Exhaust structure and compressor

Abstract

The present invention provides an exhaust structure and a compressor. The exhaust structure includes an exhaust flange. The exhaust flange has a main exhaust port. The two ends of the main exhaust port are an intake end and an exhaust end respectively. The intake end is connected to the compression chamber of the cylinder. The groove on the inner wall of the intake end forms an auxiliary exhaust port. The auxiliary exhaust port is connected to the compression chamber and the main exhaust port. In this scheme, the main exhaust port and the auxiliary exhaust port jointly form an exhaust channel. By setting the auxiliary exhaust port, the exhaust area of ​​the end of the exhaust channel connected to the compression chamber is increased, which effectively reduces the exhaust loss of the compressor when it is running at a high frequency. At the same time, the exhaust area of ​​the end of the exhaust channel that cooperates with the valve plate (that is, the exhaust end of the main exhaust port) is small, so that when the valve plate is closed, the pressure difference on both sides is small, the deformation of the valve plate is small, and the reliability of the valve plate is guaranteed. Therefore, compared with the prior art, this scheme solves the problem that it is difficult for the exhaust structure to balance the high-frequency exhaust loss and the reliability of the valve plate.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to an exhaust structure and a compressor. Background Art

[0002] With the development of rotary compressor technology, the displacement of rotary compressors has expanded to more than 100cc, which can meet the cooling capacity requirements of air-conditioning systems above 20hp. There is a strong demand for the development of large-displacement rotary compressors, and the design of large-displacement compressor exhaust systems is crucial. The exhaust system not only affects the performance of the compressor but also the reliability of the compressor. If a single exhaust port is too large, the reliability of the valve used to open and close the exhaust port will decrease. If the exhaust port is too small, the exhaust loss will be large during high-frequency operation, and the compressor performance will decrease.

[0003] Specifically, large-displacement compressors have large displacement, wide operating conditions, and operating frequencies ranging from 10 Hz to 150 Hz. In order to meet the high energy efficiency requirements of high, medium and low frequencies, the thickness of the valve plate cannot be too thick. At the same time, in order to reduce high-frequency exhaust losses, a larger exhaust port area is required to meet the exhaust requirements. In the study, it was found that when the area of ​​a single exhaust port is too large, the upper surface of the valve plate is exhaust pressure in the closing stage, and the lower surface is suction pressure. The gas pressure difference between the upper and lower surfaces is the largest, and the valve plate is in a concave deformation state. The deformation of the center point of the valve plate is the largest. After exceeding a certain deformation, the valve plate stress is too large and there is a problem of valve plate reliability; but in order to reduce the exhaust loss during high-frequency operation and ensure the energy efficiency of high-frequency operation compressors, the compressor exhaust port must be designed according to a larger exhaust area. How to balance the high-frequency exhaust loss and valve plate reliability is the key to the design of large-displacement compressors. Therefore, when the compressor displacement design becomes larger and larger, the existing design scheme is used to simply increase the exhaust port aperture size to increase the exhaust area. It is difficult to meet the dual design requirements of compressor energy efficiency and valve plate reliability. It is necessary to design a new exhaust structure to solve the above problems. Summary of the invention

[0004] The present invention provides an exhaust structure and a compressor to solve the problem that the exhaust structure in the prior art is difficult to balance high-frequency exhaust loss and valve reliability.

[0005] In order to solve the above-mentioned problem, according to one aspect of the present invention, the present invention provides an exhaust structure for a compressor, comprising: an exhaust flange, wherein the exhaust flange has a main exhaust port, wherein the two ends of the main exhaust port are an intake end and an exhaust end respectively, the intake end is connected to a compression chamber of a cylinder, a groove on an inner wall of the intake end forms an auxiliary exhaust port, and the auxiliary exhaust port is connected to both the compression chamber and the main exhaust port.

[0006] Furthermore, along the axial direction of the main exhaust port, the flow areas of the auxiliary exhaust port at different positions are equal.

[0007] Further, the flow area of ​​the main exhaust port is S1, the flow area of ​​the auxiliary exhaust port is S2, K=S2 / S1, wherein 0.1≤K≤0.6.

[0008] Further, 0.35≤K≤0.45.

[0009] Further, on the mating end surface where the exhaust flange and the cylinder cooperate, the edge of the auxiliary exhaust port is a part of a preset circle.

[0010] Furthermore, the exhaust flange has a mounting hole for mounting a valve plate, and the valve plate is used to open and close the exhaust end of the main exhaust port; on the mating end face, the center of the main exhaust port is O1, the center of the preset circle is O2, and the center of the mounting hole is O3; the line connecting O1 and O2 is the first line, and the line connecting O1 and O3 is the second line, and the angle between the first line and the second line is θ, wherein θ≤90°.

[0011] Further, θ≤30°.

[0012] Further, along the axial direction of the main exhaust port, the height of the main exhaust port is H, and the height of the auxiliary exhaust port is h, wherein 0.2<h / H≤0.5.

[0013] According to another aspect of the present invention, a compressor is provided, comprising the above-mentioned exhaust structure.

[0014] Furthermore, the compressor also includes a cylinder and a valve plate, the cylinder has a compression chamber, the exhaust flange is connected to the cylinder, the main exhaust port and the auxiliary exhaust port are both connected to the compression chamber, the valve plate is installed on the exhaust flange, and the valve plate is used to open and close the exhaust end of the main exhaust port.

[0015] By applying the technical solution of the present invention, an exhaust structure is provided, which includes an exhaust flange, the exhaust flange has a main exhaust port, the two ends of the main exhaust port are respectively an intake end and an exhaust end, the intake end is connected to the compression chamber of the cylinder, the groove on the inner wall of the intake end forms an auxiliary exhaust port, and the auxiliary exhaust port is connected to the compression chamber and the main exhaust port. In this solution, the main exhaust port and the auxiliary exhaust port together form an exhaust channel, and by providing the auxiliary exhaust port, the exhaust area of ​​the end of the exhaust channel connected to the compression chamber is increased, which effectively reduces the exhaust loss of the compressor when it is running at a high frequency. At the same time, the exhaust area of ​​the end of the exhaust channel that cooperates with the valve plate (that is, the exhaust end of the main exhaust port) is small, so that when the valve plate is closed, the pressure difference on both sides is small, the deformation of the valve plate is small, and the reliability of the valve plate is guaranteed. Therefore, compared with the prior art, this solution solves the problem that it is difficult for the exhaust structure to balance the high-frequency exhaust loss and the reliability of the valve plate.

[0016] If the auxiliary exhaust port is designed too large, the clearance volume will increase and the volumetric efficiency will decrease. If the auxiliary exhaust port is designed too small, the exhaust loss will be large and the indicated efficiency will decrease. Therefore, the size of the auxiliary exhaust port needs to be within a certain range to have a better value. At the same time, the compressor operates under a wide range of operating conditions and frequencies, and the auxiliary exhaust port design requirements are different under different operating conditions and frequencies. In order to meet the high efficiency of medium, high, low frequencies and all operating conditions, and to ensure the reliability of the valve plate at high frequencies, a large number of simulation calculations and analyses have shown that the new exhaust structure of this scheme can effectively ensure the energy efficiency of the compressor while ensuring the reliability of the valve plate. When the K value in the new exhaust structure of this scheme is designed within the above range, it can ensure better performance of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0018] Figure 1 A schematic diagram of an exhaust structure provided by an embodiment of the present invention is shown;

[0019] Figure 2 Shows Figure 1 A bottom view of the exhaust structure in FIG.

[0020] Figure 3 Shows Figure 1 A top view of the exhaust structure in FIG.

[0021] Figure 4 Shows Figure 2 A partial enlarged view of

[0022] Figure 5 Shows Figure 2 A cross-sectional view of

[0023] Figure 6 The graph showing the relationship between the energy efficiency and the K value of the compressor using the exhaust structure provided by the present invention.

[0024] The above drawings include the following reference numerals:

[0025] 10. Exhaust flange; 20. Main exhaust port; 30. Auxiliary exhaust port; 40. Mounting hole. DETAILED DESCRIPTION

[0026] The technical solutions in the embodiments of the present invention will be described clearly and completely below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0027] like Figures 1 to 6 As shown, an embodiment of the present invention provides an exhaust structure for a compressor, including: an exhaust flange 10, the exhaust flange 10 has a main exhaust port 20, the two ends of the main exhaust port 20 are respectively an intake end and an exhaust end, the intake end is connected to the compression chamber of the cylinder, and the groove on the inner wall of the intake end forms an auxiliary exhaust port 30, and the auxiliary exhaust port 30 is connected to the compression chamber and the main exhaust port 20.

[0028] In this scheme, the main exhaust port 20 and the auxiliary exhaust port 30 jointly form an exhaust channel. By setting the auxiliary exhaust port 30, the exhaust area of ​​the end of the exhaust channel connected to the compression chamber of the cylinder is increased, which effectively reduces the exhaust loss of the compressor when it is running at a high frequency. At the same time, the exhaust area of ​​the end of the exhaust channel that cooperates with the valve plate (that is, the exhaust end of the main exhaust port 20) is small, so that the pressure difference on both sides of the valve plate is small when the valve plate is closed, and the deformation of the valve plate is small, which ensures the reliability of the valve plate. Therefore, compared with the prior art, this scheme solves the problem that it is difficult for the exhaust structure to balance the high-frequency exhaust loss and the reliability of the valve plate, and realizes that the high-frequency exhaust loss of the exhaust structure is small and the reliability of the valve plate is high.

[0029] In this solution, the flow areas of the auxiliary exhaust port 30 at different positions along the axis of the main exhaust port 20 are equal, that is, the cross-sectional area of ​​the auxiliary exhaust port 30 is constant, which facilitates the processing of the auxiliary exhaust port 30.

[0030] Specifically, the flow area of ​​the main exhaust port 20 is S1, the flow area of ​​the auxiliary exhaust port 30 is S2, K=S2 / S1, wherein 0.1≤K≤0.6.

[0031] The adoption of a new exhaust structure effectively solves the problems of excessive exhaust losses and valve reliability when large-displacement compressors are running at high frequencies. The energy efficiency of the compressor is positively correlated with the volumetric efficiency and the indicated efficiency, and the exhaust loss is the key factor affecting the indicated efficiency. If the auxiliary exhaust port is designed too large, the clearance volume will increase and the volumetric efficiency will decrease. If the auxiliary exhaust port is designed too small, the exhaust loss will be large and the indicated efficiency will decrease. Therefore, the size of the auxiliary exhaust port needs to be within a certain range to have a better value. At the same time, the compressor operates under a wide range of operating conditions and frequencies, and the auxiliary exhaust port design requirements are different under different operating conditions and frequencies. In order to meet the high efficiency of medium, high, low frequencies and all operating conditions, and to ensure the reliability of the valve at high frequencies, a large number of simulation calculations and analyses have shown that the new exhaust structure of this scheme can effectively guarantee the energy efficiency of the compressor while ensuring the reliability of the valve. Figure 6 As shown, when the K value in the novel exhaust structure in this scheme is designed within the above range, the compressor performance can be guaranteed to be better.

[0032] Furthermore, 0.35≤K≤0.45. In this way, the compressor has better use effect and higher energy efficiency. Among them, the optimal value of K is 0.4.

[0033] like Figure 2 As shown, on the mating end surface of the exhaust flange 10 and the cylinder, the edge of the auxiliary exhaust port 30 is a part of the preset circumference. In this way, the auxiliary exhaust port 30 is easy to process, for example, by milling.

[0034] like Figure 4 As shown, the exhaust flange 10 has a mounting hole 40 for mounting a valve plate, and the valve plate is used to open and close the exhaust end of the main exhaust port 20; on the mating end surface, the center of the main exhaust port 20 is O1, the center of the preset circle is O2, and the center of the mounting hole 40 is O3; the line connecting O1 and O2 is the first line, the line connecting O1 and O3 is the second line, and the angle between the first line and the second line is θ, where θ≤90°. In this way, the setting position of the auxiliary exhaust port 30 is limited to the vicinity of the second line, and within this range, the axial projection of the auxiliary exhaust port 30 mostly falls within the cylinder compression chamber. The auxiliary exhaust port 30 is set within the range on both sides of the second line, which can effectively increase the exhaust flow area, reduce high-frequency exhaust losses, improve the efficiency of the compressor, and ensure the reliability of the valve plate.

[0035] Preferably, θ≤30°, which can better increase the exhaust flow area and reduce high-frequency exhaust losses.

[0036] like Figure 5As shown, along the axis 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≤0.5. If the height of the auxiliary exhaust port 30 is too high, on the one hand, the clearance volume will be increased to reduce the volumetric efficiency of the compressor and thus reduce the energy efficiency. At the same time, if its height is too high, the local strength of the exhaust flange 10 at the auxiliary exhaust port 30 will be weakened, and the exhaust flange 10 will be easily deformed and insufficient in strength during high-frequency and high-load operation, resulting in fracture problems. Therefore, the height of the auxiliary exhaust port 30 should not exceed 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 will be reduced, the exhaust loss will increase, and the indicated efficiency of the compressor will be reduced. The energy efficiency of the compressor will also decrease. Therefore, the height of the auxiliary exhaust port 30 needs to be greater than 20% of the height of the main exhaust port.

[0037] Optionally, the exhaust flange 10 has an assembly groove on the side away from the cylinder, and the valve plate is installed in the assembly groove. The periphery of the exhaust end of the main exhaust port 20 has a sealing rib, and the sealing rib is arranged on the bottom wall of the assembly groove. The sealing rib cooperates with the valve plate, and the sealing rib can ensure full contact with the valve plate, thereby ensuring a sealing effect when the main exhaust port 20 is closed.

[0038] Another embodiment of the present invention further provides a compressor, which includes the above-mentioned exhaust structure. In this scheme, the main exhaust port 20 and the auxiliary exhaust port 30 jointly form an exhaust channel. By setting the auxiliary exhaust port 30, the exhaust area of ​​the end of the exhaust channel connected to the compression chamber of the cylinder is increased, which effectively reduces the exhaust loss of the compressor during high-frequency operation. At the same time, the exhaust area of ​​the end of the exhaust channel that cooperates with the valve plate (that is, the exhaust end of the main exhaust port 20) is small, so that when the valve plate is closed, the pressure difference on both sides is small, the deformation of the valve plate is small, and the reliability of the valve plate is guaranteed. Therefore, compared with the prior art, this scheme solves the problem that it is difficult for the exhaust structure to balance the high-frequency exhaust loss and the reliability of the valve plate, and realizes that the high-frequency exhaust loss of the exhaust structure is small and the reliability of the valve plate is high.

[0039] Among them, the compressor also includes a cylinder and a valve plate. The cylinder has a compression chamber for compressing the refrigerant. The exhaust flange 10 is connected to the cylinder. The main exhaust port 20 and the auxiliary exhaust port 30 are both connected to the compression chamber. The valve plate is installed on the exhaust flange 10, and the valve plate is used to open and close the exhaust end of the main exhaust port 20.

[0040] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

[0041] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0042] Unless otherwise specifically stated, the relative arrangement of the parts and steps described in these embodiments, numerical expressions and numerical values ​​do not limit the scope of the present invention. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to the actual proportional relationship. The technology, method and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, method and equipment should be regarded as a part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once a certain item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.

[0043] In the description of the present invention, it is necessary to understand that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the devices or elements referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of the present invention. The directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

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

[0045] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. If not otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

Claims

1. An exhaust structure for a compressor, characterized in that: include: An exhaust flange (10), the exhaust flange (10) having a main exhaust port (20), the two ends of the main exhaust port (20) being an intake end and an exhaust end respectively, the intake end being connected to a compression chamber of a cylinder, a groove on an inner wall of the intake end forming an auxiliary exhaust port (30), the auxiliary exhaust port (30) being connected to the compression chamber and the main exhaust port (20); The flow area of ​​the main exhaust port (20) is S1, the flow area of ​​the auxiliary exhaust port (30) is S2, K=S2 / S1, wherein 0.1≤K≤0.

6.

2. The exhaust structure according to claim 1, characterized in that: In the axial direction of the main exhaust port (20), the flow areas of the auxiliary exhaust port (30) at different positions are equal.

3. The exhaust structure according to claim 1, characterized in that: 0.35≤K≤0.45。 4. The exhaust structure according to claim 1, characterized in that: On the mating end surface of the exhaust flange (10) and the cylinder, the edge of the auxiliary exhaust port (30) is a part of a preset circumference.

5. The exhaust structure according to claim 4, characterized in that: The exhaust flange (10) has a mounting hole (40) for mounting a valve plate, and the valve plate is used to open and close the exhaust end of the main exhaust port (20); on the matching end surface, the center of the main exhaust port (20) is O1, the center of the preset circle is O2, and the center of the mounting hole (40) is O3; the line connecting O1 and O2 is the first line, and the line connecting O1 and O3 is the second line, and the angle between the first line and the second line is θ, wherein θ≤90°.

6. The exhaust structure according to claim 5, characterized in that: θ≤30°.

7. The exhaust structure according to claim 1, characterized in that: 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≤0.

5.

8. A compressor, characterized in that: The compressor comprises the exhaust structure according to any one of claims 1 to 7.

9. The compressor according to claim 8, characterized in that The compressor also includes a cylinder and a valve plate, the cylinder having a compression chamber, the exhaust flange (10) being connected to the cylinder, the main exhaust port (20) and the auxiliary exhaust port (30) being both connected to the compression chamber, the valve plate being mounted on the exhaust flange (10), and the valve plate being used to open and close the exhaust end of the main exhaust port (20).

Images