CN220705947U - Exhaust structure and compressor - Google Patents
Exhaust structure and compressor Download PDFInfo
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- CN220705947U CN220705947U CN202321596627.9U CN202321596627U CN220705947U CN 220705947 U CN220705947 U CN 220705947U CN 202321596627 U CN202321596627 U CN 202321596627U CN 220705947 U CN220705947 U CN 220705947U
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- 230000006835 compression Effects 0.000 claims abstract description 21
- 238000007906 compression Methods 0.000 claims abstract description 21
- 238000000034 method Methods 0.000 claims description 5
- 230000013011 mating Effects 0.000 claims description 3
- 238000013461 design Methods 0.000 description 11
- 238000006073 displacement reaction Methods 0.000 description 8
- 238000007789 sealing Methods 0.000 description 5
- 238000004458 analytical method Methods 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000000875 corresponding effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 238000003801 milling Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
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Abstract
The utility model provides an exhaust structure and a compressor, wherein the exhaust structure comprises an exhaust flange, the exhaust flange is provided with a main exhaust port, two ends of the main exhaust port are respectively an air inlet end and an exhaust end, the air inlet end is communicated with a compression cavity of a cylinder, a groove on the inner wall of the air inlet end forms an auxiliary exhaust port, and the auxiliary exhaust port is communicated with the compression cavity and the main exhaust port. In this scheme, main gas vent and assistance gas vent form the exhaust passage jointly, through setting up assistance gas vent, the exhaust area increase of the one end of exhaust passage and compression chamber intercommunication like this has effectively reduced the exhaust loss when the high frequency operation of compressor, and exhaust passage and valve block complex one end (i.e. the exhaust end of main gas vent) exhaust area are little simultaneously, and the pressure differential of both sides is little when the valve block is closed like this, and the valve block warp for a short time, has guaranteed the reliability of valve block. Therefore, compared with the prior art, the scheme solves the problem that the high-frequency exhaust loss and the valve plate reliability are difficult to balance in the exhaust structure.
Description
Technical Field
The utility model relates to the technical field of compressors, in particular to an exhaust structure and a compressor.
Background
With the development of rotor compressor technology, the displacement of the rotor compressor is expanded to be more than 100cc, and the cooling capacity requirement of an air conditioning system above 20hp can be met. The development requirement of the large-displacement rotor compressor is strong, the design of an exhaust system of the large-displacement compressor is crucial, and the exhaust system not only affects the performance of the compressor, but also affects the reliability of the compressor. If the single exhaust port is too large, the reliability of the valve plate for opening and closing the exhaust port is reduced, and if the exhaust port is too small, the exhaust loss is large during high-frequency operation, and the performance of the compressor is reduced.
Specifically, the large-displacement compressor has large displacement, wide operating condition range and operating frequency from 10hz to 150hz, and the valve plate cannot be too thick in order to meet the high-energy efficiency requirements of high, medium and low frequencies, and meanwhile, a larger exhaust port area is required to meet the exhaust requirements in order to reduce the high-frequency exhaust loss. When the area of a single exhaust port is too large, the upper surface of the valve plate is exhaust pressure, the lower surface of the valve plate is suction pressure, the difference of the gas pressure on the upper surface and the gas pressure on the lower surface is the largest, the valve plate is in a concave deformation state, the deformation of the central point of the valve plate is the largest, and the reliability problem of the valve plate can exist due to the too large stress of the valve plate after the deformation exceeds a certain deformation; however, in order to reduce the exhaust loss during high-frequency operation and ensure the compressor efficiency during high-frequency operation, the exhaust port of the compressor must be designed according to a larger exhaust area, and how to balance the high-frequency exhaust loss and the valve plate reliability is a key of the design of the large-displacement compressor, so when the design of the displacement of the compressor is larger and larger, the prior design scheme simply increases the aperture of the exhaust port to increase the exhaust area, which is difficult to meet the dual design requirements of the compressor energy and the valve plate reliability, and a new exhaust structure needs to be designed to solve the problems.
Disclosure of Invention
The utility model provides an exhaust structure and a compressor, which are used for solving the problems that the exhaust structure in the prior art is difficult to balance high-frequency exhaust loss and valve plate reliability.
In order to solve the above-described problems, according to an aspect of the present utility model, there is provided a discharge structure for a compressor, including: the exhaust flange is provided with a main exhaust port, two ends of the main exhaust port are respectively an air inlet end and an exhaust end, the air inlet end is communicated with a compression cavity of the cylinder, a groove on the inner wall of the air inlet end forms an auxiliary exhaust port, and the auxiliary exhaust port is communicated with the compression cavity and the main exhaust port.
Further, in the axial direction along the main exhaust port, the flow areas of the auxiliary exhaust ports at different positions are equal.
Further, the flow area of the main exhaust port is S1, and the flow area of the auxiliary exhaust port is S2, wherein K=S2/S1, and K is more than or equal to 0.1 and less than or equal to 0.6.
Further, K is more than or equal to 0.35 and less than or equal to 0.45.
Further, on the matching end surface of the exhaust flange and the cylinder, the edge of the auxiliary exhaust port is a part of a preset circumference.
Further, the exhaust flange is provided with a mounting hole for mounting a valve plate, and the valve plate is used for opening and closing the exhaust end of the main exhaust port; on the matching end face, the center of the circle of the main exhaust port is O 1 The circle center of the preset circumference is O 2 The circle center of the mounting hole is O 3 The method comprises the steps of carrying out a first treatment on the surface of the By O 1 And O 2 Is a first connection line, with O 1 And O 3 The connecting line of the first connecting line is a second connecting line, and the included angle between the first connecting line and the second connecting line is theta, wherein theta is less than or equal to 90 degrees.
Further, θ is less than or equal to 30 °.
Further, in the axial direction along the main exhaust port, the height of the main exhaust port is H, and the height of the auxiliary exhaust port is H, wherein H/H is more than 0.2 and less than or equal to 0.5.
According to another aspect of the present utility model, there is provided a compressor including the above-described discharge structure.
Further, the compressor further comprises a cylinder and a valve plate, the cylinder is provided with a compression cavity, the exhaust flange is connected with the cylinder, the main exhaust port and the auxiliary exhaust port are communicated with the compression cavity, the valve plate is installed on the exhaust flange, and the valve plate is used for opening and closing an exhaust end of the main exhaust port.
By applying the technical scheme of the utility model, the exhaust structure comprises an exhaust flange, wherein the exhaust flange is provided with a main exhaust port, two ends of the main exhaust port are respectively an air inlet end and an exhaust end, the air inlet end is communicated with a compression cavity of a cylinder, a groove on the inner wall of the air inlet end forms an auxiliary exhaust port, and the auxiliary exhaust port is communicated with the compression cavity and the main exhaust port. In this scheme, main gas vent and assistance gas vent form the exhaust passage jointly, through setting up assistance gas vent, the exhaust area increase of the one end of exhaust passage and compression chamber intercommunication like this has effectively reduced the exhaust loss when the high frequency operation of compressor, and exhaust passage and valve block complex one end (i.e. the exhaust end of main gas vent) exhaust area are little simultaneously, and the pressure differential of both sides is little when the valve block is closed like this, and the valve block warp for a short time, has guaranteed the reliability of valve block. Therefore, compared with the prior art, the scheme solves the problem that the high-frequency exhaust loss and the valve plate reliability are difficult to balance in the exhaust structure.
If the design of the auxiliary exhaust port is too large, the clearance volume is increased, the volumetric efficiency is reduced, if the design of the auxiliary exhaust port is too small, the exhaust loss is large, the indication efficiency is reduced, so that the size of the auxiliary exhaust port needs to have a better value within a certain range, the compressor is operated under a wide working condition and a wide frequency, and the design requirements of the auxiliary exhaust port are different under different working conditions and different frequencies. In order to meet the high efficiency of medium-high frequency and low frequency and full operating mode and ensure the valve plate reliability at high frequency, the novel exhaust structure adopting the scheme can effectively ensure the compressor energy efficiency and simultaneously ensure the valve plate reliability through a large number of simulation calculation and analysis discovers. The K value design in the novel exhaust structure in this scheme can guarantee that the compressor performance is better when above-mentioned within range.
Drawings
The accompanying drawings, which are included to provide a further understanding of the utility model and are incorporated in and constitute a part of this specification, illustrate embodiments of the utility model and together with the description serve to explain the utility model. In the drawings:
FIG. 1 shows a schematic diagram of an exhaust structure provided by an embodiment of the present utility model;
FIG. 2 illustrates a bottom view of the exhaust structure of FIG. 1;
FIG. 3 shows a top view of the exhaust structure of FIG. 1;
FIG. 4 shows a partial enlarged view of FIG. 2;
FIG. 5 shows a cross-sectional view of FIG. 2;
fig. 6 shows a graph of energy efficiency versus K value for a compressor employing the exhaust structure provided by the present utility model.
Wherein the above figures include the following reference numerals:
10. an exhaust flange; 20. a main exhaust port; 30. an auxiliary exhaust port; 40. and (5) mounting holes.
Detailed Description
The technical solutions in the embodiments of the present utility model will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present utility model. It will be apparent that the described embodiments are only some, but not all, embodiments of the utility model. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the utility model, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.
As shown in fig. 1 to 6, an embodiment of the present utility model provides a discharge structure for a compressor, including: the exhaust flange 10, the exhaust flange 10 has a main exhaust port 20, two ends of the main exhaust port 20 are an air inlet end and an exhaust end respectively, the air inlet end is communicated with a compression cavity of the cylinder, a groove on the inner wall of the air inlet end forms an auxiliary exhaust port 30, and the auxiliary exhaust port 30 is communicated with the compression cavity and the main exhaust port 20.
In this scheme, main gas vent 20 and auxiliary gas vent 30 form the exhaust passage jointly, through setting up auxiliary gas vent 30, the exhaust area increase of the one end that exhaust passage and the compression chamber of cylinder communicate like this has effectively reduced the exhaust loss when the compressor is at high frequency operation, and exhaust passage and valve block complex one end (i.e. the exhaust end of main gas vent 20) exhaust area are little simultaneously, and the pressure differential of both sides is little when the valve block is closed like this, and the valve block warp for a short time, has guaranteed the reliability of valve block. Therefore, compared with the prior art, the scheme solves the problems that the high-frequency exhaust loss and the valve plate reliability are difficult to balance in the exhaust structure, and realizes that the high-frequency exhaust loss of the exhaust structure is small and the valve plate reliability is high.
In this embodiment, the flow areas of the auxiliary exhaust ports 30 at different positions are equal in the axial direction along the main exhaust port 20. I.e., the cross-sectional area of the auxiliary exhaust port 30 is constant, thus facilitating the processing of the auxiliary exhaust port 30.
Specifically, the flow area of the main exhaust port 20 is S1, and the flow area of the auxiliary exhaust port 30 is S2, where k=s2/S1, where K is 0.1 and 0.6.
The novel exhaust structure effectively solves the problem that the exhaust loss is overlarge and the reliability of the valve plate cannot be considered when the high-frequency operation of the large-displacement compressor is performed. Compressor efficiency is positively correlated with volumetric efficiency and indicating efficiency, and exhaust loss is a key factor affecting indicating efficiency. The extra-large clearance volume of the auxiliary exhaust port is increased, the volumetric efficiency is reduced, the extra-small exhaust loss of the auxiliary exhaust port is increased, the indication efficiency is reduced, the size of the auxiliary exhaust port needs to have a better value in a certain range, meanwhile, the compressor is operated at a wide working condition and a wide frequency, and the design requirements of the auxiliary exhaust port are different under different working conditions and different frequencies. In order to meet the high efficiency of medium-high frequency and low frequency and full operating mode and ensure the valve plate reliability at high frequency, the novel exhaust structure adopting the scheme can effectively ensure the compressor energy efficiency and simultaneously ensure the valve plate reliability through a large number of simulation calculation and analysis discovers. As shown in FIG. 6, the design of the K value in the novel exhaust structure in the scheme can ensure better performance of the compressor when the K value is designed in the range.
Further, K is more than or equal to 0.35 and less than or equal to 0.45. Thus, the compressor has better use effect and higher energy efficiency. Wherein the K value is 0.4.
As shown in fig. 2, the edge of the auxiliary exhaust port 30 is a part of a predetermined circumference on the mating end surface of the exhaust flange 10 with the cylinder. The auxiliary exhaust port 30 is thus easy to machine, for example by milling.
As shown in fig. 4, the exhaust flange 10 has a mounting hole 40 for mounting a valve sheet for opening and closing an exhaust end of the main exhaust port 20; on the mating end face, the center of the main exhaust port 20 is O 1 The circle center of the preset circumference is O 2 The center of the mounting hole 40 is O 3 The method comprises the steps of carrying out a first treatment on the surface of the By O 1 And O 2 Is a first connection line, with O 1 And O 3 The connecting line of the first connecting line is a second connecting line, and the included angle between the first connecting line and the second connecting line is theta, wherein theta is less than or equal to 90 degrees. The setting position of the auxiliary exhaust port 30 is limited near the second connecting line, most of the axial projection of the auxiliary exhaust port 30 falls in the compression cavity of the cylinder in the range, the exhaust flow area can be effectively increased by setting the auxiliary exhaust port 30 in the range of two sides of the second connecting line, the high-frequency exhaust loss is reduced, the efficiency of the compressor is improved, and meanwhile, the reliability of the valve plate can be ensured.
Preferably, θ is less than or equal to 30 °, so that the exhaust gas flow area can be increased better, and the high-frequency exhaust gas loss can be reduced.
As shown in fig. 5, in the axial direction of the main exhaust port 20, the height of the main exhaust port 20 is H, and the height of the auxiliary exhaust port 30 is H, wherein 0.2 < H/h.ltoreq.0.5. If the height of the auxiliary exhaust port 30 is too high, on the one hand, the clearance volume is increased to reduce the volumetric efficiency of the compressor and further reduce the energy efficiency, meanwhile, the local strength of the exhaust flange 10 at the auxiliary exhaust port 30 is weakened due to the too high height, the problem of fracture caused by deformation and insufficient strength of the exhaust flange 10 easily occurs during high-frequency high-load operation, so that the height of the auxiliary exhaust port 30 is not more than 50% of the height of the main exhaust port 20, if the height of the auxiliary exhaust port 30 is too low, the high-frequency exhaust space is reduced, the exhaust loss is increased to reduce the indication efficiency of the compressor, and the energy efficiency of the compressor is also reduced, so that the height of the auxiliary exhaust port 30 is more than 20% of the height of the main exhaust port.
Optionally, the exhaust flange 10 has an assembly groove on a side far away from the cylinder, the valve plate is installed in the assembly groove, the periphery of the exhaust end of the main exhaust port 20 is provided with a sealing convex rib, the sealing convex rib is arranged on the bottom wall of the assembly groove, the sealing convex rib is matched with the valve plate, and the sealing convex rib can be guaranteed to be fully contacted with the valve plate, so that the sealing effect when the main exhaust port 20 is closed is guaranteed.
Another embodiment of the present utility model also provides a compressor including the above-described exhaust structure. In this scheme, main gas vent 20 and auxiliary gas vent 30 form the exhaust passage jointly, through setting up auxiliary gas vent 30, the exhaust area increase of the one end that exhaust passage and the compression chamber of cylinder communicate like this has effectively reduced the exhaust loss when the compressor is at high frequency operation, and exhaust passage and valve block complex one end (i.e. the exhaust end of main gas vent 20) exhaust area are little simultaneously, and the pressure differential of both sides is little when the valve block is closed like this, and the valve block warp for a short time, has guaranteed the reliability of valve block. Therefore, compared with the prior art, the scheme solves the problems that the high-frequency exhaust loss and the valve plate reliability are difficult to balance in the exhaust structure, and realizes that the high-frequency exhaust loss of the exhaust structure is small and the valve plate reliability is high.
The compressor further comprises a cylinder and a valve plate, the cylinder is provided with a compression cavity and used for compressing a refrigerant, the exhaust flange 10 is connected with the cylinder, the main exhaust port 20 and the auxiliary exhaust port 30 are communicated with the compression cavity, the valve plate is arranged on the exhaust flange 10 and used for opening and closing an exhaust end of the main exhaust port 20.
The above description is only of the preferred embodiments of the present utility model and is not intended to limit the present utility model, but various modifications and variations can be made to the present utility model by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model should be included in the protection scope of the present utility model.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present utility model unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.
In the description of the present utility model, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present utility model and simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present utility model; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
In addition, the terms "first", "second", etc. are used to define the components, and are only for convenience of distinguishing the corresponding components, and the terms have no special meaning unless otherwise stated, and therefore should not be construed as limiting the scope of the present utility model.
Claims (10)
1. A discharge structure for a compressor, comprising:
the exhaust flange (10), exhaust flange (10) have main gas vent (20), the both ends of main gas vent (20) are inlet end and exhaust end respectively, inlet end and the compression chamber intercommunication of cylinder, recess on the inner wall of inlet end forms auxiliary gas vent (30), auxiliary gas vent (30) with compression chamber main gas vent (20) all communicate.
2. The exhaust structure according to claim 1, characterized in that the flow areas of the auxiliary exhaust ports (30) at different positions are equal in the axial direction along the main exhaust port (20).
3. The exhaust structure according to claim 1, wherein the flow area of the main exhaust port (20) is S1, and the flow area of the auxiliary exhaust port (30) is S2, k=s2/S1, wherein 0.1.ltoreq.k.ltoreq.0.6.
4. The exhaust structure according to claim 3, wherein 0.35.ltoreq.K.ltoreq.0.45.
5. The exhaust structure according to claim 1, characterized in that the rim of the auxiliary exhaust port (30) is a portion of a predetermined circumference on a mating end surface of the exhaust flange (10) with the cylinder.
6. The exhaust structure according to claim 5, characterized in that the exhaust flange (10) has a mounting hole (40) for mounting a valve sheet for opening and closing an exhaust end of the main exhaust port (20); on the matching end face, the center of the circle of the main exhaust port (20) is O 1 The circle center of the preset circumference is O 2 The circle center of the mounting hole (40) is O 3 The method comprises the steps of carrying out a first treatment on the surface of the By O 1 And O 2 Is a first connection line, with O 1 And O 3 The connecting line of the first connecting line is a second connecting line, and the included angle between the first connecting line and the second connecting line is theta, wherein theta is less than or equal to 90 degrees.
7. The exhaust structure according to claim 6, wherein θ is equal to or less than 30 °.
8. The exhaust structure according to claim 1, characterized in that the height of the main exhaust port (20) is H and the height of the auxiliary exhaust port (30) is H in the axial direction of the main exhaust port (20), wherein 0.2 < H/h.ltoreq.0.5.
9. A compressor comprising the discharge structure of any one of claims 1 to 8.
10. The compressor of claim 9, further comprising a cylinder having a compression chamber, the discharge flange (10) and the cylinder being connected, the main discharge port (20) and the auxiliary discharge port (30) each being in communication with the compression chamber, and a valve plate mounted to the discharge flange (10) for opening and closing a discharge end of the main discharge port (20).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321596627.9U CN220705947U (en) | 2023-06-20 | 2023-06-20 | Exhaust structure and compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202321596627.9U CN220705947U (en) | 2023-06-20 | 2023-06-20 | Exhaust structure and compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN220705947U true CN220705947U (en) | 2024-04-02 |
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ID=90436192
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202321596627.9U Active CN220705947U (en) | 2023-06-20 | 2023-06-20 | Exhaust structure and compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN220705947U (en) |
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2023
- 2023-06-20 CN CN202321596627.9U patent/CN220705947U/en active Active
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