Pump body structure, compressor and air conditioner applying same

Abstract

The pump body structure comprises an air cylinder, a roller, a sliding piece and a guide assembly, the roller is arranged in the air cylinder, the sliding piece is arranged in a sliding piece groove of the air cylinder, and a cavity in the air cylinder is divided into a compression cavity and an air suction cavity by the sliding piece; a first groove formed in the moving direction of the sliding piece is formed in the side, facing the compression cavity, of the sliding piece, one end of the guide assembly communicates with the compression cavity, the other end of the guide assembly extends into the first groove, and high-pressure gas in the compression cavity acts on the sliding piece through the first groove so that the sliding piece can move towards the roller. High-pressure gas in the compression cavity is introduced into the first groove through the guide assembly, so that gas pressure directly acts on the sliding piece, and resultant force superposed with spring force is formed. By means of the design, contact between the sliding piece and the roller can still be kept when pressure changes suddenly, and separation is avoided. And meanwhile, after the slip sheet is in closer contact with the roller, the clearance leakage amount is reduced, so that the energy loss and the pressure fluctuation are reduced, and the noise caused by leakage is indirectly inhibited.

Description

Technical Field

[0001] The present invention belongs to the technical field of air conditioners, and particularly relates to a pump body structure, a compressor, and an air conditioner using the same. Background Art

[0002] The working principle of a rolling piston compressor is as follows: Inside a cylindrical cylinder, a cylindrical roller is placed. The rotation center of the roller coincides with the center of the cylinder. The roller makes a rotational motion driven by an eccentric circle of a crankshaft sleeved on its inner diameter under the drive of an electric motor. Inside a sliding vane groove of the cylinder, a sliding vane that can slide back and forth is placed. One end is equipped with a pump spring to ensure that one end of the sliding vane always contacts the outer circle of the roller. The sliding vane makes a reciprocating motion inside the sliding vane groove. Therefore, the sliding vane, the inner surface of the cylinder, the outer surface of the roller, and the upper and lower flange end faces form a high-pressure chamber and a low-pressure chamber. During operation, when the crankshaft drives the roller to rotate one week, it sucks air from the low-pressure chamber and discharges air from the high-pressure chamber to complete one working cycle.

[0003] During the above process, under the action of the spring at the tail of the sliding vane, the roller and the head of the sliding vane always remain in contact. However, when the compressor operates with liquid carried in during low-frequency suction, the high pressure in the compression chamber causes the liquid refrigerant to vaporize, resulting in a huge change in the pressure in the compression chamber. At this time, the spring does not have enough force to support the sliding vane to contact the roller, causing the two to separate. Part of the high-pressure gas will leak from between the roller and the sliding vane. Then, due to the elastic force of the spring, the sliding vane and the spring will quickly come into contact again, generating a metallic knocking "tapping sound", which affects the listening experience. Therefore, as one of the core components of the compressor pump body, eliminating or reducing the noise at low frequencies and reducing the power consumption during its reciprocating motion are of great significance for improving the listening experience and the overall performance. Summary of the Invention

[0004] In view of this, the present invention provides a pump body structure, a compressor, and an air conditioner using the same, which can effectively prevent the sliding vane from separating from the roller during low-frequency operation of the compressor, thereby solving the noise generated after the separation of the sliding vane and the roller.

[0005] To solve the above problems, according to one aspect of the present application, an embodiment of the present invention provides a pump body structure. The pump body structure includes a cylinder, a roller, a sliding vane, and a guiding assembly. The roller is arranged inside the cylinder. The sliding vane is arranged in a sliding vane groove of the cylinder and divides the cavity inside the cylinder into a compression chamber and a suction chamber. One side of the sliding vane facing the compression chamber has a first groove opened along the movement direction of the sliding vane. One end of the guiding assembly is communicated with the compression chamber, and the other end extends into the first groove. The high-pressure gas in the compression chamber acts on the sliding vane through the first groove so that the sliding vane can move towards the roller.

[0006] In some embodiments, the pump body structure further includes a flange assembly disposed at an end of the cylinder. The end face of the flange assembly, the wall of the sliding vane groove, and the first groove together form a pressure acting chamber; the guiding assembly includes a guiding groove that communicates with the pressure acting chamber.

[0007] In some embodiments, one end of the guiding groove communicates with the exhaust port of the cylinder, and the other end of the guiding groove is located at the wall of the sliding vane groove corresponding to the first end of the first groove when the compressor finishes exhausting; wherein, the first end of the first groove is the end of the first groove close to the roller.

[0008] And / or the width of the guiding groove is 0.1 mm - 0.2 mm.

[0009] In some embodiments, there are at least two first grooves; a second groove is further formed on a side of the sliding vane facing the compression chamber, and the second groove is perpendicular to the first groove and is used to communicate adjacent first grooves.

[0010] In some embodiments, an intersection of a side of the sliding vane facing the compression chamber and the upper end face of the sliding vane has a third groove, the third groove is formed along the movement direction of the sliding vane, and the third groove communicates with the second groove; one end of the guiding groove communicates with the compression chamber, and the other end of the guiding groove communicates with the third groove.

[0011] In some embodiments, a distance L between the first end of the first groove and the top of the sliding vane and a distance H that the sliding vane extends into the cylinder cavity when the compressor starts exhausting satisfy: L > H; wherein, the first end of the first groove is the end of the first groove close to the roller, and the top of the sliding vane is the end where the sliding vane is connected to the roller; a distance between the first end of the third groove and the top of the sliding vane is the same as the distance between the first end of the first groove and the top of the sliding vane.

[0012] In some embodiments, a side of the sliding vane facing the suction chamber has a fourth groove formed along the movement direction of the sliding vane; there are at least two fourth grooves.

[0013] In some embodiments, the cross-sectional shapes of the first groove and the fourth groove are one of a rectangle, a circle, a semi-circle, a triangle, or a polygon.

[0014] And / or the depth h of the first groove and the fourth groove satisfies: 6 μm ≤ h ≤ 12 μm.

[0015] According to another aspect of the present application, an embodiment of the present invention provides a compressor, and the compressor includes the above-mentioned pump body structure.

[0016] According to another aspect of the present application, an embodiment of the present invention provides an air conditioner, and the air conditioner includes the above-mentioned compressor.

[0017] Compared with the prior art, the pump body structure of the present invention has at least the following beneficial effects:

[0018] The pump body structure provided by the present invention includes a cylinder, a roller, a sliding vane, and a guiding assembly. The roller is arranged inside the cylinder. The sliding vane is arranged in the sliding vane groove of the cylinder and divides the cavity inside the cylinder into a compression chamber and a suction chamber. One side of the sliding vane facing the compression chamber has a first groove opened along the movement direction of the sliding vane. One end of the guiding assembly is communicated with the compression chamber, and the other end extends into the first groove. The high-pressure gas in the compression chamber acts on the sliding vane through the first groove so that the sliding vane can move towards the roller.

[0019] When the compressor operates at low frequency, the gasification of the liquid refrigerant causes the pressure in the compression chamber to fluctuate violently. The spring force is not sufficient to maintain the contact between the sliding vane and the roller, resulting in their separation. At this time, the high-pressure gas leaks from the gap, and then the sliding vane is reset due to the spring force, generating a metallic knocking sound ("clattering sound"). In this embodiment, the high-pressure gas in the compression chamber is introduced into the first groove of the sliding vane through the guiding assembly, so that the gas pressure directly acts on the back of the sliding vane, forming a resultant force that is superimposed with the spring force. This design can still maintain the contact between the sliding vane and the roller and avoid separation when the pressure changes suddenly. At the same time, after the sliding vane and the roller are in closer contact, the amount of gap leakage is reduced, thereby reducing energy loss and pressure fluctuation, and indirectly suppressing the noise caused by leakage.

[0020] Moreover, lubricating oil can be stored in the first groove on the side of the sliding vane to increase the thickness of the surface lubricating oil film, reduce the surface friction resistance, and thus reduce the friction power consumption.

[0021] The compressor provided by the present invention is designed based on the above-mentioned pump body structure, and for its beneficial effects, reference can be made to the beneficial effects of the above-mentioned pump body structure, which will not be elaborated here one by one.

[0022] The air conditioner provided by the present invention is designed based on the above-mentioned compressor, and for its beneficial effects, reference can be made to the beneficial effects of the above-mentioned compressor, which will not be elaborated here one by one.

[0023] The above description is only an overview of the technical solution of the present invention. In order to be able to understand the technical means of the present invention more clearly and implement it in accordance with the content of the description, the following takes the preferred embodiment of the present invention and combines with the drawings to elaborate in detail as follows. Description of the Drawings

[0024] To more clearly illustrate the technical solutions of the embodiments of the present invention, the following will briefly introduce the drawings required for the description of the embodiments. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0025] Figure 1 It is a schematic structural diagram of a pump body structure provided by an embodiment of the present invention when starting to exhaust;

[0026] Figure 2 It is a schematic structural diagram of a pump body structure provided by an embodiment of the present invention when the exhaust is completed;

[0027] Figure 3 It is a schematic structural diagram of a sliding vane in a pump body structure provided by an embodiment of the present invention;

[0028] Figure 4 It is a schematic structural diagram of a sliding vane in a pump body structure provided by an embodiment of the present invention facing the compression chamber side;

[0029] Figure 5 It is a schematic structural diagram of a sliding vane in a pump body structure provided by an embodiment of the present invention facing the suction chamber side;

[0030] Figure 6 It is a cross-sectional view of a sliding vane in a pump body structure provided by an embodiment of the present invention facing the suction chamber side;

[0031] Figure 7 It is a cross-sectional view of a pump body structure provided by an embodiment of the present invention when starting to exhaust;

[0032] Figure 8 is Figure 7 a partial enlarged view of A in;

[0033] Figure 9 It is a cross-sectional view of a pump body structure provided by an embodiment of the present invention when the exhaust is completed;

[0034] Figure 10 is Figure 9 a partial enlarged view of B in.

[0035] Wherein:

[0036] 1. Cylinder; 11. Compression chamber; 12. Suction chamber; 2. Roller; 3. Sliding vane; 31. First groove; 32. Second groove; 33. Third groove; 34. Fourth groove; 4. Guide assembly. Detailed implementation manners

[0037] To further elaborate on the technical means and effects adopted by the present invention to achieve the intended invention purpose, the following specifically describes, with reference to the accompanying drawings and preferred embodiments, the specific implementation manners, structures, features, and their effects of the application based on the present invention. In the following description, different "one embodiment" or "embodiment" do not necessarily refer to the same embodiment. In addition, the specific features, structures, or characteristics in one or more embodiments can be combined in any suitable form.

[0038] In the description of the present invention, it should be clear that the terms "first", "second", etc. in the description and claims of the present invention and the above-mentioned drawings are used to distinguish similar objects and do not necessarily need to describe a specific order or sequence; the terms "vertical", "horizontal", "longitudinal", "front", "rear", "left", "right", "up", "down", "horizontal", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention, rather than meaning that the indicated device or element must have a specific orientation or position, so it cannot be understood as a limitation to the present invention.

[0039] In the description of the present invention, it should be noted that unless otherwise clearly specified and limited, the terms "installation", "connection", and "connection" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0040] Embodiment 1

[0041] This embodiment provides a pump body structure, as Figures 1 - 10 shown. The pump body structure includes a cylinder 1, a roller 2, a sliding vane 3, and a guiding component 4. The roller 2 is arranged inside the cylinder 1. The sliding vane 3 is arranged in the sliding vane groove of the cylinder 1 and divides the cavity inside the cylinder 1 into a compression chamber 11 and a suction chamber 12. One side of the sliding vane 3 facing the compression chamber 11 has a first groove 31 opened along the movement direction of the sliding vane 3. One end of the guiding component 4 is communicated with the compression chamber 11, and the other end extends into the first groove 31. The high-pressure gas in the compression chamber 11 acts on the sliding vane 3 through the first groove 31 to enable it to move towards the roller 2.

[0042] The cylinder 1 serves as the main body of the pump body structure, and internally houses the roller 2, forming the working spaces of the compression chamber 11 and the suction chamber 12. The roller 2 is driven to rotate by the eccentric circle of the crankshaft, and changes the volumes of the compression chamber and the suction chamber by rolling, completing the suction, compression, and exhaust cycles. The sliding vane 3 is installed in the sliding vane groove, and its head is pushed by the spring force to contact the roller, separating the compression chamber (high pressure) and the suction chamber (low pressure). The first groove 31 is opened on the side of the sliding vane facing the compression chamber, providing a working surface for the high-pressure gas, generating an additional thrust through the gas pressure, and reducing the risk of separation between the sliding vane and the roller. One end of the guiding assembly 4 is connected to the high-pressure area of the compression chamber, and the other end extends to the first groove of the sliding vane. Its function is to introduce the high-pressure gas in the compression chamber to the back of the sliding vane, and assist the spring force through the gas pressure to ensure close contact between the sliding vane and the roller.

[0043] When the compressor operates at low frequency, the gasification of the liquid refrigerant causes violent pressure fluctuations in the compression chamber, and the spring force is insufficient to maintain the contact between the sliding vane and the roller, resulting in their separation. At this time, the high-pressure gas leaks from the gap, and then the sliding vane is reset by the spring force, generating a metallic knocking sound ("tapping sound"). In this embodiment, the guiding assembly 4 introduces the high-pressure gas in the compression chamber into the first groove 31 of the sliding vane 3, so that the gas pressure directly acts on the back of the sliding vane 3, forming a resultant force superimposed with the spring force. This design can still maintain the contact between the sliding vane 3 and the roller 2 during sudden pressure changes, avoiding separation. At the same time, after the sliding vane 3 and the roller 2 are in closer contact, the gap leakage amount is reduced, thereby reducing the energy loss and pressure fluctuations, and indirectly suppressing the noise caused by leakage.

[0044] In addition, lubricating oil can be stored in the first groove 31 to increase the thickness of the surface lubricating oil film, reduce the surface friction resistance, and thus reduce the friction power consumption.

[0045] In a specific embodiment, the pump body structure further includes a flange assembly, the flange assembly is arranged at the end of the cylinder 1, and the end face of the flange assembly, the wall of the sliding vane groove, and the first groove 31 together form a pressure acting chamber; the guiding assembly 4 includes a guiding groove, and the guiding groove communicates with the pressure acting chamber.

[0046] In this embodiment, the flange assembly is installed at the end of the cylinder 1. Its main functions are to seal the end face of the cylinder 1 and jointly form a pressure acting chamber with the sliding vane groove and the first groove 31 on the sliding vane 3. Specifically, the flange assembly cooperates with the end face of the cylinder 1 to prevent gas from leaking from the end, maintaining the pressure difference between the compression chamber 11 and the suction chamber 12; it forms a pressure acting chamber. Through the flange end face, the wall of the sliding vane groove, and the first groove 31 on the sliding vane 3, a closed chamber is jointly enclosed, namely the pressure acting chamber. This pressure acting chamber is directly connected to the compression chamber 11, and can guide the high-pressure gas to the back of the sliding vane 3, using the gas pressure to assist the spring force to ensure that the sliding vane 3 always tightly adheres to the roller 2, reducing the problem of the sliding vane detachment caused by pressure mutation during low-frequency operation. The core function of the pressure acting chamber is to dynamically adjust the force on the sliding vane 3 using the high-pressure gas in the compression chamber. When the compressor operates at low frequency or the suction is liquid-carrying, the pressure in the compression chamber 11 may fluctuate violently. Relying solely on the spring force is not sufficient to maintain the contact between the sliding vane 3 and the roller 2. At this time, the high-pressure gas in the pressure acting chamber exerts an additional thrust through the back of the sliding vane 3 to compensate for the deficiency of the spring force, avoiding leakage and metal knocking sounds caused by their separation.

[0047] In this embodiment, the collaborative design of the flange assembly and the pressure acting chamber realizes the dynamic regulation of the force on the sliding vane by guiding the groove to connect the compression chamber 11 and the back area of the sliding vane. This structure is particularly important under low-frequency or liquid-carrying suction conditions, which can effectively compensate for the deficiency of the spring force, reduce leakage and noise, and improve the reliability and energy efficiency of the compressor.

[0048] In a specific embodiment, as Figure 3 and Figure 4 shown, one end of the guiding groove is connected to the exhaust port of the cylinder 1, and the other end of the guiding groove is located at the groove wall of the sliding vane groove corresponding to the first end of the first groove 31 when the compressor finishes exhausting; wherein, the first end of the first groove 31 is the end of the first groove 31 close to the roller 2.

[0049] During the operation of the compressor, the sliding vane 3 reciprocates in the sliding vane groove as the roller 2 rotates. When the compressor completes the exhaust stage, the position of the sliding vane 3 reaches a certain limit point of its movement trajectory. At this time, the first end (the end close to the roller) of the first groove 31 just moves to a specific groove wall position of the sliding vane groove. At this time, the other end of the guiding groove only needs to cover the distance from the compression chamber to this groove wall position without additional extension, that is to say, the guiding groove is the shortest at this time.

[0050] The shorter guiding groove can shorten the flow time of the high-pressure gas from the compression chamber to the pressure acting chamber, enabling the gas pressure to act on the sliding vane 3 more quickly, and assisting the spring force to maintain the close contact between the sliding vane 3 and the roller 2. During low-frequency liquid operation, sudden pressure changes in the compression chamber 11 can easily cause the separation of the sliding vane 3 and the roller 2. Minimizing the length of the guiding groove can reduce the cross-sectional area of the gas leakage path and lower the leakage amount of the high-pressure gas. Additionally, minimizing the length of the guiding groove also simplifies the structural design of the cylinder 1, avoiding the processing difficulty and leakage risks caused by redundant length.

[0051] The width of the guiding groove is 0.1 mm - 0.2 mm. The guiding groove within this dimension range can ensure that the high-pressure gas in the compression chamber 11 effectively enters the first groove 31 through the guiding groove, forming a sufficient pressure acting chamber to push the sliding vane 3 towards the roller 2. This avoids the increase in air flow resistance caused by an overly small groove width and prevents the problem of increased gas leakage caused by an overly large groove width.

[0052] In a specific embodiment, as Figure 3 and Figure 4 shown, the first groove 31 has at least two; on the side of the sliding vane 3 facing the compression chamber 11, a second groove 32 is also provided, and the second groove 32 is perpendicular to the first groove 31 and is used to connect adjacent first grooves 31.

[0053] When the sliding vane operates in low-frequency liquid, the pressure in the compression chamber 11 fluctuates violently. Multiple first grooves 31 can guide the high-pressure gas to act on the sliding vane 3 from different positions, forming a more uniform pressure field. This avoids the uneven force on the sliding vane 3 caused by local pressure concentration in a single first groove 31, thereby improving the stability of the contact between the sliding vane 3 and the roller 2. Additionally, multiple first grooves 31 increase the contact area between the sliding vane 3 and the high-pressure gas, enabling the contact force between the sliding vane 3 and the roller 2 to be compensated by the gas force over a larger area when the spring force is insufficient, preventing their separation. The second groove 32 is perpendicular to the first groove 31 and connects adjacent first grooves 31. This setting can balance the pressure difference between the first grooves 31, ensuring the rapid flow of high-pressure gas between different first grooves 31 and avoiding the sliding vane vibration caused by overly high or low local pressure.

[0054] In a specific embodiment, as Figure 3 and Figure 4 shown, at the intersection of the side of the sliding vane 3 facing the compression chamber 11 and the upper end surface of the sliding vane 3, there is a third groove 33. The third groove 33 is opened along the movement direction of the sliding vane 3, and the third groove 33 is connected to the second groove 32; one end of the guiding groove is connected to the compression chamber 11, and the other end of the guiding groove is connected to the third groove 33.

[0055] The third groove 33 is located at the intersection of the side of the sliding vane 3 facing the compression chamber 11 and the upper end surface, is opened along the movement direction of the sliding vane 3, and communicates with the second groove 32. Its core function is to introduce the high-pressure gas in the compression chamber 11 into the second groove 32 of the sliding vane 3 through connection with the guiding component 4, so that the transmission of the high-pressure gas is smoother, thereby enhancing the adhesion force of the sliding vane 3 to the roller 2 and avoiding leakage and noise caused by the separation of the two.

[0056] In this embodiment, the transmission path of the high-pressure gas is successively: the compression chamber 11, the guiding component 4, the third groove 33, the second groove 32, the first groove 31, and the sliding vane 3. Specifically, the high-pressure gas enters the third groove 33 from the compression chamber 11 through the guiding groove of the guiding component 4. The third groove 33 communicates with the second groove 32, and the second groove 32 communicates with the first groove 31. Therefore, after the high-pressure gas flows from the third groove 33 into the second groove 32, it is evenly distributed into multiple first grooves 31 to form a uniform pressure field covering multiple regions of the sliding vane 3. Then, each first groove 31 transmits the high-pressure gas to the sliding vane 3, and the gas pressure acts on the side of the sliding vane 3 facing the compression chamber 11, pushing the sliding vane 3 to overcome the additional resistance other than the spring force, ensuring that the head of the sliding vane 3 always closely adheres to the outer surface of the roller 2, reducing clearance leakage and metal impact noise.

[0057] In a specific embodiment, the distance L between the first end of the first groove 31 and the top of the sliding vane 3 and the distance H that the sliding vane 3 extends into the cylinder 1 cavity when the compressor starts to exhaust satisfy: L > H; wherein, the first end of the first groove 31 is the end of the first groove 31 close to the roller 2, and the top of the sliding vane 3 is the end where the sliding vane 3 is connected to the roller 2; the distance between the first end of the third groove 33 and the top of the sliding vane 3 is the same as the distance between the first end of the first groove 31 and the top of the sliding vane 3.

[0058] L is the distance between the first end (the end close to the roller 2) of the first groove 31 and the top of the sliding vane 3. At the same time, L also represents the distance between the first end (the end close to the roller 2) of the third groove 33 and the top of the sliding vane 3. The top of the sliding vane 3 refers to the end where the sliding vane 3 is connected to the roller 2. H is the distance that the sliding vane 3 extends into the cylinder cavity when the compressor starts to exhaust. At this time, the sliding vane 3 is in the maximum extended state, and the compression chamber 11 is about to exhaust gas.

[0059] When the compressor enters the exhaust stage, the sliding vane 3 will move due to the change in pressure in the compression chamber. If L > H, the depth H of the sliding vane 3 extending into the cylinder is always less than the distance L from the end of the first groove 31 to the top of the sliding vane 3. This means that during the exhaust process, the starting ends (the ends close to the roller 2) of the first groove 31 and the third groove 33 are always located inside the sliding vane groove and do not enter the compression chamber area. Therefore, the high-pressure gas will not directly leak out of the sliding vane groove through the first groove 31 and the third groove 33, but is confined in the pressure acting chamber formed by the sliding vane groove wall, the flange end face, and the first groove 31. The pressure acting chamber needs to introduce high-pressure gas through the guiding assembly 4 to push the sliding vane 3 against the roller 2. If L ≤ H, during exhaust, the first groove 31 and / or the third groove 33 may enter the compression chamber 11, resulting in the direct connection between the pressure acting chamber and the compression chamber 11. At this time, the high-pressure gas cannot effectively act on the sliding vane 3, but will leak through the first groove 31 and / or the third groove 33, weakening the thrust on the sliding vane 3.

[0060] In a specific embodiment, as Figure 5 and Figure 6 shown, on the side of the sliding vane 3 facing the suction chamber 12, there are fourth grooves 34 opened along the movement direction of the sliding vane 3; there are at least two of the fourth grooves 34. The suction chamber 12 is a low-pressure chamber, and the flow state of the refrigerant inside it will affect the movement resistance of the sliding vane 3. The fourth grooves 34 are opened along the movement direction of the sliding vane 3, which can guide the low-pressure gas or lubricating oil in the suction chamber 12 into the contact surface between the sliding vane 3 and the sliding vane groove, forming a lubricating film and reducing the direct friction between metals. At the same time, at least two fourth grooves 34 can disperse the pressure distribution, avoid local high pressure causing the sliding vane 3 to get stuck, and make the movement of the sliding vane 3 more stable.

[0061] In a specific embodiment, the cross-sectional shapes of the first groove 31 and the fourth groove 34 are one of a rectangle, a circle, a semicircle, a triangle, or a polygon.

[0062] When the cross-sectional shape of the first groove 31 is a rectangle, the right-angle structure of the rectangle can provide a stable gas flow channel, enabling the high-pressure gas to act evenly on the surface of the sliding vane and enhancing the thrust on the sliding vane; when the cross-sectional shape of the first groove 31 is a circle or a semicircle, the smooth inner wall can reduce the gas flow resistance, reduce the energy loss, and at the same time reduce the friction between the sliding vane and the contact surface of the first groove 31; when the cross-sectional shape of the first groove 31 is a polygon, the polygon cross-section can balance the gas flow uniformity and the friction loss. For example, the hexagonal first groove 31 can not only reduce the flow resistance but also maintain the thrust stability through the straight sides.

[0063] When the cross-sectional shape of the fourth groove 34 is rectangular, the right-angle structure of the rectangle helps the refrigerant to quickly enter the suction cavity, reducing the suction resistance and improving the suction efficiency. When the cross-sectional shape of the fourth groove 34 is circular or semi-circular, the smooth inner wall can reduce the turbulent loss during the flow of the refrigerant, reducing the suction noise. At the same time, it is beneficial to the uniform distribution of the lubricating oil in the groove, reducing the dry friction between the sliding vane and the groove wall. When the cross-sectional shape of the fourth groove 34 is polygonal, such as trapezoidal, it can balance the suction efficiency and lubrication requirements. The wider channel at the top facilitates the rapid filling of the refrigerant, and the flat bottom surface is conducive to the stable movement of the sliding vane.

[0064] The depths h of the first groove 31 and the fourth groove 34 satisfy: 6μm ≤ h ≤ 12μm. When the depths of the first groove 31 and the fourth groove 34 are too shallow (less than 6μm), the cross-sectional area of gas flow is insufficient, and it may not be possible to form enough pressure difference to push the sliding vane 3 to reset quickly. While if the depth is too large (greater than 12μm), it will lead to an increase in gas leakage, weakening the effective pressure of the compression cavity 11. The depth range of 6μm - 12μm can balance the gas guiding efficiency and leakage control, ensuring that the sliding vane 3 can still stably contact the roller 2 during the pressure fluctuation of the compression cavity 11, reducing the metal knocking sound caused by separation. In addition, this depth range is beneficial to form a stable lubricating oil film between the sliding vane 3 and the cylinder wall, promoting the uniform distribution of the oil film, reducing the direct contact of metals, thereby reducing the friction power consumption and wear.

[0065] The pump body structure provided in this embodiment converts the high-pressure gas in the compression cavity into the driving force for the sliding vane to press against the roller, solving the problems of leakage and noise caused by insufficient spring force in the traditional one. And the parameters of each groove are defined, achieving the effects of controlling leakage and suppressing noise.

[0066] Embodiment 2

[0067] This embodiment provides a compressor, and the compressor includes the pump body structure described in Embodiment 1.

[0068] After adopting the pump body structure in the embodiment, the compressor in this embodiment has the following effects. On the one hand, it reduces or eliminates the "tapping sound" generated during low-frequency liquid-carrying operation, thereby reducing the low-frequency noise. On the other hand, it increases the lubrication between the sliding vane and the sliding vane groove, reducing its friction power consumption and improving the overall performance of the compressor.

[0069] Embodiment 3

[0070] This embodiment provides an air conditioner, and the air conditioner includes the compressor described in Embodiment 2.

[0071] In summary, it is easy for those skilled in the art to understand that, on the premise of no conflict, the above-mentioned advantageous technical features can be freely combined and superimposed.

[0072] The above are only the preferred embodiments of the present invention, and do not impose any form of limitation on the present invention. Any simple modification, equivalent change, and modification made to the above embodiments based on the technical essence of the present invention still fall within the scope of the technical solution of the present invention.

Claims

1. A pump body structure, characterized in that, The pump body structure includes a cylinder, a roller, a sliding vane, and a guiding component. The roller is arranged inside the cylinder. The sliding vane is arranged in the sliding vane groove of the cylinder and divides the cavity inside the cylinder into a compression chamber and a suction chamber. One side of the sliding vane facing the compression chamber has a first groove opened along the movement direction of the sliding vane. One end of the guiding component is communicated with the compression chamber, and the other end extends into the first groove. The high-pressure gas in the compression chamber acts on the sliding vane through the first groove so that the sliding vane can move towards the roller.

2. The pump body structure according to claim 1, characterized in that, The pump body structure further includes a flange component. The flange component is arranged at the end of the cylinder. The end face of the flange component, the groove wall of the sliding vane groove, and the first groove jointly form a pressure acting chamber. The guiding component includes a guiding groove, and the guiding groove is communicated with the pressure acting chamber.

3. The pump body structure according to claim 2, characterized in that, One end of the guiding groove is communicated with the exhaust port of the cylinder, and the other end of the guiding groove is located at the groove wall of the sliding vane groove corresponding to the first end of the first groove when the compressor finishes exhausting. Wherein, the first end of the first groove is the end of the first groove close to the roller. And / or the width of the guiding groove is 0.1 mm - 0.2 mm.

4. The pump body structure according to claim 1, characterized in that, There are at least two first grooves. One side of the sliding vane facing the compression chamber is also provided with a second groove, and the second groove is perpendicular to the first groove and is used for communicating adjacent first grooves.

5. The pump body structure according to claim 4, characterized in that, The intersection of the side of the sliding vane facing the compression chamber and the upper end face of the sliding vane has a third groove, and the third groove is opened along the movement direction of the sliding vane. The third groove is communicated with the second groove. One end of the guiding groove is communicated with the compression chamber, and the other end of the guiding groove is communicated with the third groove.

6. The pump body structure according to claim 5, characterized in that, The distance L between the first end of the first groove and the top of the sliding vane and the distance H that the sliding vane extends into the cylinder cavity when the compressor starts exhausting satisfy: L > H. Wherein, the first end of the first groove is the end of the first groove close to the roller, and the top of the sliding vane is the end where the sliding vane is connected to the roller. The distance between the first end of the third groove and the top of the sliding vane is the same as the distance between the first end of the first groove and the top of the sliding vane.

7. The pump body structure according to claim 1, wherein, One side of the sliding vane facing the suction chamber has a fourth groove opened along the movement direction of the sliding vane. There are at least two fourth grooves.

8. The pump body structure according to claim 7, characterized in that, The cross-sectional shapes of the first groove and the fourth groove are one of rectangle, circle, semi-circle, triangle or polygon. And / or the depth h of the first groove and the fourth groove satisfies: 6 μm ≤ h ≤ 12 μm.

9. A compressor, characterized in that, The compressor includes the pump body structure according to any one of claims 1 - 8.

10. An air conditioner, characterized in that, The air conditioner includes the compressor according to claim 9.

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