Double-cylinder rolling rotor compressor

Abstract

The application provides a double-cylinder rolling rotor compressor, which comprises two cylinders and a middle plate, one of the cylinders has an upper cylinder cover, the other cylinder has a lower cylinder cover, the two cylinders are separated by the middle plate, pistons are arranged in the two cylinders, at least one of the cylinders is provided with an air inlet hole, the compressor further comprises a suction flow channel which penetrates through the middle plate, the two ends of the suction flow channel are communicated with the two cylinders respectively, the flow area of the air inlet hole is S, the flow area of the suction flow channel is S1, the inner diameter of the cylinder provided with the air inlet hole is D1, the axial height of the cylinder is H1, the outer diameter of the piston is D2, and the unit volume refrigerating capacity of the compressor is q, so that the flow area S of the air inlet hole and the flow area S1 of the suction flow channel satisfy the following relationship: The application adjusts the flow areas of the suction and exhaust structures comprehensively, improves the resistance on the refrigerant flow path, improves the refrigerant backflow, increases the refrigerating capacity, and finally realizes the significant improvement of the APF performance of the compressor.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and in particular to a dual-cylinder rolling rotor compressor. Background Technology

[0002] The Annual Performance Factor (APF) of an air conditioner refers to its energy efficiency ratio, which is the ratio of its cooling or heating efficiency to its energy consumption. A higher APF value indicates higher energy efficiency, meaning the air conditioner saves electricity and consumes less energy for the same cooling or heating effect, thus reducing energy consumption and environmental pollution. The Coefficient of Performance (COP) is an important indicator of compressor energy efficiency, reflecting the amount of cooling or heating the compressor can provide per unit of energy consumption. A higher COP value indicates higher energy utilization efficiency.

[0003] The overall performance of the compressor is affected differently by the size of the gas flow channel area under different pump structures and refrigerant conditions, requiring targeted structural design. Each component's size and style has an optimal range. Simultaneously, the flow area of ​​the suction and exhaust channels plays a crucial role in compressor performance. Optimizing only the suction or exhaust channel has limited effect on improving the overall compressor efficiency; a comprehensive approach is needed. Therefore, this invention aims to improve the COP under various operating conditions by comprehensively adjusting the size of the suction and exhaust channels, exhaust ports, etc., ultimately achieving a significant improvement in the compressor's APF performance. Summary of the Invention

[0004] The purpose of this invention is to provide a dual-cylinder rolling rotor compressor that improves the COP (compressor performance coefficient) under various operating conditions by comprehensively adjusting the size of the intake air passage, intake port, exhaust refrigerant passage, exhaust port and muffler outlet port, and ultimately achieves a significant improvement in the compressor's APF (annual energy consumption rate) performance.

[0005] To achieve the above objectives, the present invention provides a dual-cylinder rolling rotor compressor, characterized in that it includes two cylinders and an intermediate plate, one of the cylinders having an upper cylinder cover and the other cylinder having a lower cylinder cover, the two cylinders being separated by the intermediate plate, each cylinder having a piston, at least one cylinder having an air inlet, and the compressor further including a suction passage penetrating the intermediate plate, each end of the suction passage communicating with one of the cylinders, the air inlet being used to draw refrigerant into the dual-cylinder rolling rotor compressor.

[0006] Let the flow area of ​​the air inlet be S, the flow area of ​​the air intake channel be S1, the inner diameter of the cylinder with the air inlet be D1, the axial height of the cylinder be H1, the outer diameter of the piston be D2, and the unit volume cooling capacity of the compressor be q. Then, the flow area S of the air inlet and the flow area S1 of the air intake channel should satisfy the following relationship:

[0007]

[0008] Optionally, the compressor further includes an exhaust refrigerant flow channel, which axially passes through the upper cylinder head, the two cylinders, the intermediate plate, and the lower cylinder head. The flow area of ​​the exhaust refrigerant flow channel is S2, such that the ratio of the flow area S1 of the intake flow channel to the flow area S2 of the exhaust refrigerant flow channel is not less than 0.6 and not greater than 2.2.

[0009] Optionally, the upper cylinder head is provided with an exhaust port communicating with one of the cylinders, and / or the lower cylinder head is provided with an exhaust port communicating with another cylinder, wherein the flow area of ​​the exhaust port is S3, such that the ratio of the flow area S1 of the intake channel to the flow area S3 of the exhaust port is not less than 2.03 and not greater than 4.4.

[0010] Optionally, the compressor further includes a first silencer and a second silencer, wherein the first silencer and / or the second silencer are provided with a silencer outlet, and the flow area of ​​the silencer outlet is S4, such that the ratio of the flow area S1 of the suction channel to the flow area S4 of the silencer outlet is not less than 0.9 and not greater than 5.24.

[0011] Optionally, the two cylinders have the same inner diameter, the same axial height, and the same outer diameter of the pistons in the two cylinders.

[0012] Optionally, when there are two or more exhaust refrigerant channels, S2 is the sum of the flow areas of all the exhaust refrigerant channels.

[0013] Optionally, the dual-cylinder rolling rotor compressor has two exhaust ports with the same flow area.

[0014] Optionally, the portion of the intake channel within the cylinder that connects to the air inlet is segmented, with one segment of the channel near the air inlet inclined to the cylinder axis and the other segment near the intermediate plate parallel to the cylinder axis.

[0015] Optionally, the extension direction of the portion of the intake passage within the cylinder that connects to the intake port is inclined to the cylinder axis.

[0016] Optionally, the intake passage located inside the cylinder, in the portion connecting to the intake port, extends through the side wall of the cylinder.

[0017] As described above, this invention derives the optimal range of values ​​for the flow area of ​​the inlet and the flow area of ​​the suction channel under certain cylinder inner diameter, cylinder axial height, piston outer diameter, and compressor unit volume cooling capacity. It also derives the optimal range of values ​​for the flow area of ​​the exhaust refrigerant channel, the exhaust port, and the muffler outlet. It is understood that the flow area of ​​the above-mentioned suction and exhaust structures is directly related to their cross-sectional dimensions. In summary, this invention, by comprehensively adjusting the sizes of the suction channel, inlet, exhaust refrigerant channel, exhaust port, and muffler outlet, improves the resistance in the refrigerant flow path, improves refrigerant recirculation, increases cooling capacity, and thus improves the COP (compressor performance coefficient) under various operating conditions, ultimately achieving a significant improvement in the compressor's APF (annual average power factor) performance. Attached Figure Description

[0018] Those skilled in the art will understand that the accompanying drawings are provided to better understand the invention and do not constitute any limitation on the scope of the invention. Wherein:

[0019] Figure 1 This is a schematic diagram of a dual-cylinder rolling rotor compressor according to an embodiment of the present invention;

[0020] Figure 2 This is a schematic diagram of the airflow path when the first optimized S1 scheme is adopted according to an embodiment of the present invention;

[0021] Figure 3 This is a schematic diagram of the airflow path when the third optimized S1 scheme is adopted according to an embodiment of the present invention;

[0022] Figure 4 This is a schematic diagram of the airflow path when the second optimized S1 scheme is adopted according to an embodiment of the present invention;

[0023] Figure 5 This is a schematic diagram of an optimized exhaust refrigerant flow channel according to an embodiment of the present invention;

[0024] Figure 6 This is a schematic diagram showing the position of the flow area of ​​the intake and exhaust structure of a dual-cylinder rolling rotor compressor according to an embodiment of the present invention.

[0025] The reference numerals in the attached figures are as follows:

[0026] 11-First muffler; 111-Muffler outlet; 12-Second muffler; 2-Intake air passage; 3-Intake port; 4-Exhaust refrigerant passage; 5-Exhaust port; 6-Cylinder. Detailed Implementation

[0027] In this document, unless otherwise stated, the terms “upper,” “lower,” “left,” “right,” “inner,” “outer,” “front,” “back,” “top,” “bottom,” etc., are used to indicate orientation or positional relationship based on the accompanying drawings, and are only for the convenience of describing the invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a characteristic orientation and operation, and therefore should not be construed as a limitation of the invention.

[0028] The specific embodiments of the present invention will now be described in more detail with reference to the accompanying drawings. The advantages and features of the present invention will become clearer from the following description. It should be noted that the drawings are all in a very simplified form and use non-precise proportions, and are only used to facilitate and clarify the illustration of the embodiments of the present invention.

[0029] Please refer to Figures 1 to 6 This invention provides a dual-cylinder rolling rotor compressor, comprising two cylinders 6 and an intermediate plate. The two cylinders 6 have the same inner diameter and axial height, and the pistons within the two cylinders 6 have the same outer diameter. One of the cylinders has an upper cylinder cover, and the other cylinder has a lower cylinder cover. The two cylinders are separated by the intermediate plate. It is understood that the axial height of the cylinder is the height perpendicular to the direction of its inner diameter. The dual-cylinder rolling rotor compressor has a suction passage 2 and an air inlet 3. At least one cylinder has an air inlet 3; this embodiment uses one cylinder 6 as an example. The suction passage 2 is connected to one cylinder 6 at each end, and the air inlet 3 is used to draw refrigerant into the dual-cylinder rolling rotor compressor.

[0030] Furthermore, the twin-cylinder rotary compressor has a first muffler 11, a second muffler 12, and two or more exhaust refrigerant channels 4. These exhaust refrigerant channels axially penetrate the upper cylinder head, the two cylinders, the intermediate plate, and the lower cylinder head. For example, the number of exhaust refrigerant channels 4 is three. Figure 2 As shown. The first muffler 11 is connected to the second muffler through the exhaust refrigerant passage 4, and the first muffler is provided with a muffler outlet 111. It can be understood that the refrigerant in the compressor is finally discharged through the muffler outlet 111.

[0031] For example, the dual-cylinder rolling rotor compressor has two exhaust ports 5 with the same flow area, and the two exhaust ports 5 correspond one-to-one with two cylinders. One cylinder is connected to the first muffler 11 through the exhaust port 5 to discharge refrigerant into the first muffler 11, and the other cylinder is connected to the second muffler 12 through the exhaust port 5 to discharge refrigerant into the second muffler 12.

[0032] You can refer to this. Figure 1 and Figure 6Let the flow area of ​​the intake port 3 be S, the flow area of ​​the suction channel 2 be S1, the inner diameter of the cylinder containing the intake port 3 be D1, the axial height of the cylinder containing the intake port 3 be H1, the outer diameter of the piston in the cylinder containing the intake port 3 be D2, and the unit volume cooling capacity of the compressor be q. Then, the flow area S of the intake port 3 and the flow area S1 of the suction channel 2 should satisfy the following relationship:

[0033]

[0034] When there are multiple air inlets 3, the flow area S of each air inlet 3 must satisfy the above relationship.

[0035] Preferably, the flow area of ​​the exhaust refrigerant passage in the twin-cylinder rotary compressor is S2, and the ratio of the flow area S1 of the intake passage 2 to the flow area S2 of the exhaust refrigerant passage is not less than 0.6. Further, the ratio of the flow area S1 of the intake passage 2 to the flow area S2 of the exhaust refrigerant passage 4 is not greater than 2.2, that is:

[0036]

[0037] When there are two or more exhaust refrigerant channels 4, S2 is the sum of the flow areas of all exhaust refrigerant channels 4.

[0038] Each of the two cylinders is connected to an exhaust port 5, and the flow areas of the two exhaust ports 5 are the same. Let the flow area of ​​a single exhaust port 5 be S3, so that the ratio of the flow area S1 of the intake passage 2 to the flow area S3 of the exhaust port 5 is not less than 2.03. Furthermore, the ratio of the flow area S1 of the intake passage 2 to the flow area S3 of a single exhaust port 5 is not greater than 4.4, that is:

[0039]

[0040] In other embodiments, when the flow areas of the two exhaust holes 5 are different, the flow area S3 of each exhaust hole 5 must satisfy the above relationship.

[0041] Let the flow area of ​​the muffler outlet be S4, and ensure that the ratio of the flow area S1 of the intake channel 2 to the flow area S4 of the muffler outlet 111 is not less than 0.9. Furthermore, ensure that the ratio of the flow area S1 of the intake channel 2 to the flow area S4 of the muffler outlet 111 is not greater than 5.24, that is:

[0042]

[0043] In other embodiments, when both the first muffler 11 and the second muffler 12 are provided with muffler outlets, the flow area S4 of each muffler outlet must satisfy the above-mentioned relationship.

[0044] As configured above, this invention derives the preferred range of flow areas for the inlet port 3 and the suction channel 2 under certain cylinder inner diameter, cylinder axial height, piston outer diameter, and compressor unit volume cooling capacity. It also derives the preferred range of flow areas for the exhaust refrigerant channel 4, the exhaust port 5, and the muffler outlet port 111. It is understood that the flow areas of the above-mentioned suction and exhaust structures are directly related to their cross-sectional dimensions. In summary, this invention, by comprehensively adjusting the sizes of the suction channel 2, inlet port 3, exhaust refrigerant channel 4, exhaust port 5, and muffler outlet port 111, improves the resistance in the refrigerant flow path, improves refrigerant recirculation, increases cooling capacity, and thus improves the COP (compressor performance coefficient) under various operating conditions, ultimately achieving a significant improvement in the compressor's APF (annual average power factor) performance.

[0045] In this invention, the refrigerant flow direction is: air inlet 3 → exhaust port 5 → first muffler 11 → muffler outlet 111, and air inlet 3 → intake channel 2 → exhaust port 5 → second muffler 12 → exhaust refrigerant channel 4 → first muffler 11 → muffler outlet 111.

[0046] The air intake channel 2 of the present invention can be as follows Figure 4 As shown, the portion of the intake channel 2 located inside the cylinder 6 that connects to the air inlet 3 is segmented. One segment of the channel near the air inlet 3 is inclined to the cylinder axis, and the other segment of the channel near the intermediate plate is parallel to the cylinder axis.

[0047] The air intake channel 2 of the present invention can be as follows Figure 3 As shown, the extension direction of the portion of the intake passage that connects to the air inlet in the cylinder is inclined to the cylinder axis.

[0048] The air intake channel 2 of the present invention can be as follows Figure 2 As shown, the intake air passage is located inside the cylinder and the portion that connects to the air inlet hole extends through the side wall of the cylinder.

[0049] Table 1 below shows specific examples of using R290 (propane) and R32 (difluoromethane) as refrigerants:

[0050] Combination Figure 2 , Figure 3 , Figure 4 and Figure 5 The values ​​in Table 1 are the ratios of APF and COP under various operating conditions.

[0051] Specifically, the second column (Baseline + Optimized S4 + Optimized S3) in Table 1 represents the schemes that optimize the flow area S4 of the muffler outlet 111 and the flow area S3 of the exhaust port 5 using the formula of the present invention. The schemes in the second column are used as comparison schemes for the other columns. The values ​​in the other columns are the ratios of the schemes in each column to the scheme in the second column. For example, in the APF ratio row, the values ​​in the other columns are the ratios of the APF values ​​under each column's scheme to the APF values ​​under the scheme in the second column, while the values ​​in the second column are the ratios of the APF values ​​under the scheme in the second column to themselves, i.e., 100%. The other rows in the table follow the same pattern. The first column (Baseline) represents schemes that do not use the formula for optimizing the flow area of ​​the intake and exhaust structures of the present invention.

[0052] The third column (Baseline + Optimized S4 + Optimized S3 + First Optimized S1) represents the scheme that optimizes the flow area S4 of the muffler outlet 111, the flow area S3 of the exhaust port 5, and the flow area S1 of the intake channel 2 using the relational formula of the present invention. This can be referenced. Figure 2 Let the current optimization S1 be the first optimization S1;

[0053] The fourth column (Baseline + Optimized S4 + Optimized S3 + Third Optimized S1) represents the scheme that optimizes the flow area S4 of the muffler outlet 111, the flow area S3 of the exhaust port 5, and the flow area S1 of the intake channel 2 using the relational formula of this invention. This can be referenced. Figure 3 Let the current optimization S1 be the third optimization S1;

[0054] The fifth column (Baseline + Optimized S4 + Optimized S3 + Second Optimized S1) represents the scheme that optimizes the flow area S4 of the muffler outlet 111, the flow area S3 of the exhaust port 5, and the flow area S1 of the intake channel 2 using the relational formula of this invention. This can be referenced. Figure 4 Let the optimization S1 at this time be the second optimization S1.

[0055] Understandably, the larger the value in Table 1, the better the compressor performance and the higher the energy efficiency. After comparison, the scheme in the fifth column is the best among the schemes in the first to fifth columns. Based on the scheme in the fifth column, the flow area S2 of the exhaust refrigerant channel 4 is further optimized, resulting in the values ​​in the sixth column of Table 1 (baseline + optimized S4 + optimized S3 + second optimized S1 + optimized S2), which can be used as a reference. Figure 5 , Figure 5 As can be seen from this, compared to Figures 2 to 4 This increases the area of ​​the exhaust refrigerant flow channel. Therefore, as can be seen from the embodiments, regardless of whether it is R290 or R32 refrigerant, the relationship between the flow area of ​​the intake and exhaust structure of the present invention can improve the COP under various operating conditions, ultimately achieving a significant improvement in the compressor's APF performance.

[0056] Table 1

[0057]

[0058] It should be noted that references to "an embodiment," "an embodiment," "a specific embodiment," "some embodiments," etc., in the specification only indicate that the described embodiment may include a specific feature, structure, or characteristic. Furthermore, such phrases do not necessarily refer to the same embodiment. Additionally, when a specific feature, structure, or characteristic is described in conjunction with an embodiment, whether explicitly described or not, implementing such a feature, structure, or characteristic in conjunction with other embodiments is within the knowledge of those skilled in the art.

[0059] It should be noted that the various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the systems disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the descriptions are relatively simple, and relevant parts can be referred to the method section.

[0060] It should also be noted that although the present invention has been disclosed above with reference to preferred embodiments, these embodiments are not intended to limit the present invention. For any person skilled in the art, many possible variations and modifications can be made to the technical solutions of the present invention based on the disclosed technical content, or equivalent embodiments can be modified accordingly, without departing from the scope of the present invention. Therefore, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the present invention shall still fall within the scope of protection of the present invention.

[0061] It should also be understood that, unless otherwise specified or indicated, the terms “first,” “second,” “third,” etc., in the specification are used only to distinguish the various components, elements, and steps in the specification, and not to indicate the logical or sequential relationships between the various components, elements, and steps.

[0062] Furthermore, it should be recognized that the terminology described herein is used only to describe particular embodiments and not to limit the scope of the invention. It must be noted that the singular forms “a” and “an” used herein and in the appended claims include plural bases unless the context clearly indicates otherwise. For example, a reference to “a step” or “an apparatus” means a reference to one or more steps or apparatuses, and may include secondary steps and secondary apparatuses. All conjunctions used should be understood in the broadest sense. Also, the word “or” should be understood to have the definition of logical “or” rather than logical “exclusive OR”, unless the context clearly indicates otherwise. Furthermore, implementation of the methods and / or devices in embodiments of the invention may include performing selected tasks manually, automatically, or in combination.

Claims

1. A dual-cylinder rolling rotor compressor, characterized in that, The compressor includes two cylinders and an intermediate plate. One cylinder has an upper cylinder head, and the other cylinder has a lower cylinder head. The two cylinders are separated by the intermediate plate. Each cylinder contains a piston, and at least one cylinder has an air inlet. The compressor also includes a suction passage that penetrates the intermediate plate, with each end of the suction passage communicating with one of the cylinders. The air inlet is used to draw refrigerant into the dual-cylinder rotary compressor. Let the flow area of ​​the air inlet be S, the flow area of ​​the air intake channel be S1, the inner diameter of the cylinder with the air inlet be D1, the axial height of the cylinder be H1, the outer diameter of the piston be D2, and the unit volume cooling capacity of the compressor be q. Then, the flow area S of the air inlet and the flow area S1 of the air intake channel should satisfy the following relationship: ≤ ≤ ； The upper cylinder head is provided with an exhaust port communicating with one of the cylinders, and / or the lower cylinder head is provided with an exhaust port communicating with another cylinder. The flow area of ​​the exhaust port is S3, such that the ratio of the flow area S1 of the intake channel to the flow area S3 of the exhaust port is not less than 2.03 and not greater than 4.

4. The compressor further includes a first silencer and a second silencer. The first silencer and / or the second silencer are provided with silencer outlet holes. The flow area of ​​the silencer outlet holes is S4, such that the ratio of the flow area S1 of the suction channel to the flow area S4 of the silencer outlet holes is not less than 0.9 and not greater than 5.

24. The extension direction of the portion of the intake channel that connects to the air inlet in the cylinder is inclined to the cylinder axis. Alternatively, the portion of the intake channel that connects to the air inlet in the cylinder is segmented, with one segment of the channel near the air inlet inclined to the cylinder axis and one segment of the channel near the intermediate plate parallel to the cylinder axis.

2. The dual-cylinder rolling rotor compressor as described in claim 1, characterized in that, The compressor also includes an exhaust refrigerant flow channel, which axially passes through the upper cylinder head, the two cylinders, the intermediate plate, and the lower cylinder head. The flow area of ​​the exhaust refrigerant flow channel is S2, such that the ratio of the flow area S1 of the intake flow channel to the flow area S2 of the exhaust refrigerant flow channel is not less than 0.6 and not greater than 2.

2.

3. The twin-cylinder rolling rotor compressor as described in claim 1, characterized in that, The two cylinders have the same inner diameter and the same axial height, and the pistons in the two cylinders have the same outer diameter.

4. The twin-cylinder rolling rotor compressor as described in claim 2, characterized in that, When there are two or more exhaust refrigerant channels, S2 is the sum of the flow areas of all the exhaust refrigerant channels.

5. The twin-cylinder rolling rotor compressor as described in claim 1, characterized in that, The dual-cylinder rolling rotor compressor has two exhaust ports with the same flow area.

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