Pump body structure and compressor and air conditioner formed thereby

Abstract

The utility model provides a kind of pump body structure and compressor and air conditioner formed by it, pump body structure includes: cylinder, hollow chamber is provided in the inside of cylinder, the cross section of hollow chamber is oval, suction port, first exhaust port and second exhaust port are provided in hollow chamber, in the compression path of hollow chamber, second exhaust port is located at the rear side of first exhaust port;Crankshaft is located in the inside of hollow chamber, the cross section of crankshaft is circular;The center of circle of crankshaft is overlapped with the center of circle of the hollow chamber;Slip sheet, one end of slip sheet is fixed with the side edge of crankshaft, and the other end of slip sheet is abutted with the inside wall of the hollow chamber.This application is due to second exhaust port is located at the position where first exhaust port is close to the rear side of compression path, to reduce clearance volume in the process of compressor exhaust, so that gaseous refrigerant is more fully compressed, avoid the problem such as high energy consumption, low performance caused by large clearance volume in prior art.

Description

Technical Field

[0001] This utility model relates to the technical field of pump body structure, and in particular to a pump body structure and the compressor and air conditioner formed therefrom. Background Technology

[0002] In the traditional rotary compressor pump body structure, the crankshaft eccentric circle and rollers are the main causes of unbalanced torque. In order to solve the unbalanced torque when the compressor rotates, a balance block needs to be designed to balance the torque. However, the balance block cannot completely solve the problem of unbalanced torque in the compressor and may cause problems such as compressor vibration and crankshaft wear.

[0003] To address the crankshaft wear problem, Chinese patent application CN119122810A discloses a pump body structure, a compressor, and an air conditioner. The pump body structure includes a flange assembly, a cylinder, a crankshaft, and multiple vanes. The flange assembly has two or more intake ports and two or more exhaust ports. The cylinder has a hollow cavity connected to the intake and exhaust ports via air passages. The hollow cavity is elliptical in shape. The crankshaft is rotatably mounted within the hollow cavity and has multiple sliding grooves spirally distributed along its axis. Multiple vanes are movably disposed within each groove, dividing the hollow cavity into multiple independent sealed chambers. This structure eliminates the eccentric design, reducing the impact of eccentric forces on the shaft system and improving the compressor's service life.

[0004] However, the above-mentioned pump body structure has the problem of large clearance volume, which affects the compressor efficiency. At the same time, the idea of ​​setting the suction and exhaust structure on the major and minor axes of the ellipse in the above-mentioned pump body structure will cause several chambers to be in a non-suction and exhaust state, which will reduce the cavity utilization rate to a certain extent and increase the energy consumption caused by more sliding friction. Furthermore, the exhaust port design in this structure will lead to the problem of lower compression pressure, resulting in a decrease in cooling capacity and an increase in energy consumption. Utility Model Content

[0005] To overcome the problems existing in related technologies, one of the objectives of this utility model is to provide a pump body structure in which the second exhaust port is located near the rear side of the compression path of the first exhaust port, thereby reducing the clearance volume during the compressor exhaust process, so that the gaseous refrigerant is more fully compressed, avoiding the problems of high energy consumption and low performance caused by the large clearance volume in the prior art.

[0006] This application provides a pump body structure, including:

[0007] A cylinder, wherein a hollow chamber is provided inside the cylinder, the cross-section of the hollow chamber is elliptical, and an intake port, a first exhaust port and a second exhaust port are provided in the hollow chamber. In the compression path of the hollow chamber, the second exhaust port is located behind the first exhaust port.

[0008] A crankshaft located inside the hollow cavity has a circular cross-section; the center of the crankshaft coincides with the center of the hollow cavity.

[0009] A sliding plate, one end of which is fixed to the side edge of the crankshaft, and the other end of which abuts against the inner wall of the hollow cavity.

[0010] Gaseous refrigerant enters the hollow chamber through the intake port. When the crankshaft drives the vane to rotate, the gaseous refrigerant inside the hollow chamber begins to be compressed. As the gaseous refrigerant is compressed, the vane first exhausts gas through the first exhaust port. After the first exhaust port is closed, the crankshaft continues to drive the vane to rotate to the second exhaust port for exhaust. Since the second exhaust port is located near the rear of the compression path of the first exhaust port, the clearance volume is reduced during the compressor's exhaust process, allowing the gaseous refrigerant to be compressed more fully. This avoids the problems of high energy consumption and low performance caused by the large clearance volume in the prior art.

[0011] Preferably, the crankshaft divides the hollow chamber into a first compression chamber and a second compression chamber; there are two vanes, and the two vanes are symmetrically distributed with respect to the center of the crankshaft.

[0012] In this application, the first and second compression chambers compress the gaseous refrigerant synchronously as the crankshaft rotates. Correspondingly, this application uses two vanes, symmetrically arranged with respect to the center of the crankshaft. In this way, because the first and second compression chambers are symmetrically structured, and the two vanes are also symmetrically structured, it can be ensured that the two vanes are located within the first and second compression chambers respectively, achieving synchronous compression of the two chambers. At the same time, the symmetrical arrangement of the two vanes avoids affecting the compressor's balancing torque, further ensuring the compressor's self-balance during rotation.

[0013] Preferably, there are two first exhaust ports, which are located in the first compression chamber and the second compression chamber respectively, and are symmetrically arranged with respect to the center of the hollow cavity.

[0014] There are two second exhaust ports, which are located in the first compression chamber and the second compression chamber respectively, and are symmetrically arranged with respect to the center of the hollow cavity.

[0015] In this application, both the first compression chamber and the second compression chamber are provided with an air intake, a first exhaust port, and a second exhaust port. In order to ensure the smooth compression of the first compression chamber and the second compression chamber, the air intake ports of the first compression chamber and the second compression chamber are symmetrically arranged with respect to the center of the hollow cavity, the first exhaust ports of the first compression chamber and the second compression chamber are symmetrically arranged with respect to the center of the hollow cavity, and the second exhaust ports of the first compression chamber and the second compression chamber are symmetrically arranged with respect to the center of the hollow cavity. In this way, it can not only ensure the synchronous and symmetrical compression path inside the first compression chamber and the second compression chamber, but also avoid affecting the compressor's balancing torque, and further ensure the self-balancing of the compressor during rotation.

[0016] Preferably, the outer diameter of the crankshaft is equal to the length of the short side of the ellipse of the hollow cavity; the second exhaust port is located on the side of the first exhaust port near the short side of the ellipse.

[0017] When the outer diameter of the crankshaft is equal to the length of the short side of the ellipse of the hollow chamber, the first compression chamber and the second compression chamber are symmetrically distributed on both sides of the crankshaft, and the positions of the intake port, the first exhaust port and the second exhaust port in the first compression chamber and the second compression chamber are symmetrical. Taking the first compression chamber as an example, the intake port is located at the beginning of the compression path of the first compression chamber, that is, near one of the short sides of the ellipse, and the second exhaust port is located at the end of the compression path of the first compression chamber, that is, near the other short side of the ellipse. Along the compression path, that is, along the sliding path of the vane, the first compression chamber contains the intake port, the first exhaust port and the second exhaust port in sequence. In this way, the gaseous refrigerant enters the first compression chamber through the intake port. The crankshaft drives the vane to slide, and the vane forms a sealed connection with the inner wall of the first compression chamber, compressing the gaseous refrigerant entering the first compression chamber. Along the compression path, the compressed gaseous refrigerant is output from the first exhaust port. When the vane passes the first exhaust port and is located between the first and second exhaust ports, the compressed gaseous refrigerant continues to be discharged through the second exhaust port, thereby reducing the clearance volume and improving the compressor efficiency.

[0018] Preferably, the crankshaft has a groove on its edge, and the sliding plate is disposed in the groove.

[0019] This application arranges a sliding groove within the crankshaft, with the sliding vane located inside the groove. The two grooves are symmetrically positioned with respect to the crankshaft's center, thus avoiding any impact on the compressor's balancing torque. The two symmetrical vanes simultaneously divide the hollow cavity into a symmetrical first and second compression chamber, enabling simultaneous intake and exhaust. The movement of the vane between the grooves is driven by the centrifugal force generated during crankshaft rotation. Specifically, the centrifugal force of the crankshaft rotation causes the vane to move radially within the groove, ensuring that the vane can contact the inner wall of the hollow cavity at different locations to compress the gaseous refrigerant within the compression chamber.

[0020] Preferably, a spring is provided inside the slide groove, and the two ends of the spring are fixedly connected to the inner sidewall of the slide groove and the slide plate, respectively.

[0021] As an alternative embodiment, this application incorporates a spring within the slide groove. The spring facilitates the contact between the sliding plate and the side wall of the slide groove, preventing rigid collisions between the slide groove and the sliding plate that could cause wear and affect the compressor's service life. In this application, the driving force for the sliding plate to slide within the slide groove is primarily the centrifugal force of the crankshaft, supplemented by the spring's compressive force, ensuring smooth sliding of the sliding plate within the slide groove.

[0022] Preferably, a first exhaust valve is provided at the first exhaust port, and a second exhaust valve is provided at the second exhaust port; within the same compression chamber, the closing time of the second exhaust valve is later than the closing time of the first exhaust valve.

[0023] In this application, the first exhaust valve can be opened first for exhaust, followed by the second exhaust valve, or the first and second exhaust valves can be opened simultaneously. It should be noted that the closing time of the second exhaust valve in this application must be later than the closing time of the first exhaust valve; that is, when the slide plate passes the position of the first exhaust port, the second exhaust valve is still open, to compensate for the large clearance volume of the elliptical cylinder pump body structure.

[0024] Preferably, the diameter of the second exhaust port is smaller than the diameter of the first exhaust port.

[0025] In this application, the distance between the first exhaust port and the second exhaust port is small. The first exhaust port is the main exhaust port, and the second exhaust port is an auxiliary exhaust port, which is only used to eliminate the clearance volume of the elliptical compression chamber. Therefore, this application can set the aperture of the second exhaust port to be smaller than the aperture of the first exhaust port, thereby further reducing the large space at the end of the exhaust process due to the contact between the elliptical cylinder and the sliding crankshaft, reducing the clearance volume, and solving the problem that the clearance volume of the elliptical structure is larger than that of the traditional compressor.

[0026] The second objective of this application is to provide a compressor, including the pump body structure described above. This application employs a cylinder with an elliptical inner diameter and a standard circular crankshaft without eccentricity, eliminating the influence of the eccentricity on the compressor's torque balance and achieving self-balancing during compressor rotation. Simultaneously, because the second exhaust port is closer to the minor axis of the elliptical cavity, the large space at the end of the exhaust process due to the contact between the elliptical cylinder and the sliding crankshaft is further reduced, decreasing the clearance volume and solving the problem of large clearance volume in elliptical compressor structures.

[0027] The second objective of this application is to provide an air conditioner, including a compressor as described above; ensuring that the gaseous refrigerant in the cylinder is fully compressed, reducing the clearance volume of the compressor, and having advantages such as low wear, long service life, low energy consumption, and high performance.

[0028] The beneficial effects of this utility model are as follows:

[0029] This utility model provides a pump body structure including a cylinder, a crankshaft, and a vane. The cylinder has a hollow chamber with an elliptical cross-section. The hollow chamber contains an intake port, a first exhaust port, and a second exhaust port. In the compression path of the hollow chamber, the second exhaust port is located behind the first exhaust port. The crankshaft is located inside the hollow chamber and has a circular cross-section. The center of the crankshaft coincides with the center of the hollow chamber. One end of the vane is fixed to the side edge of the crankshaft, and the other end of the vane abuts against the inner wall of the hollow chamber. Gaseous refrigerant enters the hollow chamber through the intake port. When the crankshaft drives the vane to rotate, the gaseous refrigerant inside the hollow chamber begins to be compressed. As the gaseous refrigerant is compressed, the vane first exhausts gas through the first exhaust port. After the first exhaust port is closed, the crankshaft continues to drive the vane to rotate to the second exhaust port for exhaust. Since the second exhaust port is located near the rear of the compression path of the first exhaust port, the clearance volume is reduced during the compressor's exhaust process, allowing the gaseous refrigerant to be compressed more fully. This avoids the problems of high energy consumption and low performance caused by the large clearance volume in the prior art.

[0030] This application also provides a compressor, including the pump body structure described above. This application uses a cylinder with an elliptical inner diameter and a standard circular crankshaft without eccentricity, which eliminates the influence of the eccentricity on the torque balance of the compressor and achieves self-balancing when the compressor rotates. At the same time, since the second exhaust port is closer to the minor axis of the ellipse of the hollow chamber, the large space due to the contact between the elliptical cylinder and the sliding crankshaft at the end of the exhaust process is further reduced during the compressor exhaust process, thereby reducing the clearance volume and solving the problem of large clearance volume in elliptical structure compressors.

[0031] This application also provides an air conditioner, including the compressor described above, which ensures that the gaseous refrigerant in the cylinder is fully compressed, reduces the clearance volume of the compressor, and has advantages such as low wear, long service life, low energy consumption, and high performance. Attached Figure Description

[0032] Figure 1 This is a schematic diagram of the pump body structure in the intake start position in an embodiment of this application;

[0033] Figure 2 This is a schematic diagram of the pump body structure in the compression start position in an embodiment of this application;

[0034] Figure 3 This is a schematic diagram of the pump body structure in the compression and exhaust process in the embodiment of this application;

[0035] Figure 4 This is a schematic diagram of the pump body structure in the exhaust end position in the embodiment of this application;

[0036] Figure 5 This is a schematic diagram of the structure of the spring inside the groove in the embodiment of this application;

[0037] Figure 6 This is a top view of the pump body structure in an embodiment of this application;

[0038] Figure 7 This is a cross-sectional schematic diagram of the pump body structure in an embodiment of this application.

[0039] Figure label:

[0040] 1. Cylinder; 11. First compression chamber; 12. Second compression chamber; 2. Crankshaft; 3. Sliding vane; 4. Intake port; 5. Second exhaust port; 6. Upper flange; 7. Lower flange; 8. Spring; 9. First exhaust port. Detailed Implementation

[0041] Preferred embodiments of the present invention will now be described in more detail with reference to the accompanying drawings. While preferred embodiments of the present invention are shown in the drawings, it should be understood that the present invention may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that the present invention will be thorough and complete, and will fully convey the scope of the present invention to those skilled in the art.

[0042] The terminology used in this invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The singular forms “a,” “the,” and “the” used in this invention and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise. It should also be understood that the term “and / or” as used herein refers to and includes any or all possible combinations of one or more of the associated listed items.

[0043] It should be understood that although the terms "first," "second," "third," etc., may be used in this invention to describe various information, this information should not be limited to these terms. These terms are only used to distinguish information of the same type from one another. For example, without departing from the scope of this invention, first information may also be referred to as second information, and similarly, second information may also be referred to as first information. Thus, features defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0044] Example 1

[0045] like Figures 1-7 As shown, the pump body structure provided in this application includes:

[0046] Cylinder 1, the cylinder 1 has a hollow chamber inside, the cross-section of the hollow chamber is elliptical, the hollow chamber has an intake port 4, a first exhaust port 9 and a second exhaust port 5, and in the compression path of the hollow chamber, the second exhaust port 5 is located behind the first exhaust port 9.

[0047] A crankshaft 2 is located inside the hollow cavity, and the cross-section of the crankshaft 2 is circular; the center of the crankshaft 2 coincides with the center of the hollow cavity.

[0048] Sliding vane 3, one end of which is fixed to the side edge of the crankshaft 2, and the other end of which abuts against the inner wall of the hollow cavity.

[0049] In this application, gaseous refrigerant enters the hollow cavity through the intake port 4. When the crankshaft 2 drives the vane 3 to rotate, the gaseous refrigerant inside the hollow cavity begins to be compressed. As the gaseous refrigerant is compressed, the vane 3 first exhausts through the first exhaust port 9. After the first exhaust port 9 is closed, the crankshaft 2 continues to drive the vane 3 to rotate to the second exhaust port 5 for exhaust. Since the second exhaust port 5 is located near the rear side of the compression path of the first exhaust port 9, the clearance volume is reduced during the compressor exhaust process, allowing the gaseous refrigerant to be compressed more fully. This avoids the problems of high energy consumption and low performance caused by the large clearance volume in the prior art.

[0050] In the traditional rotary compressor pump body structure, the eccentric circle and rollers of the crankshaft 2 are the main causes of unbalanced torque. To solve the unbalanced torque during compressor rotation, a balance block is needed to balance the torque. However, the balance block cannot completely eliminate the unbalanced torque caused by the compressor and may cause problems such as compressor vibration and crankshaft 2 wear. In this application, the crankshaft 2 is a standard circular crankshaft 2 without an eccentric circle. Since the design of the eccentric circle of the crankshaft 2 is eliminated, the influence of the eccentric circle on the torque balance of the compressor is eliminated, thus eliminating the need for a balance block and achieving self-balancing during compressor rotation.

[0051] In this application, crankshaft 2 is connected to a motor. While the motor drives crankshaft 2 to rotate, crankshaft 2 also drives sliding vane 3 to rotate synchronously. The other side of sliding vane 3 abuts against the hollow cavity. During the sliding process of sliding vane 3, the gaseous refrigerant inside the hollow cavity is compressed. When the gaseous refrigerant inside the hollow cavity is compressed to a certain pressure, the exhaust port opens to exhaust the gas. With the reciprocating rotation of crankshaft 2, a cycle of gaseous refrigerant intake-compression-exhaust is achieved inside the hollow cavity.

[0052] In this application, there are two exhaust ports. In the compression path of the hollow cavity, the second exhaust port 5 is located behind the first exhaust port 9. This is because during the compression process of the gaseous refrigerant, if only the first exhaust port 9 is used, the compressed gaseous refrigerant will first be discharged through the first exhaust port 9. However, in the space after the first exhaust port 9, the compressed gaseous refrigerant cannot be discharged, causing gaseous refrigerant to stagnate. This results in a larger clearance volume in the compressor, thus affecting the compressor efficiency. This application adds a second exhaust port 5, which ensures that after the first exhaust port 9 is closed, the compressed gaseous refrigerant inside the hollow cavity continues to be discharged from the second exhaust port 5, thereby reducing the clearance volume and improving the compressor efficiency.

[0053] Example 2

[0054] like Figures 1-7 As shown, the pump body structure provided in this application includes:

[0055] Cylinder 1, the cylinder 1 has a hollow chamber inside, the cross-section of the hollow chamber is elliptical, the hollow chamber has an intake port 4, a first exhaust port 9 and a second exhaust port 5, and in the compression path of the hollow chamber, the second exhaust port 5 is located behind the first exhaust port 9.

[0056] A crankshaft 2 is located inside the hollow cavity, and the cross-section of the crankshaft 2 is circular; the center of the crankshaft 2 coincides with the center of the hollow cavity.

[0057] Sliding vane 3, one end of which is fixed to the side edge of the crankshaft 2, and the other end of which abuts against the inner wall of the hollow cavity.

[0058] Furthermore, in this application, the crankshaft 2 divides the hollow cavity into a first compression chamber 11 and a second compression chamber 12; there are two sliding vanes 3, and the two sliding vanes 3 are symmetrically distributed with respect to the center of the crankshaft 2.

[0059] In this application, the outer diameter of the crankshaft 2 is equal to the length of the short side of the ellipse of the hollow cavity. When the crankshaft 2 is assembled inside the hollow cavity, since the outer diameter of the crankshaft 2 is equal to the length of the short side of the ellipse of the hollow cavity, the crankshaft 2 divides the elliptical hollow cavity into two symmetrical first compression chambers 11 and second compression chambers 12. In this application, the first compression chambers 11 and second compression chambers 12 compress the gaseous refrigerant synchronously with the rotation of the crankshaft 2. Correspondingly, in this application, there are two vanes 3, which are symmetrically arranged with respect to the center of the crankshaft 2. In this way, since the first compression chambers 11 and second compression chambers 12 are symmetrical, and the two vanes 3 are also symmetrical, it can be ensured that the two vanes 3 are located in the first compression chamber 11 and the second compression chamber 12 respectively, achieving synchronous compression of the two compression chambers. At the same time, since the two vanes 3 are symmetrically arranged, it avoids affecting the compressor's balancing torque, further ensuring the self-balancing of the compressor during rotation.

[0060] Furthermore, there are two first exhaust ports 9, which are located in the first compression chamber 11 and the second compression chamber 12 respectively, and are symmetrically arranged with respect to the center of the hollow cavity.

[0061] There are two second exhaust ports 5, which are located in the first compression chamber 11 and the second compression chamber 12 respectively, and are symmetrically arranged with respect to the center of the hollow cavity.

[0062] In this application, both the first compression chamber 11 and the second compression chamber 12 are provided with an air intake 4, a first exhaust port 9, and a second exhaust port 5. In order to ensure the smooth compression of the first compression chamber 11 and the second compression chamber 12, the air intake 4 in the first compression chamber 11 and the second compression chamber 12 are symmetrically arranged with respect to the center of the hollow chamber, the first exhaust port 9 in the first compression chamber 11 and the second compression chamber 12 are symmetrically arranged with respect to the center of the hollow chamber, and the second exhaust port 5 in the first compression chamber 11 and the second compression chamber 12 are symmetrically arranged with respect to the center of the hollow chamber. In this way, it can not only ensure the synchronous and symmetrical operation of the compression path inside the first compression chamber 11 and the second compression chamber 12, but also avoid affecting the balance torque of the compressor, and further ensure the self-balance of the compressor when it rotates.

[0063] Furthermore, the outer diameter of the crankshaft 2 is equal to the length of the short side of the ellipse of the hollow cavity; the second exhaust port 5 is located on the side of the first exhaust port 9 near the short side of the ellipse.

[0064] When the outer diameter of crankshaft 2 is equal to the length of the short side of the ellipse of the hollow cavity, the first compression chamber 11 and the second compression chamber 12 are symmetrically distributed on both sides of crankshaft 2, and the positions of the intake port 4, the first exhaust port 9, and the second exhaust port 5 in the first compression chamber 11 and the second compression chamber 12 are symmetrical. Taking the first compression chamber 11 as an example, the intake port 4 is located at the beginning of the compression path of the first compression chamber 11, that is, close to one of the short sides of the ellipse. The second exhaust port 5 is located at the end of the compression path of the first compression chamber 11, that is, close to the other short side of the ellipse. Along the compression path, that is, along the sliding path of the slider 3, the first compression chamber 11 contains the intake port 4, the first exhaust port 9, and the second exhaust port 5 in sequence. In this way, the gaseous refrigerant enters the first compression chamber 11 through the intake port 4. The crankshaft 2 drives the vane 3 to slide, and the vane 3 forms a sealed connection with the inner wall of the first compression chamber 11, compressing the gaseous refrigerant entering the first compression chamber 11. Along the compression path, the compressed gaseous refrigerant is output from the first exhaust port 9. When the vane 3 passes the first exhaust port 9 and is located between the first exhaust port 9 and the second exhaust port 5, the compressed gaseous refrigerant continues to be discharged through the second exhaust port 5, thereby reducing the clearance volume and improving the compressor efficiency.

[0065] The second compression chamber 12 is completely symmetrical to the first compression chamber 11, and the intake and exhaust paths are similar to those of the first compression chamber 11.

[0066] Furthermore, the crankshaft 2 has a groove on its edge, and the slide 3 is disposed in the groove.

[0067] In this application, a sliding groove is disposed within the crankshaft 2, and a sliding vane 3 is located inside the sliding groove. The two sliding grooves are symmetrically arranged with respect to the center of the crankshaft 2, thereby avoiding any impact on the compressor's balancing torque. The two symmetrical sliding vanes 3 simultaneously divide the hollow chamber into a symmetrical first compression chamber 11 and a second compression chamber 12, enabling simultaneous intake and exhaust. In this application, the movement of the sliding vane 3 between the sliding grooves is driven by the centrifugal force generated when the crankshaft 2 rotates. That is, the centrifugal force of the crankshaft 2 rotation drives the sliding vane 3 to move along the radial direction of the crankshaft 2 within the sliding groove, ensuring that the sliding vane 3 can abut against the inner wall of the hollow chamber at different positions to compress the gaseous refrigerant in the compression chamber.

[0068] Furthermore, a spring 8 is provided inside the slide groove, and the two ends of the spring 8 are fixedly connected to the inner sidewall of the slide groove and the slide plate 3, respectively.

[0069] As an alternative embodiment, this application provides a spring 8 within the slide groove. The spring 8 facilitates the contact between the sliding plate 3 and the side wall of the slide groove, preventing rigid collisions between the slide groove and the sliding plate 3 that could cause wear and affect the compressor's service life. In this application, the driving force for the sliding plate 3 to slide within the slide groove is primarily the centrifugal force of the crankshaft 2, supplemented by the compressive force of the spring 8, ensuring smooth sliding of the sliding plate 3 within the slide groove.

[0070] Furthermore, a first exhaust valve is provided at the first exhaust port 9, and a second exhaust valve is provided at the second exhaust port 5; within the same compression chamber, the closing time of the second exhaust valve is later than the closing time of the first exhaust valve.

[0071] The first exhaust valve covers the exhaust channel outlet corresponding to the first exhaust port 9, and the second exhaust valve covers the exhaust channel outlet corresponding to the second exhaust port 5. When the pressure inside the compression chamber reaches the opening pressure of the first exhaust valve, the first exhaust valve opens, and the compressed refrigerant inside the compression chamber is discharged through the first exhaust port 9. When the pressure inside the compression chamber reaches the opening pressure of the second exhaust valve, the second exhaust valve opens, and the compressed refrigerant inside the compression chamber is discharged through the second exhaust port 5.

[0072] In this application, the first exhaust valve can be opened first for exhaust, followed by the second exhaust valve, or the first and second exhaust valves can be opened simultaneously. It should be noted that the closing time of the second exhaust valve in this application must be later than the closing time of the first exhaust valve; that is, when the slide plate 3 passes the position of the first exhaust port 9, the second exhaust valve is still open to compensate for the large clearance volume of the pump body structure of the elliptical cylinder 1.

[0073] This application can ensure that the second exhaust valve closes later than the first exhaust valve by designing parameters such as the width and thickness of the first and second exhaust valves. Specifically, the width of the second exhaust valve can be set to be greater than that of the first exhaust valve, resulting in greater inertia and delayed closure; or the thickness of the second exhaust valve can be set to be greater than that of the first exhaust valve, resulting in greater elasticity and delayed closure. Alternatively, both the width and thickness of the second exhaust valve can be set to be greater than those of the first exhaust valve to achieve delayed closure.

[0074] Furthermore, the diameter of the second exhaust port 5 is smaller than the diameter of the first exhaust port 9.

[0075] In this application, the distance between the first exhaust port 9 and the second exhaust port 5 is small. The first exhaust port 9 is the main exhaust port, and the second exhaust port 5 is an auxiliary exhaust port, which is only used to eliminate the clearance volume of the elliptical compression chamber. Therefore, this application can set the aperture of the second exhaust port 5 to be smaller than the aperture of the first exhaust port 9, thereby further reducing the large space at the end of the exhaust process due to the contact between the elliptical cylinder 1 and the crankshaft 2 of the vane 3, reducing the clearance volume, and solving the problem that the clearance volume of the elliptical structure is larger than that of the traditional compressor.

[0076] Example 3

[0077] like Figures 1-7 As shown, this application provides a pump body structure including a cylinder 1 and a crankshaft 2. The cylinder 1 has a hollow chamber with an elliptical cross-section. The crankshaft 2, located inside the hollow chamber, has a circular cross-section. The center of the crankshaft 2 coincides with the center of the hollow chamber. The outer diameter of the crankshaft 2 is equal to the length of the shorter side of the ellipse of the hollow chamber. When the crankshaft 2 is assembled inside the hollow chamber, since its outer diameter is equal to the length of the shorter side of the ellipse, the crankshaft 2 divides the elliptical hollow chamber into two symmetrical compression chambers: a first compression chamber 11 and a second compression chamber 12. One end of a sliding vane 3 is fixed to the side edge of the crankshaft 2, and the other end of the sliding vane 3 abuts against the inner wall of the hollow chamber. There are two sliding vanes 3, and the two sliding vanes 3 are symmetrically distributed with respect to the center of the crankshaft 2.

[0078] The upper end of cylinder 1 is fixed inside the compressor via the upper flange 6, and the lower end of cylinder 1 is fixed inside the compressor via the lower flange 7. Cylinder 1 is fixed by the upper flange 6 and the lower flange 7.

[0079] This application incorporates a spring 8 within the slide groove. The spring 8 facilitates the contact between the sliding vane 3 and the side wall of the slide groove, preventing rigid collisions between the slide groove and the sliding vane 3 that could cause wear and affect the compressor's service life. In this application, the driving force for the sliding vane 3 to slide within the slide groove is primarily the centrifugal force of the crankshaft 2, supplemented by the compressive force of the spring 8, ensuring smooth sliding of the sliding vane 3 within the slide groove.

[0080] The first compression chamber 11 and the second compression chamber 12 are symmetrically structured, and the two sliding vanes 3 are also symmetrically structured, ensuring that the two sliding vanes 3 are located in the first compression chamber 11 and the second compression chamber 12 respectively, thus achieving synchronous compression of the two compression chambers. Simultaneously, in this application, the intake ports 4 in the first compression chamber 11 and the second compression chamber 12 are symmetrically arranged with respect to the center of the hollow chamber; the first exhaust ports 9 in the first compression chamber 11 and the second compression chamber 12 are symmetrically arranged with respect to the center of the hollow chamber; the second exhaust ports 5 in the first compression chamber 11 and the second compression chamber 12 are symmetrically arranged with respect to the center of the hollow chamber; and the two sliding vanes 3 are symmetrically arranged with respect to the center of the hollow chamber. This ensures the synchronous and symmetrical compression paths within the first compression chamber 11 and the second compression chamber 12, avoids affecting the compressor's balancing torque, and further ensures the compressor's self-balancing during rotation.

[0081] In this application, the distance between the first exhaust port 9 and the second exhaust port 5 is small. The first exhaust port 9 is the main exhaust port, and the second exhaust port 5 is an auxiliary exhaust port, which is only used to eliminate the clearance volume of the elliptical compression chamber. Therefore, this application can set the aperture of the second exhaust port 5 to be smaller than the aperture of the first exhaust port 9, thereby further reducing the large space at the end of the exhaust process due to the contact between the elliptical cylinder and the vane and crankshaft, reducing the clearance volume, and solving the problem that the clearance volume of the elliptical structure is larger than that of the traditional compressor.

[0082] The first exhaust valve covers the exhaust channel outlet corresponding to the first exhaust port 9, and the second exhaust valve covers the exhaust channel outlet corresponding to the second exhaust port 5. When the pressure inside the compression chamber reaches the opening pressure of the first exhaust valve, the first exhaust valve opens, and the compressed refrigerant inside the compression chamber is discharged through the first exhaust port 9. When the pressure inside the compression chamber reaches the opening pressure of the second exhaust valve, the second exhaust valve opens, and the compressed refrigerant inside the compression chamber is discharged through the second exhaust port 5.

[0083] In this application, the first exhaust valve can open first to exhaust air, followed by the second exhaust valve, or both can open simultaneously. It is important to note that the closing time of the second exhaust valve must be later than that of the first exhaust valve; that is, when the slide plate 3 passes the position of the first exhaust port 9, the second exhaust valve is still open. This compensates for the large clearance volume of the elliptical cylinder 1 pump body structure. This application can ensure that the second exhaust valve closes later than the first exhaust valve by designing parameters such as the width and thickness of the first and second exhaust valves.

[0084] The intake port 4 is located at the beginning of the compression path of the first compression chamber 11, near one of the shorter sides of the ellipse. The second exhaust port 5 is located at the end of the compression path of the first compression chamber 11, near the other shorter side of the ellipse. Along the compression path, i.e., along the sliding path of the vane 3, the first compression chamber 11 contains the intake port 4, the first exhaust port 9, and the second exhaust port 5 in sequence. In this way, gaseous refrigerant enters the first compression chamber 11 through the intake port 4. The crankshaft 2 drives the vane 3 to slide, forming a sealed connection between the vane 3 and the inner wall of the first compression chamber 11, compressing the gaseous refrigerant entering the first compression chamber 11. Along the compression path, the compressed gaseous refrigerant is output from the first exhaust port 9. After the vane 3 passes the first exhaust port 9, i.e., when it is between the first exhaust port 9 and the second exhaust port 5, the compressed gaseous refrigerant continues to be discharged through the second exhaust port 5, thereby reducing the clearance volume and improving the compressor efficiency. The second compression chamber 12 is completely symmetrical to the first compression chamber 11, and the intake and exhaust paths are similar to those of the first compression chamber 11.

[0085] This application also provides a compressor, including the pump body structure described above. This application uses a cylinder with an elliptical inner diameter and a standard circular crankshaft without eccentricity, which eliminates the influence of the eccentricity on the torque balance of the compressor and achieves self-balancing when the compressor rotates. At the same time, since the second exhaust port is closer to the minor axis of the ellipse of the hollow chamber, the large space due to the contact between the elliptical cylinder and the sliding crankshaft at the end of the exhaust process is further reduced during the compressor exhaust process, thereby reducing the clearance volume and solving the problem of large clearance volume in elliptical structure compressors.

[0086] This application also provides an air conditioner, including the compressor described above, which ensures that the gaseous refrigerant in the cylinder is fully compressed, reduces the clearance volume of the compressor, and has advantages such as low wear, long service life, low energy consumption, and high performance.

[0087] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings. In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0088] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0089] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0090] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A pump body structure, characterized in that, include: Cylinder (1), the cylinder (1) has a hollow chamber inside, the cross-section of the hollow chamber is elliptical, the hollow chamber has an air intake (4), a first exhaust port (9) and a second exhaust port (5), in the compression path of the hollow chamber, the second exhaust port (5) is located behind the first exhaust port (9); A crankshaft (2) is located inside the hollow cavity, and the cross-section of the crankshaft (2) is circular; the center of the crankshaft (2) overlaps with the center of the hollow cavity. Sliding plate (3), one end of which is fixed to the side edge of the crankshaft (2), and the other end of which abuts against the inner wall of the hollow cavity.

2. The pump body structure according to claim 1, characterized in that, The crankshaft (2) divides the hollow chamber into a first compression chamber (11) and a second compression chamber (12); there are two slides (3), and the two slides (3) are symmetrically distributed with respect to the center of the crankshaft (2).

3. The pump body structure according to claim 2, characterized in that, There are two first exhaust ports (9), which are located in the first compression chamber (11) and the second compression chamber (12) respectively, and are symmetrically arranged with respect to the center of the hollow cavity. There are two second exhaust ports (5), which are located in the first compression chamber (11) and the second compression chamber (12) respectively, and are symmetrically arranged with respect to the center of the hollow cavity.

4. The pump body structure according to claim 2, characterized in that, The outer diameter of the crankshaft (2) is equal to the length of the short side of the ellipse of the hollow cavity; the second exhaust port (5) is located on the side of the first exhaust port (9) near the short side of the ellipse.

5. The pump body structure according to claim 1, characterized in that, The crankshaft (2) has a groove on its edge, and the slide (3) is disposed in the groove.

6. The pump body structure according to claim 5, characterized in that, A spring (8) is provided inside the slide groove, and the two ends of the spring (8) are fixedly connected to the inner sidewall of the slide groove and the slide plate (3), respectively.

7. The pump body structure according to claim 1, characterized in that, A first exhaust valve is provided at the first exhaust port (9), and a second exhaust valve is provided at the second exhaust port (5); in the same compression chamber, the closing time of the second exhaust valve is later than the closing time of the first exhaust valve.

8. The pump body structure according to claim 1, characterized in that, The diameter of the second exhaust port (5) is smaller than the diameter of the first exhaust port (9).

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

10. An air conditioner, characterized in that, Includes a compressor as described in claim 9.

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