Pump body structure of rotary cylinder piston compressor, rotary cylinder piston compressor and air conditioner

Abstract

The present invention provides a pump body structure of a rotary piston compressor, a rotary piston compressor and an air conditioner, wherein the pump body structure of the rotary piston compressor comprises: a cylinder sleeve, the cylinder sleeve is provided with an intake channel, an exhaust channel and an exhaust groove, the exhaust groove is arranged on the inner wall of the cylinder sleeve, the exhaust groove is connected with the exhaust channel and extends toward the inner wall of the exhaust chamber of the cylinder sleeve. The technical solution of the present invention effectively solves the problem of low energy efficiency of the compressor caused by over-compression of the rotary piston compressor in the prior art.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioners, and in particular to a pump body structure of a rotary cylinder piston compressor, a rotary cylinder piston compressor and an air conditioner. Background Art

[0002] The rotating shaft of the rotary cylinder piston compressor drives the piston to rotate, and the piston drives the cylinder to rotate. The piston only has relative reciprocating motion relative to the rotating shaft and the cylinder, and the two reciprocating motions are perpendicular to each other, and suction, compression and exhaust are achieved in this process. During the suction, compression and exhaust process, the radial distance between the piston and the inner diameter of the cylinder liner changes periodically. During the suction process, the radial distance between the piston and the inner diameter of the cylinder liner continues to increase; during the compression and exhaust process, the distance continues to decrease until 10 -2 mm. During the exhaust process, the high-pressure gas outside the exhaust port must first flow through the space formed by the piston head and the cylinder liner before reaching the exhaust port. However, as the radial distance from the piston head to the cylinder liner continues to decrease, the area of ​​the exhaust channel (channel area = radial distance from the piston head to the cylinder liner × cross-sectional height) is much smaller than the exhaust port area. As the radial distance from the piston head to the cylinder liner continues to decrease, the effective area also continues to decrease, resulting in large exhaust resistance and increased exhaust pressure, which is significantly higher than the designed exhaust pressure. The entire compression chamber is over-compressed, affecting the energy efficiency of the compressor. Summary of the invention

[0003] The main purpose of the present invention is to provide a pump body structure of a rotary piston compressor, a rotary piston compressor and an air conditioner to solve the problem of low energy efficiency of the compressor caused by over-compression of the rotary piston compressor in the prior art.

[0004] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, a pump body structure of a rotary piston compressor is provided, including: a cylinder liner, on which an intake channel, an exhaust channel and an exhaust groove are arranged, the exhaust groove is opened on the inner wall of the cylinder liner, and the exhaust groove is connected with the exhaust channel and extends toward the inner wall of the exhaust chamber of the cylinder liner.

[0005] Furthermore, the exhaust groove is arc-shaped.

[0006] Furthermore, the exhaust groove is in an arc shape.

[0007] Furthermore, the pump body structure also includes a piston and a cylinder, the piston sleeve is arranged in the cylinder, the cylinder sleeve is arranged in the cylinder sleeve, the contour line diameter of the exhaust groove is d, the outer circle diameter of the cross section of the piston is d1, and the value range of d is between 0.8d1 and 1.2d1.

[0008] Furthermore, a pressure relief channel is also provided on the cylinder liner, and the pressure relief channel is located on the path of the piston rotating from the exhaust channel to the intake channel.

[0009] Furthermore, the end of the exhaust groove and the pressure relief channel are located on the same plane perpendicular to the end surface of the cylinder liner.

[0010] Further, the exhaust passage is located in the middle of the outline of the exhaust groove.

[0011] Furthermore, the width of the exhaust groove gradually narrows as it extends from the exhaust channel to a direction away from the exhaust channel.

[0012] Furthermore, the circumferential span angle of the exhaust groove is α, and the value range of α is between 0° and 90°.

[0013] Furthermore, the minimum distance from the exhaust groove to the end surface of the cylinder liner is L, and the value range of L is between 1 mm and 10 mm.

[0014] Furthermore, the cross section of the exhaust groove is in the shape of a circular arc section or a rectangular section.

[0015] Furthermore, the cross-sectional width of the exhaust groove is b, and b is greater than 0.5 mm.

[0016] Furthermore, the depth of the exhaust groove is h, and h is greater than 0.1 mm.

[0017] Furthermore, the cross-sectional area of ​​the exhaust groove is Si, and Si is greater than 0.05 mm2.

[0018] Furthermore, the cross-sectional area of ​​the piston head is S, and Si and S satisfy 0.001 <Si / S<0.5。

[0019] Furthermore, the volume of the exhaust groove is v, the displacement of the pump structure is V, and v and V satisfy 0.1% <v / V<2%。

[0020] According to another aspect of the present invention, a rotary piston compressor is provided. The rotary piston compressor includes a pump body assembly, and the pump body assembly is the above-mentioned pump body assembly.

[0021] Furthermore, the rotary cylinder piston compressor has a single cylinder and dual compression chamber structure.

[0022] According to another aspect of the present invention, an air conditioner is provided. The air conditioner includes a rotary piston compressor. The rotary piston compressor is the rotary piston compressor described above.

[0023] By applying the technical solution of the present invention, the cylinder sleeve is provided with an exhaust groove, so that when the gas is discharged from the exhaust channel, the exhaust groove expands the volume of the exhaust channel, increases the effective exhaust area, reduces the exhaust resistance, and improves the energy efficiency, thus greatly reducing the over-compression phenomenon. The technical solution of the present invention effectively solves the problem of low energy efficiency of the compressor caused by over-compression of the rotary cylinder piston compressor in the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0025] Figure 1 A schematic diagram of the three-dimensional structure of a cylinder liner of an embodiment of a rotary piston compressor according to the present invention is shown;

[0026] Figure 2 Shows Figure 1 A schematic diagram of the matching structure of the exhaust groove and the exhaust channel of the cylinder liner;

[0027] Figure 3 Show Figure 1 A three-dimensional schematic diagram of the matching structure of the cylinder liner and the piston of the rotary cylinder piston compressor;

[0028] Figure 4 Shows Figure 1 A schematic plan view of the matching structure of the cylinder liner and the piston of the rotary piston compressor;

[0029] Figure 5 Shows Figure 1 A schematic cross-sectional view of a piston of a rotary piston compressor;

[0030] Figure 6 Shows Figure 1 A partial cross-sectional schematic diagram of a rotary cylinder piston compressor;

[0031] Figure 7 Shows Figure 1 A schematic plan view of a rotary piston compressor; and

[0032] Figure 8 A comparative graph without and with venting grooves is shown.

[0033] The above drawings include the following reference numerals:

[0034] 10. Cylinder liner; 20. Piston; 30. Cylinder; 40. Rotating shaft; 100. Exhaust passage; 200. Exhaust groove; 300. Pressure relief passage. DETAILED DESCRIPTION

[0035] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0036] It should be noted that the following detailed descriptions are illustrative and are intended to provide further explanation of the present application. Unless otherwise specified, all technical and scientific terms used herein have the same meanings as those commonly understood by those skilled in the art to which the present application belongs.

[0037] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0038] Now, exemplary embodiments according to the present application will be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in a variety of different forms and should not be interpreted as being limited to the embodiments described herein. It should be understood that these embodiments are provided to make the disclosure of the present application thorough and complete, and to fully convey the concepts of these exemplary embodiments to those of ordinary skill in the art. In the accompanying drawings, for clarity, the thickness of the layers and regions is enlarged, and the same reference numerals are used to represent the same devices, so their description will be omitted.

[0039] like Figures 1 to 7 As shown, the present embodiment provides a pump body structure of a rotary piston compressor including a cylinder liner 10. The cylinder liner 10 is provided with an intake passage, an exhaust passage 100 and an exhaust groove 200, the exhaust groove 200 is opened on the inner wall of the cylinder liner 10, and the exhaust groove 200 is connected with the exhaust passage 100 and extends toward the inner wall of the exhaust chamber of the cylinder liner 10.

[0040] By applying the technical solution of this embodiment, the cylinder sleeve 10 is provided with an exhaust groove 200, so that when the gas is discharged from the exhaust channel 100, the exhaust groove 200 expands the volume of the exhaust channel 100, increases the effective exhaust area, reduces the exhaust resistance, and improves the energy efficiency, thus greatly reducing the over-compression phenomenon. The technical solution of this embodiment effectively solves the problem of low energy efficiency of the compressor caused by over-compression of the rotary cylinder piston compressor in the prior art.

[0041] like Figure 1 As shown, in the technical solution of this embodiment, the exhaust groove 200 is arc-shaped. The contour line of the exhaust groove 200 is arc-shaped, so that the piston 20 and the exhaust groove 200 are better matched, because the outer contour of the piston 20 is also arc-shaped. Specifically, the exhaust groove 200 is arc-shaped. The cross-section of the end face of the piston 20 is circular, so that the piston 20 and the exhaust groove 200 are more accurately matched, and the exhaust efficiency is higher.

[0042] like Figure 7 As shown, in the technical solution of this embodiment, the pump body structure also includes a piston 20 and a cylinder 30, the piston 20 is sleeved in the cylinder 30, the cylinder sleeve 10 is arranged in the cylinder sleeve 10, the contour line diameter of the exhaust groove 200 is d, the outer diameter of the cross section of the piston 20 is d1, and the value range of d is between 0.8d1 and 1.2d1. The above structure makes the exhaust effect of the pump body structure better. The pump body structure also includes a rotating shaft 40, the rotating shaft 40 drives the piston 20 to rotate, and the piston 20 drives the cylinder 30 to rotate. When working, at the moment when the compression chamber exhausts, the entire compression chamber is separated from the arc-shaped exhaust groove 200 to avoid cross-flow between the exhaust system and the intake system.

[0043] like Figure 1 and Figure 7 As shown, in the technical solution of this embodiment, a pressure relief channel 300 is also provided on the cylinder liner 10, and the pressure relief channel 300 is located on the path of the piston 20 rotating from the exhaust channel 100 to the intake channel. The provision of the pressure relief channel 300 greatly saves and improves the compression efficiency and reduces the vibration of the pump body structure. After the exhaust is completed, there is a gap between the piston 20 and the inner wall of the cylinder liner 10. At this time, the gas with a higher pressure will be between the piston 20 and the cylinder liner 10. If air is inhaled at this time, the pump body structure will have a greater impact due to the large change in pressure.

[0044] like Figure 1 As shown, in the technical solution of this embodiment, the end of the exhaust groove 200 and the pressure relief channel 300 are located on the same plane perpendicular to the end surface of the cylinder liner 10. The above structure not only ensures the isolation of the exhaust chamber and the suction chamber, but also ensures that the area of ​​the exhaust groove 200 is large. When there are multiple pressure relief channels 300, the pressure relief channels 300 are located on the same plane parallel to the axis of the cylinder liner 10, which refers to the pressure relief channel 300 closest to the exhaust channel 100.

[0045] like Figure 1As shown, in the technical solution of this embodiment, the exhaust channel 100 is located in the middle of the outline of the exhaust groove 200. Such an exhaust channel 100 has a larger effective exhaust area, and the problem of over-compression is more obviously suppressed. Specifically, in the technical solution of this embodiment, the exhaust channel 100 is located in the middle of the axial direction of the cylinder liner 10, and the exhaust grooves are symmetrically distributed along the plane of the exhaust channel 100 perpendicular to the axis of the cylinder liner 10.

[0046] like Figure 1 As shown, in the technical solution of this embodiment, the width of the exhaust groove 200 extending from the exhaust channel 100 to the direction away from the exhaust channel 100 gradually narrows. The above structure is designed after analyzing the flow factors of the exhaust gas. The gas is discharged through the exhaust channel 100. The gas gathers more near the exhaust channel 100. The different widths of the exhaust groove 200 make the gas near and far from the exhaust channel 100 tend to be balanced as much as possible.

[0047] like Figure 4 As shown, in the technical solution of this embodiment, the circumferential span angle of the exhaust groove 200 is α, and the value range of α is between 0° and 90°. The above structure can ensure that the piston head of the piston 20 has a sufficient length. At the same time, the pressure relief channel 300 is not connected to the intake channel during the pressure relief process. The exhaust groove circumferential starting angle β, the exhaust groove span angle α, and the piston head span angle γ.

[0048] like Figure 6 As shown, in the technical solution of this embodiment, the minimum distance between the exhaust groove 200 and the end surface of the cylinder sleeve 10 is L, and the value range of L is between 1mm and 10mm. The above structure can reduce leakage and ensure the strength of the pump body structure.

[0049] like Figure 1 As shown, in the technical solution of this embodiment, the cross-section of the exhaust groove 200 is in the shape of a circular arc cross-section or a rectangular cross-section. The above structure has a low processing cost. Specifically, in the technical solution of this embodiment, the cross-section of the exhaust groove 200 is in the shape of a circular arc cross-section, and the exhaust groove 200 of the above structure has a better buffering effect of the gas.

[0050] like Figure 1 As shown, in the technical solution of this embodiment, the cross-sectional width of the exhaust groove 200 is b, and b is greater than 0.5 mm. When the cross-sectional width b of the exhaust groove 200 is less than 0.5 mm, the over-compression phenomenon is not significantly reduced. Specifically, the depth of the exhaust groove 200 is h, and h is greater than 0.1 mm. Similarly, when the depth h of the exhaust groove 200 is less than 0.5 mm, the over-compression phenomenon is not significantly reduced.

[0051] like Figure 1As shown, in the technical solution of this embodiment, the cross-sectional area of the exhaust groove 200 is Si, and Si is greater than 0.05 mm2. When the cross-sectional area Si of the exhaust groove 200 is less than 0.05 mm2, the reduction of over-compression is not obvious.

[0052] As Figure 1 and Figure 7 shown, in the technical solution of this embodiment, the cross-sectional area of the head of the piston 20 is S, and Si and S satisfy 0.001 < Si / S < 0.5. Si / S cannot be too large, otherwise it will affect the exhaust and cause more compressed gas to remain in the exhaust groove 200. Si / S cannot be too small, otherwise its effect on over-compression is small.

[0053] As Figure 1 and Figure 7 shown, in the technical solution of this embodiment, the volume of the exhaust groove 200 is v, and the displacement of the pump body structure is V. v and V satisfy 0.1% < v / V < 2%. v / V cannot be too large, otherwise more compressed gas will remain in the exhaust groove 200, affecting the exhaust efficiency. v / V cannot be too small, otherwise its effect on over-compression is small.

[0054] This application also provides a rotating cylinder piston compressor. The rotating cylinder piston compressor includes a pump body assembly, and the pump body assembly is the above-mentioned pump body assembly. Specifically, there can be various types of rotating cylinder piston compressors, and the rotating cylinder piston compressor of this application can be a single-cylinder double-compression chamber structure.

[0055] The rotating shaft of the rotating cylinder compressor drives the piston to rotate, and the piston drives the cylinder to rotate. The piston only has relative reciprocating motion with respect to the rotating shaft and the cylinder, and the two reciprocating motions are perpendicular to each other. During this process, suction, compression, and exhaust are achieved.

[0056] The rotating cylinder compressor is of a single-cylinder double-compression chamber structure, and the two compression chambers are independent of each other. For a single volume chamber, the suction start angle is 0°, suction is completed from 0° to 180°, and compression and exhaust are completed from 180° to 360°. In addition, one volume chamber is misaligned by 180°. This means that when one volume chamber finishes suction and is about to enter the compression stage, the other volume chamber finishes exhaust and is about to enter the suction stage. Therefore, when setting the exhaust groove 200 on the piston head, it is necessary to avoid air leakage between the two volume chambers, which will affect the performance.

[0057] In the initial stage of exhaust, the exhaust area of the compression chamber is the sum of the areas of the main exhaust port and the pressure relief hole:

[0058] S = πd1 2 / 4 + πd2 2 / 4

[0059] d1 is the diameter of the main exhaust passage 100; d2 is the diameter of the pressure relief passage 300.

[0060] At the end of exhaust, since the radial distance from the head of the piston 20 to the inner circle of the cylinder liner 10 is continuously reduced, at this time, the exhaust area of ​​the compression chamber is linearly related to the sum of the radial distance from the head of the piston 20 to the cylinder liner 10 and the circumference of the exhaust port-pressure relief hole:

[0061] S=(πd1+πd2)×Δ

[0062] Δ is the radial distance from the head of the piston 20 to the inner circle of the cylinder liner 10 .

[0063] As the compression chamber gradually separates from the exhaust port, the overlapping area between the compression chamber and the exhaust port gradually decreases. At this time, the effective exhaust area S is:

[0064] S=δ×(πd1+πd2)×Δ

[0065] δ is the effective contact ratio (the ratio of the matching circumference of the piston 20 and the exhaust port to the total circumference of the exhaust port).

[0066] The calculation formula for defining the theoretical exhaust velocity v of a rotary compressor is as follows:

[0067] v=V' / S

[0068] V' is the volume change rate of the rotary cylinder compression chamber.

[0069] The starting angle of compression is defined as 0°, and the V' calculation formula is as follows:

[0070] V'=V×ω×sin(θ) / 4

[0071] V is the compressor displacement; ω is the angular velocity of the shaft rotation, and θ is the angle from the beginning of compression to the compression end at a certain moment.

[0072] In the whole exhaust stage, the effective exhaust area of ​​the compression chamber and the theoretical exhaust velocity change with the rotation angle as shown in Figure 8 As shown, the curve labeled 1 is the curve without the exhaust groove 200, and the curve labeled 2 is the curve with the exhaust groove 200. It can be clearly seen that at the exhaust end, the effective exhaust area of ​​the compression chamber gradually decreases, and the theoretical exhaust speed continues to increase; at this time, the corresponding exhaust resistance continues to increase, and the exhaust at the end has a large over-compression phenomenon, which seriously affects the energy efficiency of the compressor. It should be noted that Figure 8 The V on the vertical axis is the exhaust velocity.

[0073] According to the above analysis, when the operating conditions and operating frequency of the compressor are determined, the volume change rate V' is a constant. At this time, at the exhaust end, the effective exhaust area restricts the theoretical exhaust speed, while the overlapping circumference of the compression chamber and the exhaust system restricts the effective exhaust area.

[0074] The present application also provides an air conditioner, the air conditioner comprising a rotary cylinder piston compressor. The rotary cylinder piston compressor is the rotary cylinder piston compressor mentioned above.

[0075] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0076] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchangeable where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein, for example. In addition, the terms "including" and "having" and any of their variations are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units that are clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0077] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A pump body structure of a rotary cylinder piston compressor, characterized in that: include: A cylinder liner (10), wherein the cylinder liner (10) is provided with an intake channel, an exhaust channel (100) and an exhaust groove (200), wherein the exhaust groove (200) is opened on the inner wall of the cylinder liner (10), and the exhaust groove (200) is communicated with the exhaust channel (100) and extends in the direction of the inner wall of the exhaust chamber of the cylinder liner (10); The exhaust groove (200) is in an arc shape; The pump body structure further comprises a piston (20) and a cylinder (30), wherein the piston (20) is sleeved in the cylinder (30), and the cylinder (30) is sleeved in the cylinder sleeve (10), the contour line diameter of the exhaust groove (200) is d, the outer diameter of the cross section of the piston (20) is d1, and the value range of d is between 0.8d1 and 1.2d1; The cylinder liner (10) is also provided with a pressure relief channel (300), and the pressure relief channel (300) is located on a path where the piston (20) rotates from the exhaust channel (100) to the intake channel; The end of the exhaust groove (200) and the pressure relief channel (300) are located on the same plane perpendicular to the end surface of the cylinder liner (10); The exhaust channel (100) is located in the middle of the outline of the exhaust groove (200).

2. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The width of the exhaust groove (200) gradually narrows as it extends from the exhaust channel (100) to a direction away from the exhaust channel (100).

3. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The circumferential span angle of the exhaust groove (200) is α, and the value range of α is between 0° and 90°.

4. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The minimum distance between the exhaust groove (200) and the end surface of the cylinder sleeve (10) is L, and the value range of L is between 1 mm and 10 mm.

5. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The cross-section of the exhaust groove (200) is in the shape of a circular arc cross-section or a rectangular cross-section.

6. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The cross-sectional width of the exhaust groove (200) is b, and b is greater than 0.5 mm.

7. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The depth of the exhaust groove (200) is h, and h is greater than 0.1 mm.

8. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The cross-sectional area of ​​the exhaust groove (200) is Si, and the Si is greater than 0.05 mm 2 .

9. The pump body structure of the rotary piston compressor according to claim 8, characterized in that: The cross-sectional area of ​​the head of the piston (20) is S, and the Si and S satisfy 0.001 <Si / S<0.5。 10. The pump body structure of the rotary piston compressor according to claim 1, characterized in that: The volume of the exhaust groove (200) is v, the displacement of the pump structure is V, and v and V satisfy 0.1% <v / V<2%。 11. A rotary piston compressor, comprising a pump body structure, characterized in that: The pump body structure is the pump body structure according to any one of claims 1 to 10.

12. The rotary piston compressor according to claim 11, characterized in that: The rotary piston compressor has a single-cylinder dual-compression chamber structure.

13. An air conditioner comprising a rotary piston compressor, characterized in that: The rotary cylinder piston compressor is the rotary cylinder piston compressor according to claim 11 or claim 12.

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