A compressor double cylinder structure, a pump body assembly and a compressor

Abstract

This invention provides a dual-cylinder compressor structure, a pump assembly, and a compressor. The dual-cylinder compressor structure includes a first cylinder section and a second cylinder section arranged sequentially along an axial direction. The first cylinder section has a first compression chamber, and the second cylinder section has a second compression chamber. The dual-cylinder compressor structure has an intake groove penetrating both ends of the axial direction. The intake groove has a first segment located on the inner wall of the first compression chamber and a second segment located on the inner wall of the second compression chamber. An intake hole communicating with the intake groove is also provided on the outer peripheral wall of the dual-cylinder compressor structure. Both the first and second segments draw air through the intake hole. According to the technical solution of this invention, since the intake groove penetrates both ends of the dual-cylinder compressor structure along the axial direction, cutting can be performed directly along the axial direction of the dual-cylinder compressor structure during machining, completing the machining in one pass without the need for segmented machining, thus making machining more convenient and efficient.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, specifically relating to a dual-cylinder compressor structure, a pump assembly, and a compressor. Background Technology

[0002] Rotary twin-cylinder compressors typically require two suction pipes. The short distance between these pipes makes welding prone to failure, resulting in a high failure rate. The large number of parts required for machining, coupled with complex and time-consuming processes, complicates manufacturing and installation, increasing costs. This led to the development of single-suction compressor technology. However, with advancements in this technology, it was found that single-suction compressors are less energy-efficient than twin-suction compressors. This is primarily due to the reduced suction cross-sectional area, increased suction resistance, and insufficient suction, leading to decreased cooling capacity and consequently lower compressor efficiency.

[0003] Figure 1 A cross-sectional view of a conventional dual-cylinder single-intake pump assembly is shown. The dual-cylinder structure of this pump assembly includes an upper cylinder 5, a partition 6, and a lower cylinder 8. The upper cylinder 5 has a horizontal upper cylinder intake channel 26. The partition 6 has an inclined partition channel 27 communicating with the upper cylinder intake channel 26. The lower cylinder 8 has an inclined lower cylinder channel 28 communicating with the inclined partition channel 27. Refrigerant enters the compressor pump body through the intake port of the upper cylinder intake channel 26. Within the upper cylinder intake channel 26, the gas is split; part enters the upper cylinder 5 directly, and part flows through the inclined partition channel 27 and the inclined lower cylinder channel 28 into the lower cylinder 8. The inclined partition channel 27 and the inclined lower cylinder channel 28 are both designed with inclined holes, which makes machining inconvenient and reduces machining efficiency. Summary of the Invention

[0004] Therefore, the present invention provides a compressor with a dual-cylinder structure, a pump assembly, and a compressor, which can solve the technical problems of inconvenient processing and low processing efficiency caused by the inclined hole design of the inclined partition channel and the inclined lower cylinder channel in the prior art.

[0005] To solve the above problems, the present invention provides a compressor dual-cylinder structure, which includes a first cylinder section and a second cylinder section arranged sequentially along the axial direction, wherein the first cylinder section has a first compression chamber and the second cylinder section has a second compression chamber.

[0006] The compressor dual-cylinder structure has an intake groove that extends through both ends of the axial direction. The intake groove has a first groove section located on the inner wall of the first compression chamber and a second groove section located on the inner wall of the second compression chamber. The outer peripheral wall of the compressor dual-cylinder structure is also provided with an intake hole that communicates with the intake groove. Both the first groove section and the second groove section draw air through the intake hole.

[0007] In some embodiments, the air intake hole extends through the air intake groove, and an air outlet is formed on the groove wall of the air intake groove; wherein,

[0008] The partial opening area of ​​the air outlet is located on the first groove segment; and / or, the partial opening area of ​​the air outlet is located on the second groove segment.

[0009] In some embodiments, the compressor dual-cylinder structure is a one-piece molded structure.

[0010] In some embodiments, the compressor dual-cylinder structure has a compression chamber and a vane groove, both of which extend through the axial ends of the compressor dual-cylinder structure. The vane groove and the suction groove are both located on the sidewall of the compression chamber. Specifically, the portion of the compression chamber located on the first cylinder portion forms the first compression chamber, and the portion located on the second cylinder portion forms the second compression chamber. The portion of the vane groove located on the first cylinder portion forms the first vane groove, and the portion located on the second cylinder portion forms the second vane groove. The compressor dual-cylinder structure is provided with a separator, which separates the first vane groove and the second vane groove, and also separates the first compression chamber and the second compression chamber.

[0011] The separator is detachable.

[0012] In some embodiments, the compression chamber and the vane groove together form a groove structure, the groove structure having openings at both axial ends of the compressor's twin-cylinder structure, and the separator being fitted inside the groove structure and being detachable from the openings.

[0013] In some embodiments, the separator includes a first partition and a second partition, the first partition being located within the slide groove to separate the first slide groove and the second slide groove; the second partition being located within the compression chamber to separate the first compression chamber and the second compression chamber.

[0014] The first partition is used to position the second partition both circumferentially and axially.

[0015] In some embodiments, the second partition has opposing first and second ends in the axial direction of the compressor twin-cylinder structure;

[0016] The outer wall of the second partition is provided with a circumferential positioning groove that extends from the first end to the second end. One end of the first partition is inserted into the circumferential positioning groove to position the second partition circumferentially.

[0017] In some embodiments, the outer sidewall of the second partition is provided with axial positioning grooves at both ends of the compressor twin-cylinder structure in the axial direction, and the first partition is provided with a first positioning protrusion and a second positioning protrusion; the first partition is inserted into one of the axial positioning grooves through the first positioning protrusion and into the other axial positioning groove through the second positioning protrusion, so as to position the second partition in the axial direction.

[0018] In some embodiments, when the second partition has a first end and a second end opposite to each other in the axial direction of the compressor twin-cylinder structure, and the outer side wall of the second partition is provided with a circumferential positioning groove extending from the first end to the second end, and one end of the first partition is inserted into the circumferential positioning groove to position the second partition circumferentially, the two axial positioning grooves are located at both ends of the circumferential positioning groove.

[0019] In some embodiments, a sealing ring is fitted between the second partition and the inner wall of the compression chamber; or, the second partition and the inner wall of the compression chamber are sealed by an interference fit.

[0020] The present invention also provides a pump body assembly comprising the compressor dual-cylinder structure described in any one of the above-described embodiments.

[0021] The present invention also provides a compressor comprising the compressor dual-cylinder structure described in any one of the above descriptions; or comprising the pump assembly described above.

[0022] The present invention provides a compressor with a dual-cylinder structure, a pump assembly, and a compressor, which have the following beneficial effects:

[0023] 1. Because the existing inclined partition channel and inclined lower cylinder channel are both designed with inclined holes, and these inclined holes do not penetrate both ends of the axial direction of the compressor's double-cylinder structure, segmented machining is required, making the process complex and resulting in low machining efficiency. In this invention, by using a suction groove to replace the existing inclined partition channel and inclined lower cylinder channel, since the suction groove penetrates both ends of the compressor's double-cylinder structure, cutting can be performed directly along the axial direction of the compressor's double-cylinder structure during machining, completing the process in one pass without segmented machining. This makes machining more convenient and increases efficiency.

[0024] 2. By directly connecting the first and second slot sections to the air intake, the present invention reduces the magnitude of the change in airflow direction when flowing into the first slot section, thereby significantly reducing gas impact loss and channel vortex loss caused by the change in fluid flow direction, which is beneficial to improving the energy efficiency of the compressor. Attached Figure Description

[0025] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0026] Figure 1 This is a cross-sectional view of a conventional dual-cylinder single-intake pump assembly;

[0027] Figure 2 yes Figure 1 Another cross-sectional view of a conventional dual-cylinder single-intake air pump assembly;

[0028] Figure 3 This is a cross-sectional view of the pump body assembly of the present invention;

[0029] Figure 4 yes Figure 3 Another sectional view of the pump body assembly;

[0030] Figure 5 This is a schematic diagram of the dual-cylinder compressor structure of the present invention;

[0031] Figure 6 yes Figure 5 Sectional view along the BB direction;

[0032] Figure 7 yes Figure 5 Sectional view along the middle AA direction;

[0033] Figure 8 This is a schematic diagram of the structure of a first partition provided in an embodiment of the present invention;

[0034] Figure 9 yes Figure 8 Sectional view along the DD direction;

[0035] Figure 10 This is a schematic diagram of the structure of a second partition provided in an embodiment of the present invention;

[0036] Figure 11 yes Figure 10 A cross-sectional view along the CC direction;

[0037] Figure 12 This is a schematic diagram of the pump body assembly when the second partition plate of the present invention is interference-fitted with the compression chamber;

[0038] Figure 13 This is a cross-sectional view of the second partition plate of the present invention when it is interference-fitted with the compression chamber;

[0039] Figure 14 yes Figure 13Top view of the second partition.

[0040] The attached figures are labeled as follows:

[0041] 1. Crankshaft; 2. First flange; 3. First muffler; 4. First roller; 5. Upper cylinder; 6. Partition plate; 7. Second roller; 8. Lower cylinder; 9. Second flange; 10. Second muffler; 11. First vane; 12. Second vane; 13. Compressor twin-cylinder structure; 14. Second partition plate; 15. First partition plate; 16. Sealing ring; 17. Annular groove; 18. Circumferential positioning groove; 19. Axial positioning groove; 20. First positioning protrusion; 21. Second positioning protrusion; 22. Compression chamber; 23. Intake groove; 24. Vane groove; 25. 25a, First opening area; 25b, Second opening area; 26, Upper cylinder intake passage; 27, Inclined partition passage; 28, Inclined lower cylinder passage; 131, First cylinder section; 132, Second cylinder section; 141, First end; 142, Second end; 145, Separator; 151, One end of the first partition; 221, First compression chamber; 222, Second compression chamber; 224, Tank structure; 231, First tank section; 232, Second tank section; 241, First vane groove; 242, Second vane groove; 251, Air outlet. Detailed Implementation

[0042] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0043] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0044] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0045] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0046] See also Figure 3-7 As shown, according to an embodiment of the present invention, a compressor dual-cylinder structure 13 is provided, which includes a first cylinder section 131 and a second cylinder section 132 arranged sequentially along the axial direction. The first cylinder section 131 has a first compression chamber 221, and the second cylinder section 132 has a second compression chamber 222. The compressor dual-cylinder structure 13 has an intake groove 23 extending through both ends of the axial direction. The intake groove 23 has a first groove segment 231 located on the inner wall of the first compression chamber 221 and a second groove segment 232 located on the inner wall of the second compression chamber 222. An intake hole 25 communicating with the intake groove 23 is also provided on the outer peripheral wall of the compressor dual-cylinder structure 13. Both the first groove segment 231 and the second groove segment 232 draw in air through the intake hole 25.

[0047] The suction groove 23 and suction hole 25 mentioned above work together to form the suction channel of the compressor double cylinder structure 13 of the present invention. The suction hole 25 can be processed along the radial direction of the compressor double cylinder structure 13, and the suction groove 23 can be processed along the axial direction of the compressor double cylinder structure 13.

[0048] Because the inclined partition channel 27 and inclined lower cylinder channel 28 in the prior art are both inclined hole designs, and these inclined holes do not penetrate through both axial ends of the compressor double-cylinder structure 13, segmented processing is required, which is more complex and results in lower processing efficiency. In this invention, by using a suction groove 23 to replace the inclined partition channel 27 and inclined lower cylinder channel 28 in the prior art, since the suction groove 23 penetrates through both axial ends of the compressor double-cylinder structure, cutting can be performed directly along the axial direction of the compressor double-cylinder structure 13 during processing, and the process can be completed in one step without segmented processing, thus making processing more convenient and more efficient.

[0049] In some implementations, such as Figure 3 As shown, the aforementioned intake groove 23 can be a straight groove extending along the axial direction of the compressor's twin-cylinder structure 13, which can further facilitate processing and improve processing efficiency.

[0050] In some implementations, such as Figure 3 As shown, the aforementioned intake port 25 can be a straight hole extending radially along the compressor's twin-cylinder structure 13, which facilitates machining.

[0051] In some implementations, such as Figure 3 As shown, the aforementioned suction hole 25 penetrates the suction groove 23, and an air outlet 251 is formed on the groove wall of the suction groove 23. A portion of the opening area of ​​the air outlet 251 is located on the first groove segment 231. For distinction from the following text, the opening area of ​​the air outlet 251 located on the first groove segment 231 is referred to as the first opening area 25a (i.e.,...). Figure 3 (The area indicated by the dashed box in section 25a) allows gas from outlet 251 to directly enter the first slot section 231 through this first opening area 25a. This design allows the first slot section 231 to directly connect with the intake port 25, thus reducing the magnitude of the change in airflow direction as it flows into the first slot section 231. This significantly reduces gas impact losses and channel vortex losses caused by changes in fluid direction, thereby improving the compressor's energy efficiency.

[0052] In some implementations, such as Figure 3 As shown, a portion of the opening area of ​​the aforementioned air outlet 251 is located on the second groove section 232. To distinguish it from the above, the opening area of ​​the air outlet 251 located on the second groove section 232 is referred to as the second opening area 25b (i.e.,...). Figure 3(The area indicated by the dashed box in section 25b) allows gas from outlet 251 to directly enter the second slot section 232 through this second opening area 25b. This design allows the second slot section 232 to directly connect with the intake port 25, thus reducing the magnitude of the change in airflow direction as it flows into the second slot section 232. This significantly reduces gas impact losses and channel vortex losses caused by changes in fluid direction, thereby improving the compressor's energy efficiency.

[0053] In some embodiments, the aforementioned compressor twin-cylinder structure 13 can be a one-piece molded structure.

[0054] Among them, such as Figure 1-2 As shown, the existing compressor dual-cylinder structure is a split structure, consisting of an upper cylinder 5, a lower cylinder 8, and a partition 6. Figure 3-4 As shown, the compressor dual-cylinder structure 13 of the present invention is an integrally formed structure. It uses a single cylinder structure to replace the upper cylinder 5 and lower cylinder 8 in the prior art, which reduces the processing of at least one cylinder part. In actual production and processing, both material costs and machining costs will be reduced.

[0055] In some implementations, such as Figure 5-7 As shown, the aforementioned compressor dual-cylinder structure 13 has a compression chamber 22 and a vane groove 24. Both the compression chamber 22 and the vane groove 24 extend through both axial ends of the compressor dual-cylinder structure 13, and the vane groove 24 and the aforementioned intake groove 23 are both disposed on the side wall of the compression chamber 22. Specifically, the portion of the compression chamber 22 located on the first cylinder portion 131 forms the aforementioned first compression chamber 221, and the portion of the compression chamber 22 located on the second cylinder portion 132 forms the aforementioned second compression chamber 222. The portion of the vane groove 24 located on the first cylinder portion 131 forms the first vane groove 241, and the portion located on the second cylinder portion 132 forms the second vane groove 242. Figure 4 As shown, the compressor dual-cylinder structure 13 of the present invention is provided with a separator 145. The separator 145 is used to separate the first vane groove 241 and the second vane groove 242, and also to separate the first compression chamber 221 and the second compression chamber 222. Through the separation by the separator 145, the first vane groove 241, the second vane groove 242, the first compression chamber 221, and the second compression chamber 222 can all operate normally.

[0056] In the above example, since both the compression chamber 22 and the vane groove 24 pass through both axial ends of the compressor double-cylinder structure 13, they are easy to process.

[0057] In some embodiments, the aforementioned separator 145 is detachable, thus providing the technical advantage of easy disassembly and maintenance.

[0058] It should be noted that in some other examples, the aforementioned separator 145 can be integrally formed on the aforementioned compressor twin-cylinder structure 13.

[0059] To achieve the aforementioned technical effect of detachable separator 145, in some embodiments, such as Figure 5 As shown, the aforementioned compression chamber 22 and vane groove 24 together form a groove structure 224, which has openings at both axial ends of the compressor twin-cylinder structure 13. The aforementioned separator 145 is used to fit inside the groove structure 224 and can be disassembled and assembled from the openings at both ends of the groove structure 224.

[0060] In some implementations, such as Figure 4 As shown, the aforementioned separator 145 may include a first separator 15 and a second separator 14. The first separator 15 is located within the vane groove 24 to separate the first vane groove 241 and the second vane groove 242. The second separator 14 is located within the compression chamber 22 to separate the first compression chamber 221 and the second compression chamber 222. The first separator 15 is used to position the second separator 14 both circumferentially and axially to prevent the second separator 14 from moving in either direction and affecting the operation of the first compression chamber 221 and the second compression chamber 222.

[0061] The aforementioned first sliding groove 241 is used to install the first sliding piece 11, and the second sliding groove 242 is used to install the second sliding piece 12. The first partition 15 also serves to support the first sliding piece 11 and the second sliding piece 12. In some cases, the first partition 15 can also be referred to as a sliding piece bracket.

[0062] To achieve the effect of the first partition 15 positioning the second partition 14 circumferentially, in some embodiments, such as Figure 10-11 As shown, the aforementioned second partition 14 has a first end 141 and a second end 142 opposite each other in the axial direction of the compressor twin-cylinder structure 13. A circumferential positioning groove 18 is provided on the outer wall of the second partition 14, extending from the first end 141 to the second end 142. (See diagram below.) Figure 4 As shown, one end of the first partition 15 is inserted into the circumferential positioning groove 18 to position the second partition 14 circumferentially.

[0063] In the above example, the end of the first partition 15 is inserted into the circumferential positioning groove 18 on the outer side wall of the second partition 14, which can achieve the effect of the first partition 15 positioning the second partition 14 circumferentially.

[0064] To achieve the effect of axially positioning the second partition 14 by the first partition 15, in some embodiments, such as... Figure 8-11As shown, the outer wall of the aforementioned second partition 14 is provided with axial positioning grooves 19 at both ends of the compressor twin-cylinder structure 13 in the axial direction. The first partition 15 is provided with a first positioning protrusion 20 and a second positioning protrusion 21. The first partition 15 is inserted into one axial positioning groove 19 through the first positioning protrusion 20 and into the other axial positioning groove 19 through the second positioning protrusion 21, so as to position the second partition 14 axially.

[0065] In the above example, the first positioning protrusion 20 is inserted into an axial positioning groove 19 on the outer wall of the second partition 14, thereby limiting the axial movement of the second partition 14 on one side. The second positioning protrusion 21 is inserted into another axial positioning groove 19 on the outer wall of the second partition 14, thereby limiting the axial movement of the second partition 14 on the other side. The cooperation of the first positioning protrusion 20 and the second positioning protrusion 21 allows for axial positioning of the second partition 14, preventing axial movement of the second partition 14.

[0066] In some implementations, such as Figure 10-11 As shown, when the second partition 14 has a first end 141 and a second end 142 opposite to each other in the axial direction of the compressor twin-cylinder structure 13, and the outer side wall of the second partition 14 is provided with a circumferential positioning groove 18 extending from the first end 141 to the second end 142, and one end of the first partition 15 is inserted into the circumferential positioning groove 18 to position the second partition 14 circumferentially, the aforementioned two axial positioning grooves 19 can be located at both ends of the circumferential positioning groove 18, so that the first partition 15 can simultaneously position the second partition 14 circumferentially and axially from the same side.

[0067] In one example, such as Figure 4 As shown, a sealing ring 16 can be fitted between the aforementioned second partition 14 and the inner wall of the compression chamber 22 to prevent air leakage between the first compression chamber 221 and the second compression chamber 222. The sealing ring 16 can be a rubber sealing ring, etc. Figure 11 As shown, an annular groove 17 may be provided on the side wall of the second partition 14, and the sealing ring 16 may be fitted inside the annular groove 17.

[0068] In another example, such as Figure 12-14 As shown, the aforementioned second partition 14 and the inner wall of the compression chamber 22 can also be sealed by an interference fit, which can also achieve the effect of preventing gas leakage between the first compression chamber 221 and the second compression chamber 222. In this other example, to facilitate the interference fit between the second partition 14 and the inner wall of the compression chamber 22, a heating compressor twin-cylinder structure 13 or a refrigeration second partition 14 can be selected during assembly.

[0069] The present invention also provides a pump body assembly comprising the compressor dual-cylinder structure 13 described above. Because the pump body assembly uses the compressor dual-cylinder structure 13, the inclined partition channel 27 and inclined lower cylinder channel 28 in the prior art are both inclined hole designs, and these inclined holes do not penetrate both axial ends of the compressor dual-cylinder structure 13, thus requiring segmented processing, which is complex and results in low processing efficiency. In the present invention, by using a suction groove 23 to replace the inclined partition channel 27 and inclined lower cylinder channel 28 in the prior art, since the suction groove 23 penetrates both axial ends of the compressor dual-cylinder structure, cutting can be performed directly along the axial direction of the compressor dual-cylinder structure 13 during processing, completing the process in one step without segmented processing, thus making processing more convenient and more efficient.

[0070] like Figure 3 and Figure 4 As shown, the pump body assembly of the present invention further includes a crankshaft 1, a first flange 2, a first silencer 3, a first roller 4, a second roller 7, a second flange 9, a second silencer 10, a first vane 11, and a second vane 12. The first vane 11 is used to be installed in the first vane groove 241, and the second vane 12 is used to be installed in the second vane groove 242. The first flange 2 can be an upper flange, the first silencer 3 can be an upper silencer, the first roller 4 can be an upper roller, the second roller 7 can be a lower roller, the second flange 9 can be a lower flange, and the second silencer 10 can be a lower silencer. The aforementioned compression chamber 22, vane groove 24, and suction groove 23 form a first groove structure, which penetrates both axial ends of the compressor double-cylinder structure 13. The first groove structure has a first opening at one axial end of the compressor double-cylinder structure 13 and a second opening at the other axial end of the compressor double-cylinder structure 13. The aforementioned first flange 2 covers the first opening to allow the first compression chamber 221 to operate normally. The second flange 9 seals the second opening to allow the second compression chamber 222 to operate normally. The refrigerant enters the compressor's dual-cylinder structure 13 through the suction port 25, and is split at the outlet 251 at the tail end of the suction port 25, flowing into the first compression chamber 221 and the second compression chamber 222 respectively, ensuring that both chambers have the same intake volume. Meanwhile, compared to the two independent cylinders of a traditional split compressor, whose suction port diameter is limited, this invention innovatively uses a single integrated compressor dual-cylinder structure 13 to supply air to both the first and second compression chambers 221. Furthermore, the diameter of the suction port 25 has a larger margin compared to existing two independent, short cylinders, and the cross-sectional area of ​​the suction port 25 can be significantly increased. For example, the diameter of the suction port 25 can be increased from 12mm to 14mm, increasing the cross-sectional area by 36%, thereby raising the upper limit of the suction port 25's diameter.

[0071] This invention replaces the upper cylinder 5, partition 6, and lower cylinder 8 of the traditional solution with an integrated compressor dual-cylinder structure 13 and a separator 145. This not only saves on the number of parts but also ensures the coaxiality of the first compression chamber 221 and the second compression chamber 222. A single machining operation saves on processing costs and improves production efficiency. Compared to the traditional solution, the outer diameter of the second partition 14 in this invention is reduced, resulting in a gap and lack of support between the first sliding vane 11 in the first sliding vane groove 241 and the second sliding vane 12 in the second sliding vane groove 242. Therefore, a first partition 15 is designed to ensure that the first sliding vane 11 is within the first sliding vane groove 241 and that the second sliding vane 12 is within the second sliding vane groove 242.

[0072] The pump body assembly of the present invention can be assembled as follows: First, the sealing ring 16 is assembled into the annular groove 17 of the second partition 14. Then, the first partition 15 and the second partition 14 are assembled together, with the first partition 15 embedded into the circumferential positioning groove 18 of the second partition 14. The first positioning protrusion 20 and the second positioning protrusion 21 on the first partition 15 are respectively inserted into the corresponding axial positioning grooves 19 on the second partition 14. The first partition 15 and the second partition 14, once assembled, form the aforementioned partition 145, which may sometimes be referred to as a partition slide bracket assembly. During assembly, either the first compression chamber 221 or the second compression chamber 222 can be assembled first; this example illustrates the assembly of the first compression chamber 221. First, the first flange 2 and the first muffler 3 are assembled onto the compressor twin-cylinder structure 13. Then, the crankshaft 1 and the first roller 4 are installed. The first vane 11 is installed in the first vane groove 241. Next, the separator 145 is installed. In this step, the first partition 15 of the separator 145 is installed from the opening of the vane groove 24, and the second partition 14 is installed from the opening of the compression chamber 22. The first partition 15 of the separator 145 presses against the first vane 11. The compression chamber 22 restricts the translation of the second partition 14 in the horizontal and vertical directions, as well as its rotation in the horizontal and vertical directions. The first partition 15 is constrained by the first vane 11 and the second vane 12. The first partition 15 restricts the axial translation and rotation of the second partition 14. Thus, all six degrees of freedom of the second partition 14 are restricted. Then, the second roller 7 and the second vane 12 are assembled, followed by the second flange 9 and the second silencer 10. Finally, the centering and locking screws are tightened on the automatic centering machine, thus completing the assembly of the pump body assembly.

[0073] This invention also provides a compressor comprising the compressor dual-cylinder structure 13 described above; or comprising the pump assembly described above. Because the compressor employs the aforementioned compressor dual-cylinder structure 13 or pump assembly, the inclined partition channel 27 and inclined lower cylinder channel 28 in the prior art are both inclined hole designs, and these inclined holes do not penetrate both axial ends of the compressor dual-cylinder structure, thus requiring segmented processing, which is complex and results in low processing efficiency. In this invention, by using a suction groove 23 to replace the inclined partition channel 27 and inclined lower cylinder channel 28 in the prior art, since the suction groove 23 penetrates both axial ends of the compressor dual-cylinder structure 13, cutting can be performed directly along the axial direction of the compressor dual-cylinder structure 13 during processing, completing the process in one step without segmented processing, thus making processing more convenient and more efficient.

[0074] like Figure 1 and Figure 2 In the production of compressor pump body parts, the main components of a twin-cylinder single-suction compressor pump body include a crankshaft 1, a first flange 2, a first silencer 3, a first roller 4, an upper cylinder 5, a partition 6, a second roller 7, a second flange 9, a second silencer 10, a first vane 11, and a second vane 12. The upper cylinder 5, lower cylinder 8, and partition 6 all have inclined or vertical gas channels. Machining this channel, which runs through the upper and lower cylinders and partition 6, requires not only ensuring the position of the channel on these three components but also addressing the issue of inclined holes, making this machining process costly. Figure 3 and Figure 4This invention replaces the upper cylinder 5 and lower cylinder 8 in the prior art with a single cylinder structure, and replaces the partition 6 with a gas passage in the prior art with a partition 145 without a gas passage. Roughly estimated, this saves all the processing costs in the cylinder manufacturing process and reduces the processing cost of the partition 6 hole, accounting for approximately 25% of the pump body cost. In this invention, the compressor's dual-cylinder structure 13 is machined in a single step. The first compression chamber 221 and the second compression chamber 222 share a sliding vane groove 24, ensuring higher symmetry between the first cylinder section 131 and the second cylinder section 132. Since the first cylinder section 131 and the second cylinder section 132 share the same cylinder inner circle (i.e., the aforementioned compression chamber 22), they can achieve higher coaxiality compared to the upper and lower cylinders of a traditional split-type dual-cylinder compressor. Compared to the traditional split-type dual-cylinder + partition 6 layout, where the intake port diameter is limited by the thickness of the component regardless of its location, the thickness of the integrated dual-cylinder structure of this invention is more than doubled while maintaining the same compression chamber geometry. This significantly increases the upper limit of the intake port diameter of the compressor dual-cylinder structure 13. For example, increasing the diameter from 12mm to 14mm increases the intake port cross-sectional area by 36%, thus raising the upper limit of the intake port diameter. Moreover, compared to the separate air supply of traditional dual cylinders, the intake port 25 of the compressor dual-cylinder structure 13 of this invention directly connects to the intake side of the first compression chamber 221 and the second compression chamber 222, greatly reducing gas impact losses and channel eddy current losses caused by the change in fluid movement direction due to the opening of the flow channel.

[0075] The compressor dual-cylinder structure 13 of this invention is a dual-cylinder single-suction structure, which can take into account the suction volume of both the first cylinder section 131 and the second cylinder section 132; at the same time, when the suction resistance is at a similar level, it reaches or even exceeds the suction volume of a dual-cylinder dual-suction compressor. The technical solution of this invention can simplify the pump body parts of the dual-cylinder compressor, reduce the processing steps of the dual-cylinder compressor, and improve production efficiency. It can reduce costs while enabling the dual-cylinder single-suction compressor to achieve the suction volume of a dual-cylinder dual-suction compressor. In particular, it can overcome the inherent disadvantage of insufficient lower cylinder suction when the dual-cylinder single-suction compressor operates at high flow rate compared to the dual-cylinder dual-suction compressor, narrow the high-frequency energy efficiency gap between single-suction and dual-suction compressors, improve the energy efficiency of the dual-cylinder single-suction compressor, and further amplify the cost advantage of single-suction compressors. It has the advantages of low cost of dual-cylinder single-suction compressors and relatively higher energy efficiency of dual-cylinder dual-suction compressors, providing more options in the product development process where the demand for cost reduction and efficiency improvement is increasing.

[0076] Compared to the dual-cylinder single-intake structure, the present invention achieves the same intake effect in the dual-cylinder dual-intake structure, regardless of whether the intake port 25 is located in the first cylinder section 131 or the second cylinder section 132.

[0077] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0078] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A compressor with a twin-cylinder structure (13), characterized in that: The compressor includes a first cylinder section (131) and a second cylinder section (132) arranged sequentially along the axial direction. The first cylinder section (131) has a first compression chamber (221), and the second cylinder section (132) has a second compression chamber (222). The compressor dual-cylinder structure (13) has an intake groove (23) extending through both ends of the axial direction. The intake groove (23) has a first groove segment (231) located on the inner wall of the first compression chamber (221) and a second groove segment (232) located on the inner wall of the second compression chamber (222). The outer peripheral wall of the compressor dual-cylinder structure (13) is also provided with an intake hole (25) communicating with the intake groove (23). Both the first groove segment (231) and the second groove segment (232) draw air through the intake hole (25). The compressor dual-cylinder structure (13) is an integrally formed structure; the compressor dual-cylinder structure (13) has a compression chamber (22) and a vane groove (24), the compression chamber (22) and the vane groove (24) both penetrate through the axial ends of the compressor dual-cylinder structure (13), and the vane groove (24) and the suction groove (23) are both provided on the side wall of the compression chamber (22); wherein, the portion of the compression chamber (22) located on the first cylinder part (131) forms the first compression chamber (221), and the portion located on the second cylinder part (132) forms the second compression chamber (221). Compression chamber (222); the portion of the vane groove (24) located on the first cylinder part (131) forms a first vane groove (241), and the portion located on the second cylinder part (132) forms a second vane groove (242); the compressor dual-cylinder structure (13) is provided with a separator (145), the separator (145) is used to separate the first vane groove (241) and the second vane groove (242), and the separator (145) is also used to separate the first compression chamber (221) and the second compression chamber (222); wherein, the separator (145) is detachable; The compression chamber (22) and the vane groove (24) together form a groove structure (224). The groove structure (224) has openings at both ends of the axial direction of the compressor double cylinder structure (13). The separator (145) is used to be fitted inside the groove structure (224) and can be disassembled from the opening.

2. The compressor twin-cylinder structure (13) according to claim 1, characterized in that: The air intake hole (25) extends through the air intake groove (23), and an air outlet (251) is formed on the groove wall of the air intake groove (23); wherein, A portion of the opening area of ​​the air outlet (251) is located on the first groove segment (231); and / or, a portion of the opening area of ​​the air outlet (251) is located on the second groove segment (232).

3. The compressor twin-cylinder structure (13) according to claim 1, characterized in that: The separator (145) includes a first partition (15) and a second partition (14). The first partition (15) is located in the slide groove (24) to separate the first slide groove (241) and the second slide groove (242). The second partition (14) is located in the compression chamber (22) to separate the first compression chamber (221) and the second compression chamber (222). The first partition (15) is used to position the second partition (14) both circumferentially and axially.

4. The compressor twin-cylinder structure (13) according to claim 3, characterized in that: The second partition (14) has a first end (141) and a second end (142) opposite each other in the axial direction of the compressor twin-cylinder structure (13); The outer side wall of the second partition (14) is provided with a circumferential positioning groove (18) extending from the first end (141) to the second end (142). One end of the first partition (15) is inserted into the circumferential positioning groove (18) to position the second partition (14) circumferentially.

5. The compressor twin-cylinder structure (13) according to claim 3, characterized in that: The outer sidewall of the second partition (14) is provided with axial positioning grooves (19) at both ends of the compressor twin-cylinder structure (13) in the axial direction. The first partition (15) is provided with a first positioning protrusion (20) and a second positioning protrusion (21). The first partition (15) is inserted into one of the axial positioning grooves (19) through the first positioning protrusion (20) and into the other axial positioning groove (19) through the second positioning protrusion (21) to position the second partition (14) in the axial direction.

6. The compressor twin-cylinder structure (13) according to claim 5, characterized in that: When the second partition (14) has a first end (141) and a second end (142) opposite each other in the axial direction of the compressor twin-cylinder structure (13), and the outer side wall of the second partition (14) is provided with a circumferential positioning groove (18) extending from the first end (141) to the second end (142), and one end (151) of the first partition (15) is inserted into the circumferential positioning groove (18) to position the second partition (14) circumferentially, the two axial positioning grooves (19) are located at both ends of the circumferential positioning groove (18).

7. The compressor twin-cylinder structure (13) according to claim 3, characterized in that: A sealing ring (16) is fitted between the second partition (14) and the inner wall of the compression chamber (22); or, the second partition (14) and the inner wall of the compression chamber (22) are sealed by an interference fit.

8. A pump body assembly, characterized in that: The compressor includes a twin-cylinder structure (13) as described in any one of claims 1-7.

9. A compressor, characterized in that: It includes the compressor twin-cylinder structure (13) of any one of claims 1-7; or includes the pump assembly of claim 8.

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