A rotary vane type automotive air conditioning compressor cylinder block

Abstract

This utility model relates to the field of compressor cylinder technology, and more particularly to a rotary vane automotive air conditioning compressor cylinder. The cylinder has a first bearing mounted at one end and a second bearing mounted at the other end. It includes: a cylinder body with a centrally located compression chamber; a through-flow intake channel along the length of the cylinder body; an exhaust port along the circumference of the cylinder body, connecting the compression chamber and the outside of the cylinder body; and a stepped opening on the end face of the cylinder body corresponding to the intake channel, located on the side of the intake channel closest to the compression chamber, connecting the intake channel and the compression chamber. This utility model, by employing an elliptical intake channel and adding stepped openings at both ends of the intake channel, expands the gas entry path, thereby increasing gas flow and improving the compressor's intake performance.

Description

Technical Field

[0001] This utility model relates to the field of compressor cylinder technology, and in particular to a rotary vane automotive air conditioning compressor cylinder. Background Technology

[0002] As a third-generation automotive air conditioning compressor, the rotary vane compressor boasts advantages such as small size, high speed, low energy consumption, and low noise. Its core structure includes a compression chamber composed of a front bearing, a cylinder, and a rear bearing. In existing technologies, the cylinder of a rotary vane compressor typically has two through-flow intake channels along its length. Part of the refrigerant enters the compression chamber through the front bearing (first bearing), while the other part enters the cylinder's intake channel from the front bearing and then enters the compression chamber through the rear bearing (second bearing). After being compressed by the rotor shaft driving the vanes to rotate, the refrigerant is discharged from the exhaust port in the middle of the cylinder. Traditional intake channels are mostly circular, which is simple to manufacture and low in cost, making them suitable for small to medium displacement and conventional speed conditions.

[0003] However, existing technologies have obvious limitations. The radial cross-sectional area of ​​the circular suction channel is small. When the compressor is used in large displacement or high speed conditions, the flow capacity of the suction channel is insufficient, resulting in a reduction in refrigerant intake and a significant decrease in volumetric efficiency. In addition, there is no direct connection between the traditional suction channel and the compression chamber. The refrigerant can only enter through the first and second bearings, which limits the expansion of rotary vane compressors to larger displacement and higher speed scenarios.

[0004] Therefore, a compressor cylinder with an optimized internal gas passage layout is needed to improve refrigerant intake and volumetric efficiency. Utility Model Content

[0005] In view of at least one of the above technical problems, the present invention provides a rotary vane automotive air conditioning compressor cylinder block, which adopts an elliptical radial cross-section intake channel and a stepped opening structure, so that the intake channel is directly connected to the compression chamber, thereby expanding the passage area for refrigerant to enter the compression chamber and improving the volumetric efficiency under large displacement and high speed conditions.

[0006] This utility model provides a rotary vane automotive air conditioning compressor cylinder block, with a first bearing installed at one end and a second bearing installed at the other end, comprising: The cylinder has a compression chamber at its center and a through intake channel along its length; the cylinder also has an exhaust port along its circumference, which connects the compression chamber to the outside of the cylinder. The cylinder body has a stepped opening on its end face corresponding to the air intake channel. The stepped opening is located on the side of the air intake channel close to the compression chamber, and the stepped opening connects the air intake channel and the compression chamber.

[0007] In some embodiments of this utility model, the air intake channel has an elliptical cross-section along the radial direction.

[0008] In some embodiments of this utility model, the stepped opening is flared, and the opening width on the side of the stepped opening near the compression chamber is greater than the opening width on the side near the suction channel.

[0009] In some embodiments of this utility model, at least one vent is provided in the air intake channel, and the vent connects the air intake channel and the compression chamber.

[0010] In some embodiments of this utility model, the axis of the vent hole is inclined relative to the end face of the cylinder.

[0011] In some embodiments of this utility model, a transition port is provided at the contact point between the exhaust port and the inner wall of the cylinder, and the transition port extends along the exhaust port in an arc-shaped flare to the inner wall of the cylinder.

[0012] In some embodiments of this utility model, a stable section extends outward in the circumferential direction from one end face of the cylinder body.

[0013] In some embodiments of this utility model, a plurality of spaced connecting holes are provided on the two end faces of the cylinder body.

[0014] In some embodiments of this utility model, the cylinder body includes a valve face, and a plurality of spaced fixing holes are formed on the valve face.

[0015] In some embodiments of this utility model, the cylinder body has oil holes extending from one end face to the other end face along its length.

[0016] The beneficial effects of this utility model are as follows: By adopting an elliptical radial cross-section suction channel, the area of ​​the suction port is increased. The stepped opening structure, in conjunction with this, allows the refrigerant to enter the compression chamber not only through the bearing but also through the suction passage, increasing the gas passage area, effectively improving the suction volume, and enhancing the volumetric efficiency of the compressor under large displacement and high speed conditions. By adding an inclined vent hole in the middle of the suction channel, the airflow distribution is optimized, allowing the refrigerant to enter the compression chamber from multiple points, thus improving the stability of the refrigerant supply during compression. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this utility model 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 recorded in this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the working process of the rotary vane automotive air conditioning compressor cylinder block after the first and second bearings are installed in the embodiment of this utility model. Figure 2 This is a schematic diagram of the cylinder block of the rotary vane automotive air conditioning compressor in an embodiment of this utility model; Figure 3 This is a top view of the cylinder body in an embodiment of the present invention; Figure 4 As an embodiment of this utility model Figure 3 Schematic diagram of the cross-sectional structure at point AA; Figure 5 This is a schematic diagram showing the bottom view of the cylinder in an embodiment of this utility model.

[0019] Reference numerals: 1. Cylinder block; 11. Compression chamber; 12. Intake passage; 121. Exhaust port; 122. Vent hole; 13. Step opening; 14. Transition port; 15. Stabilizing section; 16. Connecting hole; 17. Valve face; 18. Fixing hole; 19. Oil hole; 2. First bearing; 3. Second bearing. Detailed Implementation

[0020] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present utility model. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments.

[0021] It should be noted that when an element is referred to as being "fixed to" another element, it can be directly attached to the other element or there may be an intervening element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0022] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0023] This utility model provides a method such as Figures 1 to 5 The rotary vane type automotive air conditioning compressor cylinder shown has a first bearing 2 (front bearing) installed at one end and a second bearing 3 (rear bearing) installed at the other end, including: The cylinder body 1 has a compression chamber 11 in the center and a through intake channel 12 along its length. Multiple intake channels 12 can be provided and distributed around the cylinder body to meet the intake volume required by different operating environments. The cylinder body 1 also has an exhaust port 121 around its circumference, which connects the compression chamber 11 and the outside of the cylinder body 1. The cylinder body 1 has a stepped opening 13 on its end face corresponding to the intake channel 12. The stepped opening 13 is located on the side of the intake channel 12 that is close to the compression chamber 11. The stepped opening 13 connects the intake channel 12 and the compression chamber 11. Preferably, the stepped opening 13 is opened on both end faces of the cylinder body 1 to correspond to the intake channel 12, so that the fluid flow area can be expanded from both ends, and the effect is better.

[0024] Based on the above embodiment, the intake channel 12 has an elliptical cross-section along the radial direction.

[0025] The working principle of this utility model is as follows: In an automotive air conditioner, the refrigerant is divided into two paths at the inlet of the first bearing 2. One path enters the compression chamber 11 directly through the cylinder block 1 at the inlet where the first bearing 2 is installed. The other path passes through the entire intake passage 12 and reaches the recess on the end face of the cylinder block 1 where the second bearing 3 is installed, entering the compression chamber 11. Inside the compression chamber 11, located in the center of the cylinder block 1, the rotor shaft drives the blades to rotate, compressing the incoming refrigerant. The compressed refrigerant is then discharged through the exhaust port 121 on the inner wall of the cylinder block 1. While the traditional cylinder block 1 has a circular intake port, which is simple to manufacture, it has drawbacks under high displacement or high speed conditions. The problem of insufficient cross-sectional area of ​​the intake passage leads to limited intake volume and decreased volumetric efficiency. In this embodiment, the radial cross-section of the intake passage 12 is designed as an ellipse, which increases the space for refrigerant flow. When the refrigerant enters the intake passage 12, the flow rate can also be increased. Furthermore, a stepped opening 13 is added to the side of the intake passage 12 at both ends that is close to the compression chamber 11, so that the refrigerant can directly enter the compression chamber 11 from the intake passage 12 of the cylinder 1. This expands the passage area for the refrigerant to enter the compression chamber 11, effectively improving the intake efficiency and volumetric efficiency without changing the compressor volume.

[0026] In some embodiments of this utility model, the stepped design at the intake of the cylinder 1 results in different performance improvements for compressors with different displacements and speeds. For compressors with a displacement of less than 96cc, the design of the intake channel 12 combined with the stepped opening 13 can slightly improve performance when the compressor speed is below 2000rpm; and moderately improve performance when the speed is above 2000rpm. For compressors with a displacement of more than 96cc, the design of the intake channel 12 combined with the stepped opening 13 can moderately improve performance when the compressor speed is below 2000rpm; and significantly improve performance when the speed is above 2000rpm. This further proves that the design of the elliptical intake channel 12 and the stepped opening 13 increases the passage area for refrigerant to enter the compression chamber 11.

[0027] In some embodiments of this utility model, such as Figure 2 and Figure 3 As shown, the stepped opening 13 is flared, and the opening width of the stepped opening 13 on the side near the compression chamber 11 is greater than the opening width on the side near the suction channel 12; forming a gradual transition structure from the suction channel 12 to the compression chamber 11. When the refrigerant enters the compression chamber 11 directly from the stepped opening 13 on the side of the first bearing 2 or through the elliptical suction channel 12 from the stepped opening 13 on the side of the second bearing 3, the flared design of the stepped opening 13 directly increases the passage area for the refrigerant to enter the compression chamber 11. Moreover, the gradual width of the flared opening can also buffer and guide the airflow, avoiding eddy current loss caused by abrupt changes in the channel during high-speed flow of the refrigerant. Combined with the basic cross-sectional area advantage of the elliptical suction channel 12, it together achieves efficient and stable entry of the refrigerant into the compression chamber 11 from both ends.

[0028] In some embodiments of this utility model, such as Figure 2 and Figure 4 As shown, at least one vent 122 is provided in the air intake channel 12, and the vent 122 connects the air intake channel 12 and the compression chamber 11.

[0029] Based on the above embodiments, such as Figure 4 As shown, the axis of the vent hole 122 is inclined relative to the end face of the cylinder block 1, with the optimal inclination angle being 45 degrees. The inclined vent hole 122 is also easy to process.

[0030] The vent 122 expands the single path of refrigerant entering the compression chamber 11 from the stepped openings 13 on both sides into a dual path from the intake channel 12 into the compression chamber 11. The inclined axis guides the airflow to enter in a tangential direction that is closer to the inner wall of the compression chamber 11, reducing direct impact with the rotor blades. When the refrigerant enters the compression chamber 11 through the elliptical main channel and the flared stepped opening 13, the inclined vent 122 allows the refrigerant to be introduced from the middle of the intake channel 12. The angle design makes this part of the airflow distributed circumferentially along the compression chamber 11, complementing the main airflow and improving the uniformity of the airflow in the compression chamber 11. In specific experiments, it was found that after adding the vent 122, when the speed of the rotary vane automotive air conditioning compressor increases to more than 2000 rpm, the volumetric efficiency does not decrease significantly.

[0031] In some embodiments of this utility model, such as Figure 2 and Figure 4 As shown, a transition port 14 is opened at the contact point between the exhaust port 121 and the inner wall of the cylinder 1.

[0032] Based on the above embodiment, the transition port 14 extends in an arc-shaped flare along the exhaust port 121 to the inner wall of the cylinder 1.

[0033] The transition port 14 acts like a funnel, improving exhaust efficiency. The arc-shaped flare design transforms the exhaust path from a sharp right-angle turn to a gradual curve. When the high-pressure refrigerant is discharged from the compression chamber 11, the airflow can smoothly turn along the arc surface, achieving a smoother exhaust effect. In addition, the arc transition eliminates the local high-pressure area at the right-angle connection, making the pressure distribution on the inner wall of the cylinder 1 more uniform during the exhaust stage. This reduces the instantaneous impact of the airflow on the inner wall, lowers the fatigue risk of the inner wall caused by long-term alternating stress, and further enhances the operating stability and service life of the compressor.

[0034] In some embodiments of this utility model, such as Figure 4 As shown, a stabilizing section 15 extends outward circumferentially from one end face of the cylinder body 1. The extension of the stabilizing section 15 increases the contact area between the cylinder body 1 and the bearing. At the same time, the continuous circumferential extension structure forms a reinforcing ring similar to a flange edge, which can disperse the local stress on the end face of the cylinder body 1 to a larger area. When the compressor vibrates radially due to rotor imbalance at high speed, the stabilizing section 15 can resist deformation through its own rigidity, avoiding the risk of micro-cracks caused by stress concentration at the edge of the cylinder body 1 in traditional structures. In addition, the circumferential extension of the stabilizing section 15 provides a more uniform distribution space for bolt connections, so that the preload during assembly is evenly transmitted along the circumference of the cylinder body 1, reducing the deformation of the cylinder body 1 caused by local bolt overtightening.

[0035] In some embodiments of this utility model, such as Figure 3 and Figure 5As shown, a number of spaced connecting holes 16 are opened on the two end faces of the cylinder body 1; the spaced distribution of the connecting holes 16 provides circumferentially uniform fixed points for the bearings at both ends. When the compressor is running at high speed, the bearings form a rigid connection with the cylinder body 1 through the connecting holes 16, reducing the displacement caused by vibration and avoiding the fluctuation of the gap between the rotor and the blades.

[0036] In some embodiments of this utility model, such as Figure 5 As shown, the cylinder body 1 includes a valve face 17, on which a number of spaced fixing holes 18 are opened for fixing the exhaust valve plate; the spaced fixing holes 18, together with the screw design, make the exhaust valve plate and the valve face 17 form a uniform sealing connection, so as to avoid refrigerant leakage caused by valve plate flutter under high frequency operating conditions of the compressor cylinder body 1.

[0037] In some embodiments of this utility model, such as Figure 5 As shown, the cylinder body 1 has oil holes 19 extending from one end face to the other along its length. Preferably, two oil holes 19 can be symmetrically opened on both sides of the cylinder body 1. The two ends of the oil holes 19 are connected to the two end faces of the cylinder body 1. The first bearing 2 and the second bearing 3 connected to the cylinder body 1 also have corresponding oil holes that are connected to the cylinder body oil holes 19. Under the action of the compressor discharge pressure, the lubricating oil enters from the oil hole of the second bearing 3, enters the first bearing 2 through the cylinder body oil hole 19, enters the compression chamber 11, and is discharged from the exhaust port 121 with the refrigerant, forming an internal circulation. The lubricating oil lubricates and cools the moving parts through the internal circulation, improving the compressor life and reliability.

[0038] Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claimed utility model. The scope of protection of this utility model is defined by the appended claims and their equivalents.

Claims

1. A rotary vane type automotive air conditioning compressor cylinder block, wherein a first bearing (2) is installed at one end and a second bearing (3) is installed at the other end, characterized in that, include: The cylinder (1) has a compression chamber (11) in the center and a through intake channel (12) along its length. The cylinder (1) has an exhaust port (121) along its circumference, which connects the compression chamber (11) and the outside of the cylinder (1). The cylinder (1) has a stepped opening (13) on its end face corresponding to the air intake channel (12). The stepped opening (13) is located on the side of the air intake channel (12) close to the compression chamber (11). The stepped opening (13) connects the air intake channel (12) and the compression chamber (11).

2. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, The air intake channel (12) has an elliptical cross section along its radial direction.

3. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, The stepped opening (13) is flared, and the opening width of the stepped opening (13) on the side closer to the compression chamber (11) is greater than the opening width on the side closer to the air intake channel (12).

4. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, At least one vent (122) is provided in the air intake channel (12), and the vent (122) connects the air intake channel (12) and the compression chamber (11).

5. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 4, characterized in that, The axis of the vent (122) is inclined relative to the end face of the cylinder (1).

6. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, A transition port (14) is provided at the contact point between the exhaust port (121) and the inner wall of the cylinder (1). The transition port (14) extends in an arc-shaped flare along the exhaust port (121) to the inner wall of the cylinder (1).

7. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, The cylinder body (1) has a stable section (15) extending outward in the circumferential direction from one end face.

8. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, The cylinder body (1) has several spaced connection holes (16) on its two end faces.

9. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, The cylinder body (1) includes a valve face (17), on which a plurality of spaced fixing holes (18) are opened.

10. The cylinder block of the rotary vane automotive air conditioning compressor according to claim 1, characterized in that, The cylinder (1) has oil holes (19) extending from one end face to the other end face along its length.

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