, the muffler 800 is an automatically variable capacity muffler used to suppress the transmission of refrigerant pulsation noise.

[0238] It should be noted that, based on the principle of muffler noise reduction, the noise reduction frequency is only related to the length of muffler 800. Therefore, after obtaining the vibration frequency of exhaust pipe 12 through sensor 17, the flexible pipe section 830 is driven to extend or shorten through drive unit 860 to realize the length change of muffler 800, so as to improve the noise reduction effect.

[0239] In some embodiments, referring to FIG30, the connecting pipe segment includes a first connecting pipe segment 810 and a second connecting pipe segment 820, and a flexible pipe segment 830 is connected between the first connecting pipe segment 810 and the second connecting pipe segment 820.

[0240] The first connecting pipe section 810 and the second connecting pipe section 820 are metal pipes, such as copper pipes. The flexible pipe section 830 is a corrugated pipe, which is convenient for expansion and contraction.

[0241] In some embodiments, the drive unit 860 is configured to drive the first connecting pipe segment 810 and the second connecting pipe segment 820 to move closer to each other so that the flexible pipe segment 830 contracts.

[0242] The drive unit 860 is also configured to drive the first connecting pipe section 810 and the second connecting pipe section 820 away from each other so that the flexible pipe section 830 extends.

[0243] It should be noted that the flexible pipe section 830 is located between the first connecting pipe section 810 and the second connecting pipe section 820. The movement of the first connecting pipe section 810 and the second connecting pipe section 820 is driven by the driving unit 860 to realize the contraction or extension of the flexible pipe section 830.

[0244] The first connecting pipe section 810 and the second connecting pipe section 820 are metal pipes, which facilitates the installation of the drive unit 860.

[0245] In some embodiments, a first connecting portion 840 is provided on one of the first connecting pipe segment 810 and the second connecting pipe segment 820, and a second connecting portion 850 is provided on the other.

[0246] A drive motor 861 is provided on one of the first connecting part 840 and the second connecting part 850, and a threaded hole is provided on the other. A lead screw 862 is provided at the power output end of the drive motor 861, and the lead screw 862 is connected to the threaded hole.

[0247] The drive motor 861 drives the lead screw 862 to rotate. Through the threaded connection between the lead screw 862 and the threaded hole, the first connecting part 840 and the second connecting part 850 are brought closer or further apart, thereby bringing the first connecting pipe section 810 and the second connecting pipe section 820 closer or further apart, thus realizing the contraction or extension of the flexible pipe section 830.

[0248] In some embodiments, the sensor 17 detects the vibration frequency range of the exhaust pipe 12 from 1000 to 3000 Hz.

[0249] In some embodiments, the exhaust pipe 12 is disposed on the upper housing 410. Referring to FIG7, the inner diameter of the upper housing 410 is D8. Referring to FIG2A, the inner diameter of the exhaust pipe 12 is D9.

[0250] Referring to Figure 2B, the distance between the intake end of the exhaust pipe 12 and the top of the crankshaft is H8, and D8, D9, and H8 satisfy the following relationship: Within this range, the compressor's oil discharge rate decreases.

[0251] In some embodiments, referring to FIG2A, the inner diameter of the housing is D10, the inner diameter of the exhaust pipe 12 is D9, and D10 / D9 = [8, 12].

[0252] It should be noted that the inner diameter of the compressor main casing is greatly affected by the displacement. Generally, the larger the displacement, the larger the inner diameter. Moreover, when the displacement is larger, the inner diameter of the exhaust pipe 12 also needs to be larger in order to reduce the oil discharge rate and refrigerant gas pressure loss. When D10 / D9=[8,12], the displacement can be increased while reducing the oil discharge rate.

[0253] In some embodiments, sensor 17 is disposed on exhaust pipe 12 and is configured to detect the vibration frequency of exhaust pipe 12.

[0254] The muffler 800 includes a pipe section that is connected to the exhaust pipe 12, and the inner diameter of the pipe section is larger than the inner diameter of the exhaust pipe 12. The muffler 800 is an expansion type muffler.

[0255] The muffler 800 includes a drive unit 860, configured to drive a pipe section to move according to the vibration frequency of the exhaust pipe 12 to change the volume of the pipe section. The muffler 800 is an automatically variable displacement muffler to improve the effect of suppressing the transmission of refrigerant pulsation noise.

[0256] [Compressor feet]

[0257] To reduce compressor vibration, vibration-damping pads can be used to reduce compressor vibration from the perspectives of stiffness and damping matching. However, as the size and weight of the compressor increase, the stiffness of the pads cannot be too low. If the stiffness of the pads is too low, it will easily cause excessive shaking of the compressor during transportation, which will impact the pipeline and cause pipeline breakage and other problems.

[0258] In some embodiments, the compressor's base is optimized to improve vibration damping.

[0259] In some embodiments, referring to FIG2A, the circumferential housing 430 constitutes the circumferential wall of the compressor body 1, the height of the circumferential housing 430 is H10, and the inner diameter of the circumferential housing 430 is D10.

[0260] The mounting part 16 is provided on the outside of the circumferential housing 430, and the mounting part 16 is provided with a mounting hole with an inner diameter of D18.

[0261] The compressor also includes a foot 15, with a connector (such as a bolt) passing through a mounting hole to mount the foot 15 to the mounting portion 16. The foot 15 is configured to carry the compressor, and the height of the foot 15 is H16.

[0262] It should be noted that, from the perspective of controlling the position of the compressor's center of gravity, 4.5 < H10 / H16 < 6.5, and 5.5 < D10 / D18 < 8.5. Controlling the position of the compressor's center of gravity helps reduce compressor casing vibration and meets the vibration reduction requirements of the rotary compressor casing.

[0263] In some embodiments, if the number of feet 15 is too large, installation becomes inconvenient. If the number of feet 15 is too small, the feet 15 will be subjected to greater force, making them prone to deformation from drops and causing significant vibration. For example, if the compressor weighs G (kg) and the number of feet 15 is N, G and N satisfy the formula: 12.5 > G / N > 5, that is, 12.5 kg / foot 15 > designed compressor weight / number of feet 15 > 5 kg / foot 15. Within this range, the compressor has low vibration and noise and good drop resistance.

[0264] In some embodiments, three feet 15 are provided on the side of the circumferential housing 430, and the angle between the foot 15 near the gas-liquid separator 2 and the gas-liquid separator 2 is greater than or equal to 30° and less than or equal to 60°. Within this range, the compressor vibration noise is low and the drop resistance is good.

[0265] In some embodiments, four feet 15 are provided on the side of the circumferential housing 430, and the angle between the foot 15 near the gas-liquid separator 2 and the gas-liquid separator 2 is greater than or equal to 20° and less than or equal to 45°. Within this range, the compressor vibration noise is low and the drop resistance is good.

[0266] In some embodiments, the height of the base 15 / the height of the compressor's center of gravity = [0.07, 0.15], so that the compressor vibration noise is low within this range.

[0267] It should be noted that any one of the technical solutions disclosed in this disclosure can solve one or more of the above-mentioned technical problems and achieve a certain inventive purpose to a certain extent; multiple technical disclosures can also be combined into an overall solution to solve one or more of the above-mentioned technical problems and achieve a certain inventive purpose; some technical disclosures can also be selected and combined into an overall solution, while adopting related technologies and deteriorating solutions, but the deterioration trend can be compensated by the means of this technical disclosure, and the overall solution can solve one or more of the above-mentioned technical problems and achieve a certain inventive purpose to a certain extent; each technical disclosure combined into a complete technical solution constitutes an organic and indivisible overall solution, which solves the technical problems and achieves a certain inventive purpose as a whole.

[0268] Any technical disclosure in this disclosure, as well as the recombination of multiple technical disclosures, can form a complete technical solution and solve one or more of the aforementioned technical problems, thereby achieving the inventive objective. All of these fall under the content of this disclosure and are directly and unambiguously determined based on the content of this disclosure.

[0269] Those skilled in the art will understand that the scope of this invention is not limited to the specific embodiments described above, and that modifications and substitutions can be made to certain elements of the embodiments without departing from the spirit of this application. The scope of this application is limited by the appended claims.

Claims

1. A compressor, comprising: The compressor body includes a first housing, and a compression mechanism is disposed within the first housing, the compression mechanism being configured to compress refrigerant; A gas-liquid separator, disposed outside the first housing, is configured to supply gaseous refrigerant to the compression chamber of the compression mechanism; and Two supports, symmetrically arranged, are configured to connect the first housing and the second housing of the gas-liquid separator. Each of the two supports includes a first support, a second support, a third support, and a fourth support connected in sequence. The first support and the third support are located on the same side of the second support, and the second support and the fourth support are located on opposite sides of the third support. The second support is adapted to and fixedly connected to the outer contour of the second housing. The first support and the third support extend between the first housing and the second housing, respectively, and the first support and the fourth support are fixedly connected to the first housing. The length of the first support is greater than the length of the third support. The two fourth supports of the two supports are close to each other.

2. The compressor according to claim 1, wherein, The bracket has an opening extending along its length, the width of which is H and the length of which is L, where H / L = (0, 0.82).

3. The compressor according to claim 1 or 2, wherein, The width of the second part of the bracket is W3, the outer contour radius of the second shell is R2, and the range of W3 / R2 is [1.4, 2.2].

4. The compressor according to any one of claims 1 to 3, wherein, The radius of the arc-shaped structure where the two parts of the bracket are located is R3, and the outer contour radius of the second shell is R2, R3-R2=[0.5mm, 2mm].

5. The compressor according to any one of claims 1 to 4, wherein, The arc α of the second part of the bracket is greater than 39°.

6. The compressor according to any one of claims 1 to 5, wherein, The distance from the junction of the first and second parts of the bracket to the plane of symmetry of the two brackets is W1, the distance from the third part of the bracket to the plane of symmetry of the two brackets is W2, the outer contour radius of the second shell is R2, the outer contour radius of the first shell is R1, and (W1 / R2)×(W2 / R1)>0.

3.

7. The compressor according to any one of claims 1 to 6, wherein, The bracket part includes a first section of the first bracket part and a second section of the first bracket part. The first section of the first bracket part extends outward at an angle from the first end of the second section of the first bracket part. The first section of the first bracket part is adapted to and fixedly connected to the first housing. The second end of the second section of the first bracket part intersects and connects with the second section of the second bracket part. The angle β between the line connecting the second end of the first part of the bracket and the end of the first part of the bracket and the second part of the bracket is 2°.

8. The compressor according to any one of claims 1 to 7, wherein, The height of the compressor body is H1, and the height of the bracket from the bottom of the compressor body is H2, where H2 / H1 = [0.49, 0.71].

9. The compressor according to any one of claims 1 to 7, wherein, The distance between the connection point of one part of the two supports and the first housing is D2, the outer diameter of the first housing is D1, and D2 / D1 = [0.06, 0.9].

10. An air conditioner, comprising a compressor, an evaporator, a condenser, and a throttling device, wherein, The compressor is the compressor described in any one of claims 1 to 9.

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