Double-cylinder rolling rotor type compressor

Abstract

The invention provides a double-cylinder rolling rotor type compressor which comprises two air cylinders and a middle plate, one air cylinder is provided with an upper cylinder cover, the other air cylinder is provided with a lower cylinder cover, the two air cylinders are separated by the middle plate, pistons are arranged in the two air cylinders, at least one air cylinder is provided with an air inlet hole, and the compressor further comprises an air suction runner penetrating through the middle plate. The through-flow area of the air inlet hole is S, the through-flow area of the air suction flow channel is S1, the inner diameter of the air cylinder provided with the air inlet hole is D1, the axial height of the air cylinder is H1, the outer diameter of the piston is D2, and the refrigerating capacity per unit volume of the compressor is q, and if not, the through-flow area S of the air inlet hole and the through-flow area S1 of the air suction flow channel meet the following relational expression: # imgabs0 #. According to the air suction and exhaust structure disclosed by the invention, by comprehensively adjusting the through-flow area of the air suction and exhaust structure, the resistance on a refrigerant flow path is improved, the refrigerant backflow is improved, the refrigerating capacity is increased, and finally, the APF performance of the compressor is remarkably improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioning, and in particular to a double-cylinder rolling rotor type compressor. Background Art

[0002] The APF (Annual Energy Percentage) value of an air conditioner refers to the energy efficiency ratio of the air conditioner, that is, the ratio of the cooling or heating efficiency of the air conditioner to the energy consumption. The higher the APF value, the higher the energy efficiency of the air conditioner, the more electricity it saves, and it can consume less energy under the same cooling or heating effect, thereby reducing energy consumption and environmental pollution. The coefficient of performance (COP) of the compressor is an important indicator to measure the energy efficiency of the compressor, reflecting the amount of cooling or heat that the compressor can provide per unit of energy consumption. The higher the COP value, the higher the energy utilization efficiency.

[0003] The performance of the whole machine under different pump body structures and refrigerant conditions is affected differently by the size of the gas flow channel area, so targeted structural design is required, and there is an optimal range for the size and style of each component. At the same time, the size of the suction and exhaust flow area plays a vital role in the performance of the compressor. Optimizing the suction flow channel alone or optimizing the exhaust flow channel alone has a very limited effect on improving the overall efficiency of the compressor, and comprehensive improvement is needed. In view of this, the present invention intends to improve the COP of each working condition by comprehensively adjusting the size of the suction and exhaust flow channels, exhaust holes, etc., and ultimately achieve a significant improvement in the APF performance of the compressor. Summary of the invention

[0004] The purpose of the present invention is to provide a twin-cylinder rolling rotor compressor, which can improve the COP (compressor performance coefficient) under various working conditions by comprehensively adjusting the sizes of the suction flow channel, the air inlet hole, the exhaust refrigerant flow channel, the exhaust hole and the muffler outlet hole, and ultimately achieve the purpose of significantly improving the compressor APF (annual power consumption rate) performance.

[0005] In order to achieve the above-mentioned object, the present invention provides a twin-cylinder rolling rotor compressor, characterized in that it comprises two cylinders and an intermediate plate, wherein 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, pistons are arranged in the two cylinders, and at least one cylinder is provided with an air inlet hole, the compressor also comprises an intake air passage penetrating the intermediate plate, the two ends of the intake air passage are respectively connected with one of the cylinders, and the air inlet hole is used to draw refrigerant into the twin-cylinder rolling rotor compressor,

[0006] Suppose 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 refrigeration capacity of the compressor is q, then the flow area S of the air inlet hole and the flow area S1 of the suction flow channel satisfy the following relationship:

[0007]

[0008] Optionally, the compressor also includes an exhaust refrigerant flow channel, which axially penetrates the upper cylinder head, the two cylinders, the middle plate and the lower cylinder head, and the flow area of ​​the exhaust refrigerant flow channel is S2, so 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 more than 2.2.

[0009] Optionally, the upper cylinder head is provided with an exhaust hole connected to one of the cylinders, and / or the lower cylinder head is provided with an exhaust hole connected to another of the cylinders, and the flow area of ​​the exhaust hole is S3, so that the ratio of the flow area S1 of the intake air duct to the flow area S3 of the exhaust hole is not less than 2.03 and not more than 4.4.

[0010] Optionally, the compressor also includes a first muffler and a second muffler, and the first muffler and / or the second muffler are provided with a muffler outlet hole, and the flow area of ​​the muffler outlet hole is S4, so that the ratio of the flow area S1 of the intake air duct to the flow area S4 of the muffler outlet hole is not less than 0.9 and not greater than 5.24.

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

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

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

[0014] Optionally, the portion of the intake flow channel located in the cylinder and connected to the air inlet hole is segmented, a section of the flow channel close to the air inlet hole is inclined to the axis of the cylinder, and a section of the flow channel close to the middle plate is parallel to the axis of the cylinder.

[0015] Optionally, the extending direction of the portion of the intake air passage located in the cylinder and connected to the air inlet hole is inclined to the axial direction of the cylinder.

[0016] Optionally, a portion of the intake air passage located in the cylinder and connected to the air inlet hole passes through a side wall of the cylinder.

[0017] As configured above, the present invention derives the preferred value ranges of the flow area of ​​the air inlet hole and the flow area of ​​the suction flow channel under certain cylinder inner diameter, cylinder axial height, piston outer diameter and unit volumetric refrigeration capacity of the compressor, and also derives the preferred value ranges of the flow area of ​​the exhaust refrigerant flow channel, the flow area of ​​the exhaust hole and the flow area of ​​the muffler outlet hole. It can be understood that the flow area of ​​the above-mentioned suction and exhaust structure is directly related to the size of its cross-sectional size. In summary, the present invention improves the resistance on the refrigerant flow path, improves the refrigerant reflux, increases the refrigeration capacity, and further improves the COP (compressor coefficient of performance) under various working conditions, and ultimately achieves a significant improvement in the APF (annual power consumption rate) performance of the compressor by comprehensively adjusting the size of the suction flow channel, the air inlet hole, the exhaust refrigerant flow channel, the exhaust hole and the muffler outlet hole. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Those skilled in the art should understand that the drawings are provided for a better understanding of the present invention and do not constitute any limitation on the scope of the present invention.

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

[0020] Figure 2 A schematic diagram of an inhalation airway when the first optimization S1 solution is adopted according to an embodiment of the present invention;

[0021] Figure 3 A schematic diagram of an inhalation airway when the third optimization S1 solution is adopted according to an embodiment of the present invention;

[0022] Figure 4 A schematic diagram of an inhalation airway when the second optimization S1 solution is adopted according to an embodiment of the present invention;

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

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

[0025] The reference numerals are as follows:

[0026] 11-first muffler; 111-muffler outlet; 12-second muffler; 2-intake flow channel; 3-intake hole; 4-exhaust refrigerant flow channel; 5-exhaust hole; 6-cylinder. DETAILED DESCRIPTION

[0027] In this document, unless otherwise specified, the terms "upper", "lower", "left", "right", "inside", "outside", "front", "back", "top", "bottom", etc. are used to indicate directions or positional relationships based on the drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction and operation. Therefore, they cannot be understood as limiting the present invention.

[0028] The specific implementation of the present invention will be described in more detail below in conjunction with the schematic diagram. The advantages and features of the present invention will become clearer based on the following description. It should be noted that the drawings are all in a very simplified form and are not in exact proportions, and are only used to facilitate and clearly assist in explaining the purpose of the embodiments of the present invention.

[0029] Please refer to Figures 1 to 6 , an embodiment of the present invention provides a twin-cylinder rolling rotor compressor, which includes two cylinders 6 and an intermediate plate, and the two cylinders 6 have the same inner diameter and the same axial height, and the outer diameters of the pistons in the two cylinders 6 are the same. One of the cylinders has an upper cylinder head, and the other cylinder has a lower cylinder head, and the two cylinders are separated by the intermediate plate. It can be understood that the axial height of the cylinder is the height perpendicular to the inner diameter direction of the cylinder. The twin-cylinder rolling rotor compressor has an intake flow channel 2 and an air inlet hole 3, and at least one cylinder is provided with an air inlet hole 3. This embodiment takes an example in which an air inlet hole 3 is provided on one cylinder 6. The two ends of the intake flow channel 2 are respectively connected to a cylinder 6, and the air inlet hole 3 is used to suck the refrigerant into the twin-cylinder rolling rotor compressor.

[0030] Further, the twin-cylinder rolling rotor compressor has a first muffler 11, a second muffler 12 and more than two exhaust refrigerant flow channels 4, wherein the exhaust refrigerant flow channels axially penetrate the upper cylinder head, the two cylinders, the intermediate plate and the lower cylinder head. For example, the number of the exhaust refrigerant flow channels 4 is 3, such as Figure 2 The first muffler 11 is connected to the second muffler through the exhaust refrigerant flow channel 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] Exemplarily, a two-cylinder rolling rotor compressor has two exhaust holes 5 with the same flow area, and the two exhaust holes 5 correspond one-to-one to the two cylinders. One cylinder is connected to the first muffler 11 through the exhaust hole 5 to discharge the refrigerant into the first muffler 11, and the other cylinder is connected to the second muffler 12 through the exhaust hole 5 to discharge the refrigerant into the second muffler 12.

[0032] You can refer to Figure 1 and Figure 6, let the flow area of ​​the air inlet hole 3 be S, the flow area of ​​the air intake channel 2 be S1, the inner diameter of the cylinder where the air inlet hole 3 is located be D1, the axial height of the cylinder where the air inlet hole 3 is located be H1, the outer diameter of the piston in the cylinder where the air inlet hole 3 is located be D2, and the unit volume refrigeration capacity of the compressor be q, then the flow area S of the air inlet hole 3 and the flow area S1 of the air intake channel 2 satisfy the following relationship:

[0033]

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

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

[0036]

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

[0038] The two cylinders are each connected to an exhaust hole 5, and the flow areas of the two exhaust holes 5 are the same. The flow area of ​​a single exhaust hole 5 is S3, and the ratio of the flow area S1 of the intake flow passage 2 to the flow area S3 of the exhaust hole 5 is not less than 2.03. Furthermore, the ratio of the flow area S1 of the intake flow passage 2 to the flow area S3 of the single exhaust hole 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] The flow area of ​​the silencer outlet hole is set to S4, and the ratio of the flow area S1 of the air intake passage 2 to the flow area S4 of the silencer outlet hole 111 is not less than 0.9. Furthermore, the ratio of the flow area S1 of the air intake passage 2 to the flow area S4 of the silencer outlet hole 111 is set to be 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 outlet holes, the flow area S4 of each muffler outlet hole must satisfy the above relationship.

[0044] As configured above, the present invention derives the preferred value ranges of the flow area of ​​the air inlet 3 and the flow area of ​​the suction flow channel 2 under certain cylinder inner diameter, cylinder axial height, piston outer diameter and unit volume refrigeration capacity of the compressor, and also derives the preferred value ranges of the flow area of ​​the exhaust refrigerant flow channel 4, the flow area of ​​the exhaust hole 5 and the flow area of ​​the muffler outlet hole 111. It can be understood that the flow area of ​​the above-mentioned suction and exhaust structure is directly related to the size of its cross-sectional size. In summary, the present invention improves the resistance on the refrigerant flow path, improves the refrigerant reflux, increases the refrigeration capacity, and further improves the COP (compressor coefficient of performance) under various working conditions, and finally achieves a significant improvement in the compressor APF (annual power consumption rate) performance by comprehensively adjusting the size of the suction flow channel 2, the air inlet 3, the exhaust refrigerant flow channel 4, the exhaust hole 5 and the muffler outlet hole 111.

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

[0046] The inhalation flow channel 2 of the present invention can be as follows Figure 4 As shown, the portion of the intake flow channel 2 located in the cylinder 6 and connected to the air inlet hole 3 is segmented, a section of the flow channel close to the air inlet hole 3 is inclined to the cylinder axis, and a section of the flow channel close to the middle plate is parallel to the cylinder axis.

[0047] The inhalation flow channel 2 of the present invention can be as follows Figure 3 As shown, the extending direction of the portion of the intake flow passage located in the cylinder and connected to the intake hole is inclined to the axial direction of the cylinder.

[0048] The inhalation flow channel 2 of the present invention can be as follows Figure 2 As shown, the portion of the intake air passage located in the cylinder and connected to the air inlet hole passes through the side wall of the cylinder.

[0049] The following table 1 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 working conditions.

[0051] Specifically, the second column (benchmark + optimized S4 + optimized S3) in Table 1 represents the solution of optimizing the flow area S4 of the muffler outlet hole 111 and the flow area S3 of the exhaust hole 5 by using the relational expression of the present invention, and the solution of the second column is used as the comparison solution of other columns, and the values ​​of other columns are the ratios of the solutions of each column to the solutions of the second column. For example, in the row of APF ratio, the values ​​of other columns are the ratios of the APF values ​​under the solutions of each column to the APF values ​​under the solutions of the second column, and the values ​​of the second column are the ratios of the APF values ​​under the solutions of the second column to themselves, that is, 100%, and the same applies to other rows in the table. The first column (benchmark) represents the solution of optimizing the flow area relational expression of the intake and exhaust structure without using the present invention;

[0052] The third column (benchmark + optimization S4 + optimization S3 + first optimization S1) represents the solution of optimizing the flow area S4 of the muffler outlet hole 111, the flow area S3 of the exhaust hole 5 and the flow area S1 of the intake air duct 2 by using the relationship of the present invention. Figure 2 , let the optimization S1 at this time be the first optimization S1;

[0053] The fourth column (benchmark + optimization S4 + optimization S3 + third optimization S1) represents the solution of optimizing the flow area S4 of the muffler outlet hole 111, the flow area S3 of the exhaust hole 5 and the flow area S1 of the suction flow channel 2 by using the relationship of the present invention, which can be referred to Figure 3 , let the optimization S1 at this time be the third optimization S1;

[0054] The fifth column (benchmark + optimization S4 + optimization S3 + second optimization S1) represents the solution of optimizing the flow area S4 of the muffler outlet hole 111, the flow area S3 of the exhaust hole 5 and the flow area S1 of the suction flow channel 2 by using the relationship of the present invention. Figure 4 , let the optimization S1 at this time be the second optimization S1.

[0055] It can be understood that 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. On the basis of the scheme in the fifth column, the flow area S2 of the exhaust refrigerant flow channel 4 is optimized to obtain the value of the sixth column in Table 1 (benchmark + optimized S4 + optimized S3 + second optimized S1 + optimized S2), which can be referred to Figure 5 , Figure 5 It can be seen that compared with Figures 2 to 4 Therefore, it can be seen from the embodiment that, regardless of R290 refrigerant or R32 refrigerant, the relationship between the flow area of ​​the suction and exhaust structure of the present invention can improve the COP of each working condition, and finally achieve a significant improvement in the APF performance of the compressor.

[0056] Table 1

[0057]

[0058] It should be noted that references to "one embodiment", "an embodiment", "a specific embodiment", "some embodiments", etc. in the specification only indicate that the described embodiment may include a particular feature, structure or characteristic. Moreover, such phrases do not necessarily refer to the same embodiment. In addition, when a particular feature, structure or characteristic is described in conjunction with an embodiment, whether or not explicitly described, it is within the knowledge of a person skilled in the relevant art to implement such feature, structure or characteristic in conjunction with other embodiments.

[0059] It should be noted that the various embodiments in this specification are described in a progressive manner, and each embodiment focuses on the differences from other embodiments, and the same or similar parts between the various embodiments can be referred to each other. For the system disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant parts can be referred to the method part description.

[0060] It should also be noted that, although the present invention has been disclosed as a preferred embodiment, the above embodiment is not intended to limit the present invention. For any technician familiar with the art, without departing from the scope of the technical solution of the present invention, the technical content disclosed above can be used to make many possible changes and modifications to the technical solution of the present invention, or modified into equivalent embodiments of equivalent changes. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present invention without departing from the content of the technical solution of the present invention still falls within the scope of protection of the technical solution 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 merely used to distinguish between the various components, elements, steps, etc. in the specification, and are not used to indicate the logical relationship or sequential relationship between the various components, elements, steps, etc.

[0062] It should also be recognized that the terms described herein are only used to describe specific embodiments and are not intended to limit the scope of the invention. It should be noted that the singular forms "a" and "an" used herein and in the appended claims include plural references unless the context clearly indicates otherwise. For example, a reference to "a step" or "a device" means a reference to one or more steps or devices, and may include secondary steps and secondary devices. All conjunctions used should be understood in the broadest sense. And, the word "or" should be understood to have the definition of a logical "or", rather than a logical "exclusive or", unless the context clearly indicates otherwise. In addition, the implementation of the method and / or device in the embodiments of the present invention may include performing the selected task manually, automatically, or in combination.

Claims

1. A twin-cylinder rolling rotor compressor, characterized in that: The compressor comprises two cylinders and an intermediate plate, wherein 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, pistons are arranged in the two cylinders, and at least one cylinder is provided with an air inlet hole, the compressor further comprises an air intake passage penetrating the intermediate plate, the two ends of the air intake passage are respectively connected with one of the cylinders, and the air inlet hole is used to inhale the refrigerant into the double-cylinder rolling rotor compressor, Suppose 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 refrigeration capacity of the compressor is q, then the flow area S of the air inlet hole and the flow area S1 of the suction flow channel satisfy the following relationship:

2. The twin-cylinder rolling rotor compressor according to claim 1, characterized in that: The compressor also includes an exhaust refrigerant flow channel, which axially penetrates the upper cylinder head, the two cylinders, the middle plate and the lower cylinder head. The flow area of ​​the exhaust refrigerant flow channel is S2, so 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 more than 2.

2.

3. The twin-cylinder rolling rotor compressor according to claim 1, characterized in that: The upper cylinder head is provided with an exhaust hole connected to one of the cylinders, and / or the lower cylinder head is provided with an exhaust hole connected to another of the cylinders, and the flow area of ​​the exhaust hole is S3, so that the ratio of the flow area S1 of the intake flow passage to the flow area S3 of the exhaust hole is not less than 2.03 and not more than 4.

4.

4. The twin-cylinder rolling rotor compressor according to claim 1, characterized in that: The compressor also includes a first muffler and a second muffler, the first muffler and / or the second muffler are provided with a muffler outlet hole, the flow area of ​​the muffler outlet hole is S4, so that the ratio of the flow area S1 of the intake air duct to the flow area S4 of the muffler outlet hole is not less than 0.9 and not more than 5.

24.

5. The twin-cylinder rolling rotor compressor according to claim 1, characterized in that: The two cylinders have the same inner diameter and the same axial height, and the outer diameters of the pistons in the two cylinders are the same.

6. The twin-cylinder rolling rotor compressor according to claim 2, characterized in that: When the number of the exhaust refrigerant flow channels is two or more, S2 is the sum of the flow areas of all the exhaust refrigerant flow channels.

7. The twin-cylinder rolling rotor compressor according to claim 3, characterized in that: The twin-cylinder rolling rotor compressor has two exhaust holes with the same flow area.

8. The double-cylinder rolling rotor compressor according to any one of claims 1 to 7, characterized in that: The portion of the intake flow channel located in the cylinder and connected to the air inlet hole is segmented, a section of the flow channel close to the air inlet hole is inclined to the axial direction of the cylinder, and a section of the flow channel close to the middle plate is parallel to the axial direction of the cylinder.

9. The twin-cylinder rolling rotor compressor according to any one of claims 1 to 7, characterized in that: The extending direction of the portion of the intake flow passage located in the cylinder and communicating with the intake hole is inclined to the axial direction of the cylinder.

10. The double-cylinder rolling rotor compressor according to any one of claims 1 to 7, characterized in that: The portion of the intake flow passage located in the cylinder and communicating with the air inlet hole passes through the side wall of the cylinder.

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