A static scroll plate cover, compressor and air conditioner

Abstract

The present application relates to compressor technical field, more specifically, it relates to a kind of static scroll disc cover, compressor and air conditioner, wherein, static scroll disc cover includes cover body, and the cover body is equipped with static scroll tooth, suction passage and exhaust passage;The static scroll disc cover is covered with the one end of the body of compressor by the cover body, make suction passage and suction flow passage on the body communicate, and make static scroll tooth and the dynamic scroll tooth of the dynamic scroll disc of body cooperate to compress low-pressure refrigerant inhaled in suction passage;The exhaust passage is used to lead out high-pressure refrigerant after compression from cover body;The cover body is integrally formed structure, and the suction passage and exhaust passage are separately arranged.The technical scheme according to the present application, since cover body is integrally formed structure, and by separating exhaust passage and suction passage, it can avoid that refrigerant in exhaust passage leaks to suction passage, so that it can prevent that refrigerant leaks between high-pressure exhaust side and low-pressure suction side.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a static scroll cover, a compressor, and an air conditioner. Background Technology

[0002] Scroll compressors have been widely used in many fields due to their advantages such as compact structure, high efficiency and energy saving, stable operation, and low vibration and noise.

[0003] The scroll compressor includes a housing, a stationary scroll, a moving scroll, and end covers. Both the stationary and moving scrolls are located inside the housing. A front cover is located on the side of the housing closest to the stationary scroll, and a rear cover is located on the side of the housing closest to the moving scroll. The front and rear covers work together to enclose the moving and stationary scrolls inside the housing.

[0004] The scroll compressor utilizes the meshing motion of a moving scroll and a stationary scroll to compress the refrigerant and achieve refrigeration. The compressed refrigerant is discharged from the front cover through the exhaust port of the stationary scroll. To prevent refrigerant leakage inside the compressor and reduce the cooling capacity, it is usually necessary to separate the high-pressure exhaust side from the low-pressure suction side. This is typically achieved by machining a sealing groove on the base plate of the stationary scroll and assembling a seal within the sealing groove.

[0005] In practice, due to manufacturing and assembly errors of both the front cover and the stationary scroll plate, there is a relative displacement between them. Under the influence of external variable forces over a long period of time, the seal is prone to deformation or even failure. In addition, when the machining accuracy of the sealing groove is poor, the seal is prone to over-compression or under-compression, which will also cause the seal to fail to completely seal the gap between the front cover and the stationary scroll plate. This will cause the refrigerant in the high-pressure exhaust side to leak into the low-pressure suction side through the gap, resulting in a reduction in the cooling capacity of the air conditioner. Summary of the Invention

[0006] In view of this, the present invention provides a static scroll cover, a compressor and an air conditioner, the main technical problem to be solved is: how to prevent refrigerant leakage between the high-pressure exhaust side and the low-pressure intake side.

[0007] To achieve the above objectives, the present invention mainly provides the following technical solutions:

[0008] In a first aspect, embodiments of the present invention provide a static vortex disk cover, which includes a cover body, wherein the cover body is provided with static vortex teeth, an air intake channel and an air exhaust channel;

[0009] The stationary scroll cover covers one end of the compressor body, connecting the intake channel to the intake channel on the body, and allowing the stationary scroll teeth to engage with the moving scroll teeth of the moving scroll on the body to compress the low-pressure refrigerant drawn in through the intake channel; the exhaust channel is used to lead the compressed high-pressure refrigerant out of the cover.

[0010] The cover is a one-piece molded structure, and the air intake channel and the air exhaust channel are set separately.

[0011] In some embodiments, the static vortex cover further includes a noise reduction structure for reducing the noise of the refrigerant within the exhaust passage.

[0012] In some embodiments, the noise reduction structure includes an annular cavity disposed on the cover, the exhaust channel includes an exhaust hole disposed on the cover, the annular cavity is disposed around the exhaust hole, and there is a wall thickness between the annular cavity and the hole wall of the exhaust hole;

[0013] The static vortex disk cover also includes a first air intake channel, which is used to introduce low-pressure refrigerant into the annular cavity.

[0014] In some embodiments, the length L of the annular cavity along the centerline of the exhaust port satisfies:

[0015]

[0016] Where D is the inner diameter of the annular cavity, and the unit of D is m; T1 is the temperature inside the annular cavity, and T2 is the temperature inside the exhaust port, and the units of T1 and T2 are both K.

[0017] In some embodiments, the cover has an inner cavity with a refrigerant intake side communicating with an intake channel; the stationary vortex gear is located in the inner cavity to compress the refrigerant within the inner cavity;

[0018] The first air intake channel is connected to the intake channel through the refrigerant intake side of the inner cavity, so as to draw the low-pressure refrigerant in the intake channel to the annular cavity.

[0019] In some embodiments, when the exhaust passage includes an exhaust hole provided on the cover, the exhaust hole is a stepped hole, and the diameter of the stepped hole gradually increases along the direction of refrigerant discharge.

[0020] In some embodiments, the exhaust passage is provided with an oil-gas separation structure, which is used to separate the refrigerant flowing through the exhaust passage into oil and gas, and to return the separated refrigeration oil, so that the stationary vortex tooth cooperates with the moving vortex tooth of the moving vortex disk of the machine body to compress the returned refrigeration oil.

[0021] The oil-gas separation structure includes an oil guide funnel and an impeller. The oil guide funnel is installed in the exhaust channel so that the refrigerant in the exhaust channel flows in through the small end of the oil guide funnel and flows out through the large end of the oil guide funnel. The impeller is rotatably installed in the oil guide funnel and is rotated by the refrigerant flowing through the oil guide funnel, and performs oil-gas separation on the refrigerant.

[0022] In some embodiments, the exhaust passage is further provided with an anti-return structure, which is used to prevent refrigerant from flowing back into the exhaust passage.

[0023] The anti-return structure includes an end cap, and the exhaust channel has an exhaust port section and a step disposed at the opening of the exhaust port section. The end cap is movable and is used to be relatively close to or away from the step. When the end cap is close to the step, it abuts against the step to cover the opening of the exhaust port section. When the end cap is away from the step, it forms a gap with the step, allowing the refrigerant in the exhaust port section to flow out through the gap.

[0024] The static vortex cover also includes a stop structure for stopping the end cover when it moves to an extreme position away from the step.

[0025] In some embodiments, a protruding post is provided on the side of the end cap near the vent section, and a guide portion is provided on the outer side wall of the protruding post. There are two or more guide portions, which are arranged at intervals along the circumference of the protruding post. A guide groove is provided on the step, and the number of guide grooves is equal to the number of guide portions.

[0026] The protruding post has an oil guide groove between each pair of adjacent guide parts; the protruding post is used to insert into the exhaust hole section, so that each guide part and each guide groove are inserted and matched one by one, and the oil guide groove is connected to the exhaust hole section; when the end cover opens the exhaust hole section, the refrigerant in the exhaust hole section flows out from the gap through the oil guide groove.

[0027] In some embodiments, the air intake channel includes an air intake channel hole disposed on the cover body, so as to communicate with the air intake channel through the air intake channel hole and introduce low-pressure refrigerant in the air intake channel for compression;

[0028] The air intake of the air intake channel hole is located on the end face of the cover. When the cover closes one end of the compressor body, the air intake of the air intake channel hole is opposite to the outlet of the air intake channel, so that the air intake channel hole and the air intake channel are connected.

[0029] Secondly, embodiments of the present invention also provide a compressor that may include any of the aforementioned static scroll cover.

[0030] In some embodiments, the compressor includes a second bleed passage for drawing exhaust pressure from the exhaust passage to the back pressure chamber of the compressor.

[0031] The compressor further includes a throttling device for throttling the refrigerant flowing through the second air intake passage. The throttling device includes a throttling block with a throttling groove extending through both ends on its outer wall. There are two or more throttling blocks, stacked sequentially in a stepped configuration to form a stepped column structure. This stepped column structure is inserted into the second air intake passage and engages with its inner wall, allowing the refrigerant in the second air intake passage to flow sequentially from the throttling groove on one throttling block to the throttling groove on the next throttling block along the stacking direction of the throttling blocks.

[0032] In some implementations, two adjacent throttling blocks are detachably connected;

[0033] And / or, along the refrigerant outflow direction in the second air intake channel, the cross-sectional area of ​​the throttling groove on each throttling block gradually decreases;

[0034] And / or, along the refrigerant outflow direction in the second air intake channel, the depth of the throttling grooves on each throttling block gradually decreases.

[0035] In some embodiments, the length Lc of the second air intake channel and its inner diameter d should satisfy the following:

[0036] The average flow velocity, u, is expressed in m / s; ρ is the density of the refrigerant in the second air intake channel, expressed in kg / m³. 3 ∑k is the sum of the resistance coefficient at the inlet and the damping coefficient at the outlet of the second air intake channel, and ΔP is the pressure drop in the second air intake channel.

[0037] Thirdly, embodiments of the present invention also provide an air conditioner that may include any of the compressors described above.

[0038] By employing the above technical solutions, the static scroll cover, compressor, and air conditioner of the present invention have at least the following beneficial effects:

[0039] 1. Because the cover is a one-piece molded structure, and by setting the exhaust channel and the intake channel separately, the refrigerant in the exhaust channel can be prevented from leaking into the intake channel, thereby preventing refrigerant leakage between the high-pressure exhaust side and the low-pressure intake side.

[0040] 2. By forming the cover body by integrally molding the front cover and the stationary vortex disk in the existing technology, the screws and sealing strips required for assembling the front cover and the stationary vortex disk in the existing technology can be eliminated, thereby reducing weight, reducing processing and assembly processes, and reducing costs.

[0041] 3. A noise reduction structure is installed to reduce the noise of the refrigerant in the exhaust channel, thereby reducing noise interference;

[0042] 4. An anti-return structure is installed in the exhaust passage to prevent refrigerant backflow and improve the reliability of compressor operation;

[0043] 5. An oil-gas separation structure is installed in the exhaust channel to separate the refrigerant flowing through the exhaust channel from oil and gas, and the separated refrigeration oil is returned for reuse.

[0044] 6. A second bleed air passage is provided to guide the exhaust pressure in the exhaust passage to the back pressure chamber of the compressor, and a throttle is set to throttle the refrigerant flowing through the second bleed air passage, so as to provide a suitable back pressure for the stable operation of the moving scroll plate.

[0045] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0046] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0047] Figure 1 This is a schematic diagram of a static vortex disk cover provided in an embodiment of the present invention;

[0048] Figure 2 This is a plan view of the static vortex disk cover;

[0049] Figure 3 This is a schematic diagram of the static scroll cover, the compressor bracket, and the assembly of the moving scroll.

[0050] Figure 4 This is a schematic diagram showing how the first air intake channel on the static vortex disk cover introduces low-pressure refrigerant into the annular cavity;

[0051] Figure 5 This is a cross-sectional schematic diagram of the static vortex disk cover;

[0052] Figure 6 This is a schematic diagram of an oil-gas separation structure provided in an embodiment of the present invention;

[0053] Figure 7 This is a schematic diagram of the oil guide funnel.

[0054] Figure 8 This is a schematic diagram of the impeller structure;

[0055] Figure 9This is a schematic diagram showing the exhaust port section and steps on the static vortex disk cover;

[0056] Figure 10 This is a schematic diagram of an anti-oil return structure provided in an embodiment of the present invention;

[0057] Figure 11 This is a schematic diagram showing how the guide section and guide groove work together to guide the movement of the end cap.

[0058] Figure 12 This is a schematic diagram of a compressor provided in one embodiment of the present invention;

[0059] Figure 13 This is a schematic diagram of a throttle provided in an embodiment of the present invention.

[0060] Reference numerals: 1. Cover; 2. Moving scroll plate; 3. Support; 4. Crankshaft; 5. Motor; 6. Housing; 10. Stationary scroll gear; 11. Intake channel; 16. Oil return hole; 17. Exhaust hole; 18. Second intake channel; 19. Inner cavity; 20. Exhaust hole; 21. Exhaust hole section; 22. Second section; 23. Third section; 30. Back pressure chamber; 31. Intake channel; 100. Stationary scroll plate cover; 111. Intake port of intake channel hole; 112. Intake passage 121. Air outlet of the channel; 122. Guide groove; 123. Protrusion; 124. Guide part; 125. End cover; 130. Oil-gas separation structure; 131. Oil guide funnel; 132. Impeller; 133. Oil guide hole; 151. First air intake channel; 153. Annular cavity; 182. Throttling device; 191. Refrigerant suction side; 211. Step; 1221. Oil guide groove; 1321. Wheel body; 1322. Blade; 1821. Throttling block; 1822. Throttling groove. Detailed Implementation

[0061] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0062] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicators will also change accordingly.

[0063] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. If the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0064] like Figures 1 to 3 As shown, an embodiment of the present invention provides a static vortex disk cover 100, which includes a cover body 1, on which static vortex teeth 10 and an air intake channel 11 are provided (e.g., ...). Figure 3 (as shown) and exhaust passage.

[0065] like Figure 3 As shown, the stationary scroll cover 100 covers one end of the compressor body through the cover body 1, connecting the intake passage 11 with the intake passage 31 on the body, and allowing the stationary scroll teeth 10 to cooperate with the moving scroll teeth of the moving scroll 2 of the body to compress the low-pressure refrigerant drawn in through the intake passage 11. The exhaust passage is used to lead the compressed high-pressure refrigerant out of the cover body 1.

[0066] It should be noted that the terms "low-pressure refrigerant" and "high-pressure refrigerant" are relative. Low-pressure refrigerants have lower pressures than high-pressure refrigerants, and high-pressure refrigerants have higher pressures than low-pressure refrigerants. Additionally, as... Figure 12 As shown, the compressor body has a housing 6, a crankshaft 4, a bracket 3, and a moving scroll 2. The moving scroll 2, crankshaft 4, and bracket 3 are all housed within the housing 6. The bracket 3 provides support for the crankshaft 4. The crankshaft 4 drives the moving scroll 2 to move, causing the moving scroll teeth on the moving scroll 2 to engage with the stationary scroll teeth 10 to compress the refrigerant. The compressor body is covered by a cover 1 of the stationary scroll cover 100 via one end of the bracket 3. Figure 3 As shown, the air intake channel 31 on the body is set on the bracket 3. In a specific application example, the air intake channel 31 is an air intake channel hole set on the bracket 3.

[0067] like Figure 3As shown, the aforementioned suction channel 11 may include a suction channel hole provided on the cover 1, which communicates with the suction flow channel 31 to introduce low-pressure refrigerant into the suction flow channel 31 for compression. The suction port 111 of the suction channel hole is located on the end face of the cover 1, and when the cover 1 is closed on one end of the compressor body, the suction port 111 is opposite to the outlet of the suction flow channel 31, thus enabling communication between the suction channel hole and the suction flow channel 31. In a specific application example, such as... Figure 1 and Figure 2 As shown, the cover 1 has an inner cavity 19, which has a refrigerant intake side 191 communicating with the intake channel 11. The aforementioned stationary vortex tooth 10 is located in the inner cavity 19. In one example, the stationary vortex tooth 10 is generally disposed on the bottom surface of the inner cavity 19, and the bottom surface of the inner cavity 19 is provided with an air passage 17 for introducing compressed high-pressure gas into the exhaust channel. The sidewall of the inner cavity 19 serves as the aforementioned refrigerant intake side 191. The intake channel 11 delivers low-pressure refrigerant through the refrigerant intake side 191 between the stationary vortex tooth 10 and the moving vortex tooth for compression. Figure 1 As shown, the outlet 112 of the intake channel hole is located on the side wall of the refrigerant intake side 191 of the inner cavity 19, so that the intake channel hole is connected to the refrigerant intake side 191 of the inner cavity 19. The intake channel 11 can introduce low-pressure refrigerant in the intake channel 31 into the refrigerant intake side 191 of the inner cavity 19 through the intake channel hole.

[0068] The cover 1 mentioned above can be a one-piece molded structure, and the air intake channel 11 and the air exhaust channel are set separately. Here, "set separately" means that the air exhaust channel and the air intake channel 11 do not intersect.

[0069] In the above example, since the cover 1 is a one-piece molded structure, and by setting the exhaust channel and the intake channel 11 separately, the refrigerant in the exhaust channel can be prevented from leaking into the intake channel 11, thereby preventing refrigerant leakage between the high-pressure exhaust side and the low-pressure intake side.

[0070] Compared to the existing separate design of the front cover and stationary scroll plate, the manufacturing and assembly errors of both components result in relative displacement between them. This makes the seals prone to deformation or even failure under prolonged external forces. Furthermore, poor machining precision of the sealing groove can lead to over- or under-compression of the seals, preventing complete sealing of the gap between the front cover and stationary scroll plate, resulting in refrigerant leakage and reduced cooling capacity. This invention addresses this by using an integrated design, where the front cover and stationary scroll plate are integrally formed into a cover body 1. This cover body 1 possesses both the function of the stationary scroll plate (capable of drawing in low-pressure refrigerant and compressing it in conjunction with the moving scroll plate 2) and the function of the front cover (capable of covering one end of the housing 6 and discharging high-pressure refrigerant from the stationary scroll plate). Furthermore, since the cover 1 is a one-piece molded structure, it avoids the refrigerant leakage caused by manufacturing and assembly errors between the static vortex disk and the front cover in the prior art, thus preventing a reduction in cooling capacity.

[0071] In addition, by integrally molding the front cover and the stationary vortex disk into the cover body 1 in the prior art, the screws and sealing strips required for assembling the front cover and the stationary vortex disk in the prior art can be eliminated, thereby reducing weight, reducing processing and assembly processes, and reducing costs.

[0072] The aforementioned static vortex cover 100 also includes a noise reduction structure, which is used to reduce the noise of the refrigerant in the exhaust passage in order to reduce noise interference.

[0073] In a specific application example, such as Figure 4 As shown, the aforementioned noise reduction structure may include an annular cavity 153 disposed on the cover 1. To facilitate the processing of the annular cavity 153, an annular groove may be provided on the cover 1, and a sealing cap is fitted at the opening of the annular groove, with the sealing cap and the annular groove fitting together to form the aforementioned annular cavity 153.

[0074] like Figure 4As shown, the aforementioned exhaust channel includes an exhaust hole 20 disposed on the cover 1, and the aforementioned annular cavity 153 is disposed around the exhaust hole 20, with a wall thickness between the annular cavity 153 and the hole wall of the exhaust hole 20. The aforementioned stationary vortex cover 100 also includes a first air intake channel 151, which is used to introduce low-pressure refrigerant into the annular cavity 153. Preferably, the first air intake channel 151 is used to guide the low-pressure refrigerant in the intake channel 11 to the annular cavity 153. In one example, the aforementioned cover 1 has an inner cavity 19, which has a refrigerant intake side 191 communicating with the intake channel 11. The aforementioned stationary vortex tooth 10 is located in the inner cavity 19, and the intake channel 11 sends low-pressure refrigerant through the refrigerant intake side 191 between the stationary vortex tooth 10 and the moving vortex tooth for compression. The aforementioned first air intake channel 151 communicates with the intake channel 11 via the refrigerant intake side 191 of the inner cavity 19, so as to guide the low-pressure refrigerant in the intake channel 11 to the annular cavity 153. The first air intake channel 151 may include a first air intake channel hole disposed on the cover 1. One end of the first air intake channel hole may be located on the side wall of the refrigerant intake side 191 of the inner cavity 19, so that the first air intake channel hole communicates with the refrigerant intake side 191 of the inner cavity 19. The other end of the first air intake channel hole may be located on the cavity wall of the annular cavity 153, so as to communicate with the interior of the annular cavity 153. This allows the first air intake channel 151 to introduce the low-pressure refrigerant in the intake channel 11 into the annular cavity 153 through the refrigerant intake side 191 of the inner cavity.

[0075] In the above example, the low-pressure refrigerant in the intake channel 11 has a lower temperature. Leading this lower-temperature refrigerant to the annular cavity 153 creates a low-temperature zone within it. Conversely, the refrigerant in the exhaust port 20 is a compressed, high-pressure refrigerant, resulting in a higher temperature zone within it. This high-temperature and low-temperature zone create a temperature gradient on both sides of the wall thickness, causing the exhaust noise sound waves to be absorbed after being refracted and bent by the wall of the exhaust port 20, thus achieving noise reduction for both exhaust noise and exhaust airflow regeneration.

[0076] To better achieve noise reduction, sound-absorbing materials or micro-perforated plates or other structures can be installed on the inner wall of the aforementioned exhaust port 20.

[0077] In a specific application example, the length L of the aforementioned annular cavity 153 along the centerline of the exhaust port 20 satisfies:

[0078]

[0079] Where D is the inner diameter of the annular cavity 153, and the unit of D is m (meter); T1 is the temperature inside the annular cavity 153, and T2 is the temperature inside the exhaust port 20, and the units of T1 and T2 are both K (Kelvin).

[0080] In the above example, with the inner diameter of the annular cavity 153 determined, the length of the annular cavity 153 can be calculated based on the temperatures within the annular cavity 153 and the exhaust port 20. This allows for convenient machining based on the calculated length, thus avoiding an excessively long annular cavity 153 length L that would increase the dimensions of the installation structure. Furthermore, if the length L of the annular cavity 153 is too long, more energy is required. Calculating and appropriately setting the length L of the annular cavity 153 can prevent energy waste, as cooling requires the introduction of low-temperature components.

[0081] like Figure 5 As shown, when the exhaust channel includes an exhaust hole 20 provided on the cover 1, the exhaust hole 20 can be a stepped hole, and the diameter of the stepped hole gradually increases along the discharge direction of the refrigerant. In this way, a multi-stage resonant variable-capacity silencing cavity can be formed, so that the refrigerant can reduce noise when it flows inside.

[0082] like Figure 5 As shown, the aforementioned exhaust passage may be equipped with an oil-gas separation structure 130. The oil-gas separation structure 130 is used to separate the refrigerant flowing through the exhaust passage into oil and gas, and to return the separated refrigeration oil, so that the stationary vortex tooth 10 cooperates with the moving vortex tooth of the moving vortex disk 2 of the machine body to compress the returned refrigeration oil.

[0083] In the example above, the oil-gas separation structure 130 can separate the refrigeration oil from the exhaust gas and return it for compression.

[0084] To achieve the function of the aforementioned oil-gas separation structure 130, such as Figures 6 to 8 As shown, the oil-gas separation structure 130 may include an oil guide funnel 131 and an impeller 132. The oil guide funnel 131 is disposed within the exhaust channel, allowing refrigerant in the exhaust channel to flow in through the small opening of the oil guide funnel 131 and out through the large opening of the oil guide funnel 131. Specifically, the oil guide funnel 131 may be slightly interference-fitted into the exhaust channel, and the impeller 132 is rotatably disposed within the oil guide funnel 131. The impeller 132 is rotated by the refrigerant flowing through the oil guide funnel 131 and performs oil-gas separation on the refrigerant. Wherein, as... Figure 8 As shown, the impeller 132 has a wheel body 1321 and a plurality of blades 1322 arranged sequentially along the circumference of the wheel body 1321. The impeller 132 is rotatably mounted inside the oil guide funnel 131 via the wheel body 1321. When the high-pressure refrigerant flows through the oil guide funnel 131, the high-pressure refrigerant pushes the blades 1322, causing the impeller 132 to rotate. During the rotation of the impeller 132, oil-gas separation can be performed on the refrigerant.

[0085] It should be noted that there can be more than two impellers 132. Each impeller 132 is arranged in sequence along the direction of refrigerant discharge, and the blades 1322 on adjacent impellers 132 are staggered in the circumferential direction, which can improve the oil-gas separation effect.

[0086] like Figure 5 As shown, an oil guide hole 133 may be provided on the inner wall of the oil guide funnel 131. When the aforementioned cover 1 has an inner cavity 19, which has a refrigerant suction side 191 communicating with the suction channel 11, and the stationary vortex tooth 10 is located in the inner cavity 19, and the suction channel 11 sends low-pressure refrigerant through the refrigerant suction side 191 between the stationary vortex tooth 10 and the moving vortex tooth for compression, an oil return hole 16 may be provided on the inner cavity wall. The opening of the oil return hole 16 away from the inner cavity wall is opposite to the opening of one end of the oil guide hole 133, so that the oil return hole 16 communicates with the oil guide hole 133. The refrigerant oil separated in the oil guide funnel 131 can flow to the refrigerant suction side 191 of the inner cavity 19 through the oil guide hole 133 and the oil return hole 16. To prevent cross-flow of gas between the high and low pressure sides, a one-way throttling structure, such as a one-way valve, is installed in the oil return hole 16. This one-way throttling structure causes the refrigerant in the oil return hole 16 to flow to the refrigerant suction side 191 of the inner cavity.

[0087] The aforementioned exhaust passage also includes an anti-refrigerant backflow structure, which prevents refrigerant from flowing back into the exhaust passage. In a specific application example, such as... Figures 9 to 11 As shown, the anti-return structure may include an end cap 124, and the exhaust channel has an exhaust port section 21 and a step 211 disposed at the opening of the exhaust port section 21. The end cap 124 is movable and is used to move relative to or away from the step 211. When the end cap 124 is close to the step 211, it abuts against the step 211 to close the opening of the exhaust port section 21 and prevent refrigerant from flowing back into the exhaust port section 21. When the end cap 124 is away from the step 211, a gap is formed between the end cap 124 and the step 211, allowing the refrigerant in the exhaust port section 21 to flow out through the gap. The stationary scroll cover 100 also includes a stop structure, which stops the end cap 124 when it moves to its extreme position away from the step 211. The stop structure cooperates with the step 211 to allow the end cap 124 to move within a limited range.

[0088] In the above example, the high-pressure refrigerant in the exhaust port section 21, under its own pressure, can push the end cover 124 away from the step 211, creating a gap between the end cover 124 and the step 211. The high-pressure refrigerant in the exhaust port section 21 can flow out through the gap between the end cover 124 and the step 211. When the compressor reverses, the refrigerant moving away from the end cover 124 from the exhaust port section 21 will push the end cover 124 to close the opening of the exhaust port section 21, blocking the refrigerant passage and preventing the compressor from compressing normally, thus preventing the compressor from reversing.

[0089] In a specific application example, such as Figures 9 to 11 As shown, a protruding post 122 is provided on the side of the end cap 124 near the exhaust port section 21. The protruding post 122 can be integrally formed on the end cap 124. A guide portion 123 is provided on the outer wall of the protruding post 122. The guide portion 123 can be integrally formed on the protruding post 122. There are two or more guide portions 123, which are arranged alternately along the circumference of the protruding post 122. A guide groove 121 is provided on the step 211, and the number of guide grooves 121 is equal to the number of guide portions 123. Among them, an oil guide groove 1221 is provided between each pair of adjacent guide portions 123 on the protruding post 122. The protruding post 122 is used to insert into the exhaust port section 21, so that each guide portion 123 and each guide groove 121 are inserted and engaged in a one-to-one correspondence, and the oil guide groove 1221 is connected to the exhaust port section 21. When the end cap 124 opens the vent section 21, the refrigerant in the vent section 21 flows out through the gap via the oil guide groove 1221.

[0090] In the above example, each guide portion 123 cooperates with each guide groove 121 to guide the movement of the end cover 124, thereby improving the movement accuracy of the end cover 124.

[0091] In a specific application example, the aforementioned guide portion 123 may be T-shaped, and the aforementioned guide groove 121 may be a T-shaped groove that matches the shape of the guide portion 123.

[0092] It should be noted here that: (as...) Figure 5 As shown, when an oil guide funnel 131 is provided in the exhaust channel, the oil guide funnel 131 is located on the side of the end cover 124 away from the exhaust port section 21. The oil guide funnel 131 can serve as the aforementioned stop structure. The oil guide funnel 131 stops the end cover 124 when the end cover 124 moves to the extreme position away from the step 211.

[0093] When the exhaust channel includes an exhaust hole 20 provided on the cover 1, and the exhaust hole 20 is a stepped hole, with the diameter of the stepped hole gradually increasing along the direction of refrigerant discharge, such as Figure 5 As shown, the stepped orifice has a first section, a second section 22, and a third section 23 connected sequentially along the refrigerant discharge direction. The first section serves as the aforementioned vent section 21, and the step between the first section and the second section 22 serves as the aforementioned step 211. The aforementioned annular cavity 153 is arranged around the third section 23. The aforementioned oil guide funnel 131 is arranged inside the second section 22. A vent hole 17 is provided on the bottom surface of the aforementioned inner cavity 19, which communicates with the vent hole 20. The compressed refrigerant flows into the vent hole 20 through the vent hole 17 and is discharged through the vent hole 20.

[0094] like Figure 12As shown, embodiments of the present invention also provide a compressor, which may include any of the aforementioned stationary scroll cover 100. Because the compressor uses the aforementioned stationary scroll cover 100, refrigerant leakage from the exhaust passage to the intake passage 11 can be prevented. Furthermore, by integrally molding the front cover and the stationary scroll into the cover body 1, the screws and sealing strips required for assembling the front cover and the stationary scroll in the prior art can be eliminated, thereby reducing weight, simplifying processing and assembly, and lowering costs.

[0095] like Figure 12 As shown, the aforementioned compressor may include a second bleed air passage 18, which is used to guide the exhaust pressure in the exhaust passage to the back pressure chamber 30 of the compressor to provide back pressure for the moving scroll 2, and prevent gaps from appearing between the moving scroll 2 and the stationary scroll, which would lead to refrigerant leakage.

[0096] like Figure 12 As shown, the aforementioned compressor also includes a throttle valve 182, which is used to throttle the refrigerant flowing through the second bleed passage 18 to prevent excessive back pressure. In a specific application example, such as Figure 13 As shown, the throttle 182 may include a throttle block 1821, and the outer wall of the throttle block 1821 is provided with a throttle groove 1822 extending through both ends. There may be two or more throttle blocks 1821, which are stacked sequentially in a stepped arrangement to form a stepped column structure. This stepped column structure is used to insert into the second air intake channel 18 and cooperates with the inner wall of the second air intake channel 18, so that the refrigerant in the second air intake channel 18 flows sequentially from the throttle groove 1822 on one throttle block 1821 to the throttle groove 1822 on the next throttle block 1821 along the stacking direction of the throttle blocks 1821.

[0097] In the above example, the throttling grooves 1822 on the multiple throttling blocks 1821 cooperate to form multi-stage throttling of the refrigerant in the second air intake channel 18, which can improve the throttling and pressure reduction effect.

[0098] In a specific application example, the two adjacent throttling blocks 1821 mentioned above can be detachably connected. For example, the two adjacent throttling blocks 1821 can be detachably connected by screws. In this way, the number of throttling blocks 1821 can be increased or decreased according to the actual situation to adjust the throttling effect.

[0099] Along the refrigerant outflow direction in the second air intake channel 18, the cross-sectional area of ​​the throttling groove 1822 on each of the aforementioned throttling blocks 1821 can gradually decrease to gradually enhance the throttling effect along the refrigerant outflow direction.

[0100] Along the refrigerant outflow direction in the second air intake channel 18, the depth of the throttling groove 1822 on each throttling block 1821 can gradually decrease to gradually enhance the throttling effect along the refrigerant outflow direction.

[0101] It should be noted that: the aforementioned throttling blocks 1821 at each stage can adopt a fixed opening degree at a fixed position. In this case, the gas flow rate through the throttling groove 1822 of the throttling block 1821 remains constant, and the throttling capacity of each throttling block 1821 remains constant. Alternatively, the throttling blocks 1821 at each stage can adopt a variable opening degree with coaxial rotation under multiple phase differences. In this case, the gas flow rate through the throttling groove 1822 of the throttling block 1821 is adjustable, thereby regulating the throttling capacity of each throttling block 1821.

[0102] The length Lc and inner diameter d of the aforementioned second air intake channel 18 should satisfy the following:

[0103] The average flow velocity of the internal refrigerant, u, is in m / s; ρ is the density of the internal refrigerant in the second air intake channel 18, ρ is in kg / m³. 3 ∑k is the sum of the resistance coefficient at the inlet and the damping coefficient at the outlet of the second air intake channel 18, and ΔP is the pressure drop within the second air intake channel 18. In other words, ΔP is the pressure difference between the inlet and outlet of the second air intake channel 18.

[0104] Using the above calculation formula, the length Lc and inner diameter d of the second air intake channel 18 can be designed based on the friction coefficient of the second air intake channel 18, the average flow velocity of the refrigerant in the second air intake channel 18, the density of the refrigerant in the second air intake channel 18, the resistance coefficients at the inlet and outlet of the second air intake channel 18, and the pressure drop in the second air intake channel 18, so that the back pressure introduced into the back pressure chamber 30 can meet the requirements.

[0105] Embodiments of the present invention also provide an air conditioner, which may include any of the compressors described above. Because the air conditioner uses the aforementioned compressor, refrigerant leakage from the exhaust passage to the intake passage 11 can be prevented. Furthermore, by integrally molding the front cover and the stationary scroll plate into the cover body 1, the screws and sealing strips required for assembling the front cover and the stationary scroll plate in the prior art can be eliminated, thereby reducing weight, simplifying processing and assembly procedures, and lowering costs.

[0106] For ease of understanding, the overall structure of the present invention will be described below, and its working principle will be explained.

[0107] This invention relates to the design of a stationary scroll cover 100 and a compressor using the stationary scroll cover 100, which can be an electric scroll compressor. The compressor can be used in air conditioners and includes structures such as the stationary scroll cover 100, a moving scroll 2, a bracket 3, a crankshaft 4, a motor 5, and a housing 6. The moving scroll 2 moves under the drive of the compressor crankshaft 4. During its movement, the moving scroll 2 drives the moving scroll teeth to mesh with the stationary scroll teeth 10 on the stationary scroll cover 100, forming multiple closed compression chambers of varying sizes and volumes. After the compression process is complete, the refrigerant gas is discharged.

[0108] Compared to existing technologies, this invention integrates the existing front cover and stationary scroll plate into a single-piece stationary scroll plate cover 100, eliminating the need for sealing structures and seals between the front cover and stationary scroll plate, thus preventing internal leakage in the compressor at the location of the front cover and stationary scroll plate. Furthermore, by simplifying the two assembly parts (front cover and stationary scroll plate) into a single part (stationary scroll plate cover 100), the overall weight of the compressor can be reduced, processing and assembly procedures can be simplified, and costs can be lowered.

[0109] The above description is merely a preferred embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention's specification and drawings under the inventive concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A static vortex disc cover, characterized in that, Includes a cover (1), which is provided with a static vortex tooth (10), an air intake channel (11) and an exhaust channel; The stationary scroll cover covers one end of the compressor body through the cover body (1), so that the intake channel (11) is connected to the intake channel (31) on the body, and the stationary scroll teeth (10) cooperate with the moving scroll teeth of the moving scroll plate (2) of the body to compress the low-pressure refrigerant drawn in through the intake channel (11); the exhaust channel is used to lead the compressed high-pressure refrigerant out of the cover body (1). The cover (1) is an integrally formed structure, and the air intake channel (11) and the air exhaust channel are set separately. The exhaust channel is also provided with an anti-backflow structure to prevent refrigerant backflow in the exhaust channel; the anti-backflow structure includes an end cap (124), the exhaust channel has an exhaust port section (21) and a step (211) provided at the opening of the exhaust port section (21); the end cap (124) is movable, the end cap (124) is used to be relatively close to or away from the step (211), the end cap (124) is used to abut against the step (211) when close to the step (211) to cover the opening of the exhaust port section (21), the end cap (124) is used to form a gap with the step (211) when away from the step (211) so that the refrigerant in the exhaust port section (21) flows out through the gap; the static vortex cover also includes a stop structure, the stop structure is used to stop the end cap (124) when it moves to the extreme position away from the step (211); The end cap (124) has a protruding post (122) on one side near the exhaust port section (21). A guide portion (123) protrudes from the outer wall of the protruding post (122). There are two or more guide portions (123), arranged alternately along the circumference of the protruding post (122). A guide groove (121) is provided on the step (211), the number of guide grooves (121) being equal to the number of guide portions (123). The protruding post (122) is located on each phase... Oil guide grooves (1221) are provided between adjacent guide parts (123); the protrusion (122) is used to insert into the exhaust hole section (21) so that each guide part (123) and each guide groove (121) are inserted and matched one by one, and the oil guide groove (1221) is connected to the exhaust hole section (21); when the end cover (124) opens the opening of the exhaust hole section (21), the refrigerant in the exhaust hole section (21) flows out from the gap through the oil guide groove (1221).

2. The static vortex disk cover as described in claim 1, characterized in that, The static vortex cover also includes a noise reduction structure, which is used to reduce the noise of the refrigerant in the exhaust passage.

3. The static vortex disk cover as described in claim 2, characterized in that, The noise reduction structure includes an annular cavity (153) disposed on the cover (1), and the exhaust channel includes an exhaust hole (20) disposed on the cover (1). The annular cavity (153) is arranged around the exhaust hole (20), and there is a wall thickness between the annular cavity (153) and the hole wall of the exhaust hole (20). The static vortex cover also includes a first air intake channel (151), which is used to introduce low-pressure refrigerant into the annular cavity (153).

4. The static vortex disk cover as described in claim 3, characterized in that, The cover (1) has an inner cavity (19), the inner cavity (19) has a refrigerant intake side (191) communicating with the intake channel (11); the stationary vortex tooth (10) is located in the inner cavity (19), and the intake channel (11) sends low-pressure refrigerant into the space between the stationary vortex tooth (10) and the moving vortex tooth through the refrigerant intake side (191) for compression; The first air intake channel (151) is connected to the intake channel (11) through the refrigerant intake side (191) of the inner cavity, so as to lead the low-pressure refrigerant in the intake channel (11) to the annular cavity (153).

5. The static vortex disk cover as described in any one of claims 1 to 4, characterized in that, When the exhaust channel includes an exhaust hole (20) provided on the cover (1), the exhaust hole (20) is a stepped hole, and the diameter of the stepped hole gradually increases along the discharge direction of the refrigerant.

6. The static vortex disk cover as described in any one of claims 1 to 4, characterized in that, The exhaust passage is provided with an oil-gas separation structure (130), which is used to separate the refrigerant flowing through the exhaust passage into oil and gas, and to return the separated refrigeration oil, so that the stationary vortex tooth (10) cooperates with the moving vortex tooth of the moving vortex disk (2) of the machine body to compress the returned refrigeration oil. The oil-gas separation structure (130) includes an oil guide funnel (131) and an impeller (132). The oil guide funnel (131) is installed in the exhaust channel so that the refrigerant in the exhaust channel flows in through the small end of the oil guide funnel (131) and flows out through the large end of the oil guide funnel (131). The impeller (132) is rotatably installed in the oil guide funnel (131). The impeller (132) is driven to rotate by the refrigerant flowing through the oil guide funnel (131) and performs oil-gas separation on the refrigerant.

7. The static vortex disk cover as described in any one of claims 1 to 4, characterized in that, The air intake channel (11) includes an air intake channel hole provided on the cover (1) to communicate with the air intake channel (31) through the air intake channel hole, so as to introduce the low-pressure refrigerant in the air intake channel (31) for compression; The air intake (111) of the air intake channel hole is located on the end face of the cover (1). When the cover (1) covers one end of the compressor body, the air intake (111) is opposite to the outlet of the air intake channel (31) so that the air intake channel hole is connected to the air intake channel (31).

8. A compressor, characterized in that, Includes the static vortex disc cover (100) according to any one of claims 1 to 7.

9. The compressor as claimed in claim 8, characterized in that, The compressor includes a second air intake passage (18), which is used to introduce the exhaust pressure in the exhaust passage to the back pressure chamber (30) of the compressor. The compressor also includes a throttle (182), which is used to throttle the refrigerant flowing through the second air intake channel (18); wherein, the throttle (182) includes a throttle block (1821), and the outer wall of the throttle block (1821) is provided with a throttle groove (1822) that runs through both ends; the number of throttle blocks (1821) is two or more, and they are stacked in sequence in a stepped manner to form a stepped column structure; the stepped column structure is used to be inserted into the second air intake channel (18) and cooperates with the inner wall of the second air intake channel (18), so that the refrigerant in the second air intake channel (18) flows sequentially from the throttle groove (1822) on one throttle block (1821) to the throttle groove (1822) on the next throttle block (1821) along the stacking direction of the throttle blocks (1821).

10. The compressor as claimed in claim 9, characterized in that, The two adjacent throttling blocks (1821) are detachably connected; And / or, along the refrigerant outflow direction in the second air intake channel (18), the cross-sectional area of ​​the throttling groove (1822) on each throttling block (1821) gradually decreases; And / or, along the refrigerant outflow direction in the second air intake channel (18), the depth of the throttling groove (1822) on each throttling block (1821) gradually decreases.

11. The compressor as claimed in claim 9 or 10, characterized in that, The length Lc and inner diameter d of the second air intake channel (18) should satisfy the following: ; in: The friction coefficient of the second air intake channel (18) is... The average flow rate of the refrigerant in the second air intake channel (18) is... The unit is m / s; The density of the refrigerant in the second air intake channel (18) The unit is kg / m 3 , The sum of the resistance coefficient at the inlet and the damping coefficient at the outlet of the second air intake channel (18) is given. The pressure drop within the second air intake channel (18).

12. An air conditioner, characterized in that, The compressor includes any one of claims 8 to 11.

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