Compressor discharge structure, compression mechanism, and rotary compressor
By adjusting the structural dimensions of the exhaust chute, the problems of wasted compression work and exhaust pressure loss caused by improper exhaust chute volume were solved, thus achieving efficient operation of the rotary compressor.
Patent Information
- Application Number
- CN202521601687.4
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-07-29
- Publication Date
- 2026-08-25
- Estimated Expiration
- 2035-07-29
AI Technical Summary
The improper size of the exhaust chute volume in existing rotary compressors leads to wasted compression work and high exhaust pressure loss, affecting compressor performance.
By adjusting the structural dimensions of the exhaust chute to ensure its volume matches the cylinder compression chamber volume, the gas guiding capability is enhanced, dead volume and high-pressure gas volume are reduced, and exhaust pressure loss is decreased.
It improves the volumetric efficiency and performance of rotary compressors, and reduces compression work waste and exhaust pressure loss.
Smart Images
Figure CN224679695U_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of compressor technology, and in particular to a compressor exhaust structure, a rotary compressor compression mechanism, and a rotary compressor. Background Technology
[0002] In the compression mechanism of a rotary compressor, after the compression mechanism compresses the gas medium, the gas medium needs to be discharged from the exhaust port. In some existing technical solutions, the exhaust port is set on the end cover of the compression mechanism, and the inner peripheral wall of the cylinder is provided with an exhaust groove for guiding the gas medium in the cylinder into the exhaust port.
[0003] In related technologies, the structural dimensions of the exhaust chute in existing compression mechanisms affect its volume, thus impacting the performance of the rotary compressor. For example, if the exhaust chute volume is too large, the dead volume of the compression chamber within the cylinder becomes excessive. This prevents the compressed high-pressure gas from being completely expelled from the cylinder, resulting in wasted compression work and reduced compression efficiency. Furthermore, the high-pressure gas that cannot be expelled directly participates in the next compression cycle. The mixing of this high-pressure gas with the re-intake of low-pressure gas causes a pressure increase within the cylinder, leading to a reduction in actual intake volume and decreased volumetric efficiency.
[0004] When the volume of the exhaust chute is too small, the gas guiding capacity of the exhaust chute is insufficient. If some of the compressed high-pressure gas fails to be guided into the exhaust port in time through the exhaust chute, the exhaust pressure loss of the compression mechanism will be high, resulting in the exhaust pressure of the rotary compressor failing to meet the gas compression requirements. Summary of the Invention
[0005] The purpose of this application is to prevent the volume of the exhaust chute from being too large, which would result in the waste of some of the compression work done by the rotary compressor, thereby improving the volumetric efficiency of the compression mechanism, and to prevent the volume of the exhaust chute from being too small, which would result in high exhaust pressure loss of the compression mechanism, thereby improving the performance of the rotary compressor.
[0006] To achieve the above objectives, this application provides a compressor exhaust structure.
[0007] This application further provides a compression mechanism for a rotary compressor.
[0008] This application further provides a rotary compressor.
[0009] According to the compressor exhaust structure of this application, the compressor exhaust structure is applicable to the compression mechanism of a rotary compressor. The compressor exhaust structure includes: a cylinder body, the cylinder body having a compression hole, the compression hole penetrating the cylinder body from the axial end wall along the axial direction of the cylinder body, the inner peripheral wall of the compression hole being inclinedly provided with an exhaust groove extending axially along the cylinder body, the exhaust groove forming an opening on the axial end wall of the cylinder body, the radial dimension of the exhaust groove gradually decreasing from the axial end wall of the cylinder body to the center of the cylinder body; an end cover, the end cover being disposed on the outer side of the axial end wall of the cylinder body, the end cover being used to cover the compression hole, the end wall of the end cover opposite to the cylinder body having an exhaust hole, the opening of the exhaust groove being opposite to and communicating with the exhaust hole, so that the exhaust groove and the exhaust hole communicate to form an exhaust flow channel; its In the reference section, the maximum distance between the edge of the exhaust groove away from the compression hole and the central axis of the compression hole is D1, the maximum vertical distance from the side of the exhaust hole facing the cylinder to the exhaust groove is D2, the axial dimension of the compression hole is H, the inclination angle of the exhaust groove relative to the central axis of the compression hole is α, the first preset value is C1, the second preset value is C2, and D1, D2, H, α, C1 and C2 satisfy the following relationships: C1≤D1*D2*cosα / H≤C2, C1<C2, 6.3mm≤C1≤8.3mm, 9.8mm≤C2≤12.8mm. The reference section is the section generated by moving the reference axis parallel to the moving direction along the line connecting the center of the compression hole and the center of the exhaust hole, with the axial direction of the cylinder as the moving direction.
[0010] According to the compressor exhaust structure of this application, by limiting the structural dimensions of the exhaust chute to adjust its volume, the volume of the exhaust chute can be matched with the volume of the compression chamber defined by the cylinder. With good gas guiding capability, the exhaust chute can reduce the dead volume of the compression chamber in the cylinder, thereby reducing the waste of compression work in the rotary compressor, reducing the amount of high-pressure gas participating in the next compression cycle of the compression mechanism, improving the volumetric efficiency of the compression mechanism, and reducing the exhaust pressure loss of the compression mechanism, thus improving the performance of the rotary compressor.
[0011] In some examples of this application, the first preset value C1 satisfies the relationship: 7.2mm≤C1≤7.9mm.
[0012] In some examples of this application, the second preset value C2 satisfies the relationship: 10.3mm≤C2≤11mm.
[0013] In some examples of this application, the exhaust groove is arranged within the projection of the exhaust port into the cylinder axial direction, and the inclination angle α of the exhaust groove relative to the central axis of the compression port satisfies the relationship: 10°≤α≤50°.
[0014] In some examples of this application, the exhaust port extends along the axial direction of the cylinder body, and the exhaust groove is arranged within the projection of the exhaust port in the axial direction of the cylinder body. Furthermore, the maximum vertical distance D2 from the side of the exhaust port facing the cylinder body to the exhaust groove satisfies the relationship: 3.5mm≤D2≤15mm.
[0015] In some examples of this application, the plane perpendicular to the cylinder axial direction is used as the cross section, the outline of the exhaust groove in the cross section is an arc, and the chord length of the arc gradually decreases from the axial end wall of the cylinder to the center of the cylinder. Furthermore, on the reference cross section, the maximum distance D1 between the edge of the exhaust groove away from the compression hole and the central axis of the compression hole satisfies the relationship: 10mm≤D1≤70mm.
[0016] In some examples of this application, the axial dimension H of the compression hole satisfies the relationship: 5mm≤H≤50mm.
[0017] According to the rotary compressor compression mechanism of this application, the compression mechanism utilizes the aforementioned compressor exhaust structure, and further includes: a piston disposed within the cylinder of the compressor exhaust structure; a vane assembly extending and retracting along the radial direction of the cylinder on the inner peripheral wall of the compression hole, the vane assembly abutting against the piston; a frame and a cylinder head, one of the frame and the cylinder head covering one axial end wall of the cylinder, and the other covering the other axial end wall of the cylinder, at least one of the frame and the cylinder head being configured as an end cover; and a drive shaft, the piston being sleeved on the outside of the drive shaft, the drive shaft passing through the frame and the cylinder head, the drive shaft being used to drive the piston to rotate along the inner peripheral wall of the compression hole of the cylinder.
[0018] According to the rotary compressor compression mechanism of this application, the compression mechanism has a compressor exhaust structure. By limiting the structural dimensions of the exhaust chute of the compression mechanism to adjust the volume of the exhaust chute, the volume of the exhaust chute can be matched with the volume of the compression chamber defined by the cylinder. With good gas guiding capability, the exhaust chute can reduce the dead volume of the compression chamber in the cylinder, thereby reducing the waste of compression work in the rotary compressor, reducing the amount of high-pressure gas participating in the next compression cycle of the compression mechanism, improving the service life of the compression mechanism, reducing the exhaust pressure loss of the compression mechanism, and thus improving the performance of the rotary compressor.
[0019] The rotary compressor according to this application includes the compression mechanism of the rotary compressor described above.
[0020] According to the rotary compressor of this application, a compression mechanism is disposed in the rotary compressor, and the compression mechanism has a compressor exhaust structure. By limiting the structural dimensions of the exhaust chute of the compression mechanism, the volume of the exhaust chute can be adjusted so that the volume of the exhaust chute matches the volume of the compression chamber defined by the cylinder. With good gas guiding capability, the exhaust chute can reduce the dead volume of the compression chamber in the cylinder, thereby reducing the waste of compression work in the rotary compressor, reducing the amount of high-pressure gas participating in the next compression cycle of the compression mechanism, improving the volumetric efficiency of the compression mechanism, and reducing the exhaust pressure loss of the compression mechanism, thereby improving the performance of the rotary compressor. Attached Figure Description
[0021] Figure 1 This is a top view of the compressor exhaust structure according to an embodiment of this application;
[0022] Figure 2 yes Figure 1 A partial sectional view at point AA in the middle;
[0023] Figure 3 yes Figure 2 A magnified view of a section at point B in the middle;
[0024] Figure 4 This is a top view of the cylinder block according to an embodiment of this application;
[0025] Figure 5 yes Figure 4 A magnified view of a section at point C;
[0026] Figure 6 This is a top view of the end cap according to an embodiment of this application.
[0027] In the diagram, 100 represents the compressor exhaust structure;
[0028] 1. Cylinder block; 11. Compression bore; 12. Compression chamber; 13. Exhaust chute; 14. Auxiliary circle;
[0029] 2. End cap; 21. Vent hole; 22. Vent flow channel. Detailed Implementation
[0030] The specific embodiments of this application will be described in further detail below with reference to the accompanying drawings and examples. The following examples are used to illustrate this application, but are not intended to limit the scope of this application.
[0031] like Figures 1-6As shown in the illustration, this application discloses a compressor exhaust structure 100, which is applicable to the compression mechanism of a rotary compressor. The rotary compressor also includes a drive device, which is connected to the compression mechanism for transmission. The drive device is used to drive the compression mechanism to draw in a gaseous medium and to drive the compression mechanism to compress the gaseous medium and discharge it outside the compression mechanism. The compressor exhaust structure 100 is used to discharge the gaseous medium inside the compression mechanism. It should be noted that the gaseous medium can be a refrigerant or other gases, etc.
[0032] like Figures 1-6 As shown, the compressor exhaust structure 100 according to an embodiment of this application includes: a cylinder body 1 and an end cover 2. The cylinder body 1 is provided with a compression hole 11 defining a compression chamber 12. The gas medium is drawn into the compression chamber 12 and compressed within the compression chamber 12. The compression hole 11 extends through the axial end wall of the cylinder body 1 along the axial direction of the cylinder body 1. The axial direction of the cylinder body 1 can be... Figure 5 The compression hole 11 has an inclined exhaust groove 13 extending axially along the cylinder body 1 on its inner peripheral wall. That is, the groove wall of the exhaust groove 13 has an inclination angle relative to the central axis of the compression hole 11. In some preferred embodiments, the exhaust groove 13 can be an arc-shaped groove, meaning the groove wall of the exhaust groove 13 is an arc surface. Furthermore, the exhaust groove 13 can be formed by removing part of the sidewall of the cylinder body 1. The exhaust groove 13 forms an open opening on the axial end wall of the cylinder body 1, and the radial dimension of the exhaust groove 13 gradually decreases from the axial end wall of the cylinder body 1 to the center of the cylinder body 1.
[0033] Furthermore, the end cap 2 is installed on the outer side of the axial end wall of the cylinder body 1. The end cap 2 is used to block the compression hole 11, and the end cap 2 can prevent the gas medium in the compression chamber 12 from leaking directly from the opening of the compression hole 11 on the axial end wall of the cylinder body 1. Figure 1 , Figure 2 , Figure 6 As shown, the end cap 2 is opposite to the cylinder body 1 at the end wall (i.e. Figure 2 The lower end wall of the middle end cover 2 is provided with an exhaust hole 21. The open opening of the exhaust groove 13 is opposite to and connected to the exhaust hole 21, so that the exhaust groove 13 and the exhaust hole 21 are connected to form an exhaust flow channel 22. The compressed gas medium in the compression chamber 12 flows through the exhaust groove 13 and the exhaust hole 21 in sequence along the exhaust flow channel 22 and is discharged outside the compressor exhaust structure 100. By using the exhaust groove 13 to guide the gas medium, the gas medium can more easily flow from the compression chamber 12 to the exhaust hole 21.
[0034] Furthermore, such as Figure 4 As shown, on the reference section, the maximum distance between the edge of the exhaust chute 13 away from the compression hole 11 and the central axis of the compression hole 11 is D1, where, as Figure 1 and Figure 2As shown, the reference section is the cross-section generated by moving the reference axis parallel to the axis of movement along the axial direction of the cylinder block 1, with the line connecting the center of the compression port 11 and the center of the exhaust port 21 as the reference axis. It should be noted that... Figure 2 The section at point AA is the reference section.
[0035] On the axial end wall surface opposite to the cylinder block 1 and end cover 2, an auxiliary circle 14 is drawn with the center of the compression hole 11 as the center. When the exhaust groove 13 is located inside the auxiliary circle 14 and the edge of the exhaust groove 13 is tangent to the auxiliary circle 14, the radius of the auxiliary circle 14 is equal to the maximum distance D1 between the edge of the exhaust groove 13 away from the compression hole 11 and the central axis of the compression hole 11. Furthermore, as... Figure 3 , Figure 4 As shown, the diameter of the compression hole 11 is D3. On the reference section, the maximum distance between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11 is D4. D1, D3 and D4 satisfy the relationship: D1=1 / 2D3+D4.
[0036] like Figure 3 As shown, the maximum vertical distance from the side of the exhaust port 21 facing the cylinder block 1 to the exhaust groove 13 is D2. In the reference section, the connection point between the end cap 2 and the end wall opposite to the cylinder block 1 and the exhaust port 21 (i.e.,...) Figure 2 The vertical distance between the edge of the connection between the lower end wall of the middle end cover 2 and the lower opening of the exhaust port 21 and the exhaust ramp 13 is the maximum vertical distance D2 from the side of the exhaust port 21 facing the cylinder block 1 to the exhaust ramp 13. The size of the maximum vertical distance D2 from the side of the exhaust port 21 facing the cylinder block 1 to the exhaust ramp 13 affects the minimum connecting area of the exhaust channel 22, thereby affecting the exhaust speed of the exhaust channel 22. Specifically, the larger the maximum vertical distance D2 from the side of the exhaust port 21 facing the cylinder block 1 to the exhaust ramp 13, the larger the minimum connecting area of the exhaust channel 22, and the faster the exhaust speed of the exhaust channel 22.
[0037] like Figures 3-5As shown, the axial dimension of the compression hole 11 is H, the inclination angle of the exhaust groove 13 relative to the central axis of the compression hole 11 is α, the first preset value is C1, the second preset value is C2, and D1, D2, H, α, C1 and C2 satisfy the following relationship: C1≤D1*D2*cosα / H≤C2, C1<C2. Wherein, 6.3mm≤C1≤8.3mm, 9.8mm≤C2≤12.8mm, the first preset value C1 and the second preset value C2 in the above formula can be obtained through experiments. By measuring the first preset value C1 and the second preset value C2, and then determining the volume of the compression chamber 12 according to the exhaust requirements of the rotary compressor, the axial dimension H of the compression hole 11 and the diameter D3 of the compression hole 11 are determined. By adjusting the inclination angle α of the exhaust groove 13 relative to the central axis of the compression hole 11, the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11, and the position of the exhaust hole 21, it is ensured that the calculated value of the above formula is not less than the first preset value C1 and not greater than the second preset value C2. In this way, the exhaust groove 13 can have a suitable volume size, and it can ensure that the exhaust groove 13 has a good gas guiding ability while the dead volume of the compression chamber 12 in the cylinder 1 is smaller.
[0038] Specifically, after determining the axial dimension H and the diameter D3 of the compression hole 11, the calculated values of the above formulas are reduced by increasing the inclination angle α of the exhaust groove 13 relative to the central axis of the compression hole 11, reducing the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11, and reducing the maximum vertical distance D2 between the side of the exhaust hole 21 facing the cylinder 1 and the exhaust groove 13. By ensuring that the calculated value is not less than the first preset value C1, the exhaust groove 13 can be ensured to have good gas guiding ability, thereby reducing the exhaust pressure loss of the compression mechanism.
[0039] Conversely, after determining the axial dimension H and the diameter D3 of the compression hole 11, by reducing the inclination angle α of the exhaust groove 13 relative to the central axis of the compression hole 11, increasing the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11, and increasing the maximum vertical distance D2 between the side of the exhaust hole 21 facing the cylinder 1 and the exhaust groove 13, the calculated value of the above formula increases. By ensuring that the calculated value is not greater than the second preset value C2, the volume of the exhaust groove 13 can be ensured to be appropriate, thereby reducing the dead volume of the compression chamber 12.
[0040] Therefore, by limiting the structural dimensions of the exhaust chute 13 to adjust its volume, the volume of the exhaust chute 13 can be matched with the volume of the compression chamber 12 defined by the cylinder 1. With good gas guiding capability, the exhaust chute 13 can reduce the dead volume of the compression chamber 12 in the cylinder 1, thereby reducing the waste of compression work in the rotary compressor, reducing the amount of high-pressure gas participating in the next compression cycle of the compression mechanism, improving the volumetric efficiency of the compression mechanism, and reducing the exhaust pressure loss of the compression mechanism, thus improving the performance of the rotary compressor.
[0041] In some more preferred embodiments of this application, the first preset value C1 satisfies the relationship: 7.2mm≤C1≤7.9mm. Specifically, once the volume of the compression chamber 12 is determined, as the diameter D3 of the compression hole 11 gradually increases, the axial dimension H of the compression hole 11 gradually decreases, meaning the shape of the cylinder 1 gradually becomes flat. At this time, the ratio of the diameter D3 of the compression hole 11 to the axial dimension H of the compression hole 11 gradually increases, meaning the calculated value of the above formula gradually increases. By setting the first preset value C1 to no more than 7.9 mm and making the value of the first preset value C1 closer to 7.9 mm, the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11 can be larger, the maximum vertical distance D2 between the side of the exhaust hole 21 facing the cylinder 1 and the exhaust groove 13 can be larger, and the inclination angle α of the exhaust groove 13 relative to the central axis of the compression hole 11 can be smaller. The exhaust groove 13 has a sufficiently large volume, thereby improving the air guiding effect of the exhaust groove 13 and reducing the exhaust pressure loss of the compressor exhaust structure 100.
[0042] Conversely, as the diameter D3 of the compression hole 11 gradually decreases, the axial dimension H of the compression hole 11 gradually increases, meaning the shape of the cylinder 1 gradually becomes elongated. At this time, the ratio of the diameter D3 of the compression hole 11 to the axial dimension H of the compression hole 11 gradually decreases, meaning the calculated value of the above formula gradually decreases. By setting the first preset value C1 to not less than 7.2 mm and making the value of the first preset value C1 closer to 7.2 mm, the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11 can be smaller, the maximum vertical distance D2 between the side of the exhaust hole 21 facing the cylinder 1 and the exhaust groove 13 can be smaller, and the tilt angle α of the exhaust groove 13 relative to the central axis of the compression hole 11 can be larger. This allows the volume of the exhaust groove 13 to be smaller, and the dead volume of the compression chamber 12 inside the cylinder 1 to be smaller.
[0043] In some preferred embodiments, the first preset value C1 can be set to 7.3 mm. This setting can make the air guiding capacity and volume of the exhaust chute 13 more balanced, and can make the performance of the rotary compressor better.
[0044] In some more preferred embodiments of this application, the second preset value C2 satisfies the relationship: 10.3mm≤C2≤11mm. Specifically, once the volume of the compression chamber 12 is determined, as the diameter D3 of the compression hole 11 gradually increases, the axial dimension H of the compression hole 11 gradually decreases, meaning the shape of the cylinder 1 gradually becomes flat. At this time, the ratio of the diameter D3 of the compression hole 11 to the axial dimension H of the compression hole 11 gradually increases, meaning the calculated value of the above formula gradually increases. By setting the second preset value C2 to no more than 11mm and making the value of the second preset value C2 closer to 11mm, the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11 can be larger, the maximum vertical distance D2 between the side of the exhaust hole 21 facing the cylinder 1 and the exhaust groove 13 can be larger, and the inclination angle α of the exhaust groove 13 relative to the central axis of the compression hole 11 can be smaller. The exhaust groove 13 has a sufficiently large volume, thereby improving the air guiding effect of the exhaust groove 13 and reducing the exhaust pressure loss of the compressor exhaust structure 100.
[0045] Conversely, as the diameter D3 of the compression hole 11 gradually decreases, the axial dimension H of the compression hole 11 gradually increases, meaning the shape of the cylinder 1 gradually becomes elongated. At this time, the ratio of the diameter D3 of the compression hole 11 to the axial dimension H of the compression hole 11 gradually decreases, meaning the calculated value of the above formula gradually decreases. By setting the first preset value C2 to not less than 10.3 mm and making the value of the first preset value C2 closer to 10.3 mm, the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11 can be smaller, the maximum vertical distance D2 between the side of the exhaust hole 21 facing the cylinder 1 and the exhaust groove 13 can be smaller, and the tilt angle α of the exhaust groove 13 relative to the central axis of the compression hole 11 can be larger. This allows the volume of the exhaust groove 13 to be smaller, and the dead volume of the compression chamber 12 inside the cylinder 1 to be smaller.
[0046] In some preferred embodiments, the second preset value C2 can be set to 10.9 mm. This setting can make the air guiding capacity and volume of the exhaust chute 13 more balanced, and can make the performance of the rotary compressor better.
[0047] Furthermore, the exhaust groove 13 is arranged within the projection of the exhaust port 21 along the axial direction of the cylinder body 1. The inclination angle α of the exhaust groove 13 relative to the central axis of the compression port 11 satisfies the relationship: 10°≤α≤50°. After determining the axial dimension H and the diameter D3 of the compression port 11, if the inclination angle α of the exhaust groove 13 relative to the central axis of the compression port 11 is too small, in order to satisfy the above calculation formula, the compressor exhaust structure 100 needs to have a larger maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression port 11, and a larger maximum vertical distance D2 from the side of the exhaust port 21 facing the cylinder body 1 to the exhaust groove 13. This will result in excessive removal of the sidewall of the cylinder body 1 during the machining of the exhaust groove 13, and insufficient strength of the sidewall structure of the cylinder body 1, which will make the cylinder body 1 prone to breakage.
[0048] If the inclination angle α of the exhaust groove 13 relative to the central axis of the compression hole 11 is too large, in order to satisfy the above calculation formula, the compressor exhaust structure 100 needs to have a smaller maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11, and a smaller maximum vertical distance D2 between the side of the exhaust hole 21 facing the cylinder 1 and the exhaust groove 13. The gas medium flows a longer distance in the part of the structure of the exhaust flow channel 22 defined by the exhaust groove 13, and the exhaust groove 13 has difficulty in quickly guiding the gas medium out of the compression chamber 12, which will cause high pressure gas to easily remain in the compression chamber 12.
[0049] By setting the inclination angle α of the exhaust groove 13 relative to the central axis of the compression hole 11 to 10° to 50°, the structural dimensions of the exhaust groove 13 can be made more suitable, which can reduce the processing difficulty of the compressor exhaust structure 100 and improve the exhaust performance of the compressor exhaust structure 100.
[0050] In some embodiments of this application, the maximum vertical distance D2 from the side of the exhaust port 21 facing the cylinder 1 to the exhaust chute 13 satisfies the relationship: 3.5mm ≤ D2 ≤ 15mm. When the exhaust pressure inside the compressor exhaust structure 100 is constant, this arrangement can make the exhaust flow rate at the minimum flow area of the exhaust channel 22 sufficiently large, thereby reducing the exhaust pressure loss of the compressor exhaust structure 100 and accelerating the gas discharge speed in the compression chamber 12, which can further improve the performance of the rotary compressor.
[0051] Furthermore, taking a plane perpendicular to the axial direction of the cylinder block 1 as a cross-section, the outline of the exhaust groove 13 is an arc, and the chord length of the arc gradually decreases from the axial end wall of the cylinder block 1 to the center of the cylinder block 1. In the reference cross-section, the maximum distance D1 between the edge of the exhaust groove 13 away from the compression hole 11 and the central axis of the compression hole 11 satisfies the relationship: 10mm ≤ D1 ≤ 70mm. In some preferred embodiments, the maximum distance D4 between the edge of the exhaust groove 13 and the inner peripheral wall of the compression hole 11 can be 1mm to 2mm, thus allowing the opening size of the exhaust groove 13 on the axial end wall of the cylinder block 1 to match the diameter of the exhaust hole 21. Based on this, by setting the maximum interval D1 between the edge of the exhaust groove 13 away from the compression hole 11 and the central axis of the compression hole 11 to 10mm to 70mm, the diameter of the compression hole 11 can be adapted to the size of the opening of the exhaust groove 13 on the axial end wall of the cylinder body 1, thereby meeting the exhaust requirements of the compressor exhaust structure 100.
[0052] Furthermore, the axial dimension H of the compression hole 11 satisfies the relationship: 5mm ≤ H ≤ 50mm. After determining the volume of the compression chamber 12 and the diameter D3 of the compression hole 11, the value of the axial dimension H of the compression hole 11 can be calculated. When the axial dimension H of the compression hole 11 is between 5mm and 50mm, the structural dimensions of the exhaust groove 13 can be adjusted according to the above calculation formula so that the compressor exhaust structure 100 can reduce the dead volume of the compression chamber 12 in the cylinder 1, and at the same time, the compressor exhaust structure 100 can reduce the exhaust pressure loss of the compression mechanism.
[0053] Based on this, this application further discloses a compression mechanism for a rotary compressor. The compression mechanism utilizes the compressor exhaust structure 100 of the above embodiment. The compression mechanism according to this application embodiment also includes: a piston, a vane assembly, a frame, a cylinder head, and a drive shaft. The piston is disposed in the cylinder 1 of the compressor exhaust structure 100. The vane assembly is extended and retracted along the radial direction of the cylinder 1 on the inner peripheral wall of the compression hole 11. The vane assembly abuts against the piston. The vane assembly and the piston together divide the compression chamber 12 into an intake chamber and an exhaust chamber. The exhaust hole 21 communicates with the exhaust chamber and is used to discharge the compressed gas medium.
[0054] One of the frame and cylinder head is covered on one side of the axial end wall of the cylinder body 1, and the other is covered on the other side of the axial end wall of the cylinder body 1. In this way, the openings formed by the compression hole 11 on both sides of the axial end wall of the cylinder body 1 are closed, and the gas medium in the compression chamber 12 is difficult to leak directly from the openings of the compression hole 11 to the outside of the compression mechanism. At least one of the frame and cylinder head is constructed as an end cover 2, that is, the frame is constructed as the end cover 2 of the above embodiment and has an exhaust hole 21, or the cylinder head is constructed as the end cover 2 of the above embodiment and has an exhaust hole 21, or both the frame and cylinder head are constructed as the end cover 2 of the above embodiment and both have an exhaust hole 21.
[0055] Furthermore, the piston is sleeved on the outside of the drive shaft, which passes through the frame and cylinder head. The drive shaft is used to drive the piston to rotate along the inner circumferential wall of the compression hole 11 of the cylinder 1. Specifically, the drive shaft is connected to the drive device of the rotary compressor. The drive device is used to drive the drive shaft to rotate the piston. When the piston rotates, it draws the gas medium into the intake chamber and compresses the gas medium in the exhaust chamber.
[0056] According to the compression mechanism of the present application embodiment, the compression mechanism has a compressor exhaust structure 100. By limiting the structural dimensions of the exhaust chute 13 of the compression mechanism, the volume of the exhaust chute 13 can be adjusted so that the volume of the exhaust chute 13 matches the volume of the compression chamber 12 defined by the cylinder 1. The exhaust chute 13 has good gas guiding ability, which can reduce the dead volume of the compression chamber 12 in the cylinder 1, thereby reducing the waste of compression work in the rotary compressor, reducing the amount of high-pressure gas participating in the next compression cycle of the compression mechanism, improving the volumetric efficiency of the compression mechanism, and reducing the exhaust pressure loss of the compression mechanism, thereby improving the performance of the rotary compressor.
[0057] Based on this, the present application further discloses a rotary compressor, which includes the compression mechanism described in the above embodiments.
[0058] According to the rotary compressor of the present application embodiment, the compression mechanism is disposed in the rotary compressor, and the compression mechanism has a compressor exhaust structure 100. By limiting the structural dimensions of the exhaust chute 13 of the compression mechanism, the volume of the exhaust chute 13 can be adjusted so that the volume of the exhaust chute 13 matches the volume of the compression chamber 12 defined by the cylinder 1. The exhaust chute 13 has good gas guiding ability, which can reduce the dead volume of the compression chamber 12 in the cylinder 1, thereby reducing the waste of compression work in the rotary compressor, reducing the amount of high-pressure gas participating in the next compression cycle of the compression mechanism, improving the volumetric efficiency of the compression mechanism, and reducing the exhaust pressure loss of the compression mechanism, thereby improving the performance of the rotary compressor.
[0059] The above description is only a preferred embodiment of this application. It should be noted that for those skilled in the art, several improvements and substitutions can be made without departing from the technical principles of this application, and these improvements and substitutions should also be considered within the scope of protection of this application.
Claims
1. A compressor exhaust structure, said compressor exhaust structure being applicable to the compression mechanism of a rotary compressor, characterized in that, The compressor exhaust structure includes: The cylinder body is provided with a compression hole, which extends through the axial end wall of the cylinder body along the axial direction. The inner peripheral wall of the compression hole is provided with an exhaust groove extending along the axial direction of the cylinder body. The exhaust groove forms an opening on the axial end wall of the cylinder body. The radial dimension of the exhaust groove gradually decreases from the axial end wall of the cylinder body to the center of the cylinder body. An end cap is provided on the outer side of the axial end wall of the cylinder body. The end cap is used to cover the compression hole. The end wall opposite to the cylinder body is provided with an exhaust hole. The opening of the exhaust groove is opposite to and connected to the exhaust hole, so that the exhaust groove and the exhaust hole are connected to form an exhaust flow channel. In the reference section, the maximum distance between the edge of the exhaust groove away from the compression hole and the central axis of the compression hole is D1, the maximum vertical distance from the side of the exhaust hole facing the cylinder to the exhaust groove is D2, the axial dimension of the compression hole is H, the inclination angle of the exhaust groove relative to the central axis of the compression hole is α, the first preset value is C1, the second preset value is C2, and D1, D2, H, α, C1 and C2 satisfy the following relationships: C1≤D1*D2*cosα / H≤C2, C1<C2, 6.3mm≤C1≤8.3mm, 9.8mm≤C2≤12.8mm. The reference section is the section generated by moving the reference axis parallel to the moving direction along the line connecting the center of the compression hole and the center of the exhaust hole.
2. The compressor exhaust structure according to claim 1, characterized in that, The first preset value C1 satisfies the relationship: 7.2mm≤C1≤7.9mm.
3. The compressor exhaust structure according to claim 1, characterized in that, The second preset value C2 satisfies the following relationship: 10.3mm≤C2≤11mm.
4. The compressor exhaust structure according to any one of claims 1-3, characterized in that, The exhaust groove is arranged within the projection of the exhaust hole into the cylinder axial direction, and the inclination angle α of the exhaust groove relative to the central axis of the compression hole satisfies the relationship: 10°≤α≤50°.
5. The compressor exhaust structure according to any one of claims 1-3, characterized in that, The exhaust port extends along the axial direction of the cylinder body, and the exhaust groove is arranged within the projection of the exhaust port in the axial direction of the cylinder body. Furthermore, the maximum vertical distance D2 from the side of the exhaust port facing the cylinder body to the exhaust groove satisfies the relationship: 3.5mm≤D2≤15mm.
6. The compressor exhaust structure according to claim 2 or 3, characterized in that, With a plane perpendicular to the cylinder axial direction as the cross section, the outline of the exhaust groove in the cross section is an arc, and the chord length of the arc gradually decreases from the axial end wall of the cylinder to the center of the cylinder. Furthermore, on the reference cross section, the maximum distance D1 between the edge of the exhaust groove away from the compression hole and the central axis of the compression hole satisfies the relationship: 10mm≤D1≤70mm.
7. The compressor exhaust structure according to claim 6, characterized in that, The axial dimension H of the compression hole satisfies the following relationship: 5mm≤H≤50mm.
8. A compression mechanism for a rotary compressor, characterized in that, The compression mechanism employs a compressor exhaust structure according to any one of claims 1-7, and the compression mechanism further includes: Piston, the piston being disposed within the cylinder of the compressor exhaust structure; A sliding vane assembly is provided on the inner peripheral wall of the compression hole along the radial direction of the cylinder body, and the sliding vane assembly abuts against the piston; A frame and a cylinder head, wherein one of the frame and the cylinder head is disposed on one side axial end wall of the cylinder body, and the other is disposed on the other side axial end wall of the cylinder body, and at least one of the frame and the cylinder head is configured as the end cover; A drive shaft is provided, and the piston is sleeved on the outside of the drive shaft. The drive shaft passes through the frame and the cylinder head. The drive shaft is used to drive the piston to rotate along the inner peripheral wall of the compression hole of the cylinder.
9. A rotary compressor, characterized in that, Includes the compression mechanism of the rotary compressor according to claim 8.