CN220705947U - Exhaust structure and compressor - Google Patents

Abstract

The utility model 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 the air intake end and the exhaust end respectively. The air inlet end is connected to the compression chamber of the cylinder, and the groove on the inner wall of the air inlet end forms an auxiliary exhaust port. 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 jointly form an exhaust channel. By setting the auxiliary exhaust port, the exhaust area at one end of the exhaust channel connected to the compression chamber is increased, which effectively reduces the compressor's load at high temperatures. Exhaust loss during high-frequency operation. At the same time, the exhaust area of the end of the exhaust channel that matches the valve plate (that is, the exhaust end of the main exhaust port) is small. In this way, when the valve plate is closed, the pressure difference on both sides is small and the valve plate is deformed. Small, ensuring the reliability of the valve plate. Therefore, compared with the existing technology, this solution solves the problem that the exhaust structure is difficult to balance high-frequency exhaust loss and valve plate reliability.

Description

Exhaust structure and compressor

Technical field

The utility model relates to the technical field of compressors, specifically to an exhaust structure and a compressor.

Background technique

With the development of rotary compressor technology, the displacement of rotary compressors has expanded to more than 100cc, which can meet the cooling capacity demand of air conditioning systems of more than 20hp. There is a strong demand for the development of large-displacement rotary compressors, and the design of the exhaust system of large-displacement compressors is crucial. The exhaust system not only affects compressor performance but also affects compressor reliability. If a single exhaust port is too large, the reliability of the valve plate 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.

Specifically, due to their large displacement, large-displacement compressors have a wide range of operating conditions and operating frequencies from 10hz to 150hz. In order to meet the high energy efficiency requirements of high, middle and low frequencies, the valve thickness cannot be too thick, and at the same time, in order to reduce high-frequency exhaust losses , a larger exhaust port area is required to meet the exhaust demand. During the study, it was found that when the area of a single exhaust port is too large, the upper surface of the valve plate during the closing stage is the exhaust pressure, and the lower surface is the 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 center point of the valve plate has the largest deformation. Excessive stress on the valve plate after exceeding a certain amount of deformation will cause valve plate reliability problems; however, in order to reduce the exhaust loss during high-frequency operation and ensure the energy efficiency of the compressor during high-frequency operation, the compressor exhaust port It must be designed according to the larger exhaust area. How to balance the high-frequency exhaust loss and valve reliability is the key to the design of large-displacement compressors. Therefore, when the compressor displacement design becomes larger and larger, the existing design is adopted. The solution of simply increasing the exhaust port aperture to increase the exhaust area cannot meet the dual design requirements of compressor energy efficiency and valve reliability. A new exhaust structure needs to be designed to solve the above problems.

Utility Model Content

The utility model provides an exhaust structure and a compressor to solve the problem that the exhaust structure in the prior art is difficult to balance the high-frequency exhaust loss and the reliability of the valve plate.

In order to solve the above problems, according to one aspect of the utility model, the utility model provides an exhaust structure for a compressor, including: an exhaust flange, the exhaust flange having 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.

Further, along the axial direction of the main exhaust port, the flow areas of the auxiliary exhaust port 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, K=S2/S1, where 0.1≤K≤0.6.

Further, 0.35≤K≤0.45.

Further, on the mating end surface of the exhaust flange and the cylinder, the edge of the auxiliary exhaust port is part of a preset circumference.

Further, the exhaust flange has a mounting hole for installing 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 surface, the main exhaust The center of the circle of the mouth is O ₁ , the center of the preset circle is O ₂ , and the center of the mounting hole is O ₃ ; the connection between O ₁ and O ₂ is the first connection, and the connection between O ₁ and O ₃ is The connecting line is a second connecting line, and the angle between the first connecting line and the second connecting line is θ, where θ≤90°.

Further, θ≤30°.

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.

According to another aspect of the present invention, a compressor is provided, which compressor includes the above exhaust structure.

Further, the compressor further includes a cylinder and a valve plate, the cylinder has a compression chamber, the exhaust flange is connected to the cylinder, and the main exhaust port and the auxiliary exhaust port are connected to the The compression chamber is connected, and the valve plate is installed on the exhaust flange. The valve plate is used to open and close the exhaust end of the main exhaust port.

Applying the technical solution of the present utility model, an exhaust structure is provided. The exhaust structure includes an exhaust flange. The exhaust flange has a main exhaust port. The two ends of the main exhaust port are the air intake end and the exhaust port respectively. The air intake end is connected to the compression chamber of the cylinder, and the groove on the inner wall of the air intake end forms an auxiliary exhaust port. 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 jointly form an exhaust channel. By setting the auxiliary exhaust port, the exhaust area at one end of the exhaust channel connected to the compression chamber is increased, which effectively reduces the compressor's load at high temperatures. Exhaust loss during high-frequency operation. At the same time, the exhaust area of the end of the exhaust channel that matches the valve plate (that is, the exhaust end of the main exhaust port) is small. In this way, when the valve plate is closed, the pressure difference on both sides is small and the valve plate is deformed. Small, ensuring the reliability of the valve plate. Therefore, compared with the existing technology, this solution solves the problem that the exhaust structure is difficult to balance high-frequency exhaust loss and valve plate reliability.

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 indication efficiency will decrease. Therefore, the size of the auxiliary exhaust port needs to be within a certain range to achieve optimal results. At the same time, the compressor operates under wide working conditions and wide frequencies. 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 and low frequencies and all working conditions, and ensure the reliability of the valve plate at high frequencies, through a large number of simulation calculations and analysis, it was found that the new exhaust structure using this solution can effectively ensure the energy efficiency of the compressor and ensure the reliability of the valve plate. When the K value in the new exhaust structure in this solution is designed within the above range, it can ensure better compressor performance.

Description of drawings

The description and drawings that constitute a part of this application are used to provide a further understanding of the present utility model. The illustrative embodiments of the present utility model and their descriptions are used to explain the present utility model and do not constitute an improper limitation of the present utility model. In the attached picture:

Figure 1 shows a schematic diagram of an exhaust structure provided by an embodiment of the present invention;

Figure 2 shows a bottom view of the exhaust structure in Figure 1;

Figure 3 shows a top view of the exhaust structure in Figure 1;

Figure 4 shows a partial enlarged view of Figure 2;

Figure 5 shows a cross-sectional view of Figure 2;

Figure 6 shows the relationship between the energy efficiency and the K value of the compressor using the exhaust structure provided by the present invention.

Among them, the above-mentioned drawings include the following reference signs:

10. Exhaust flange; 20. Main exhaust port; 30. Auxiliary exhaust port; 40. Mounting hole.

Detailed ways

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. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application or uses. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the scope of protection of the present utility model.

As shown in Figures 1 to 6, 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, and a main exhaust port 20. The two ends of the air port 20 are the air inlet end and the exhaust end respectively. The air inlet end is connected with the compression chamber of the cylinder. The groove on the inner wall of the air inlet end forms an auxiliary exhaust port 30. The auxiliary exhaust port 30 is connected to the compression chamber. The main exhaust ports 20 are all connected.

In this solution, 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 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, and realizes that the high-frequency exhaust loss of the exhaust structure is small and the reliability of the valve plate is high.

In this solution, along the axial direction of the main exhaust port 20, the flow areas of the auxiliary exhaust port 30 at different positions 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 .

Specifically, 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, where 0.1≤K≤0.6.

The adoption of a new exhaust structure effectively solves the problem of excessive exhaust loss 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 design requirements of the auxiliary exhaust port 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 found that the new exhaust structure of this scheme can effectively ensure the energy efficiency of the compressor and the reliability of the valve. As shown in Figure 6, 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.

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.

As shown in Fig. 2, 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, so that the auxiliary exhaust port 30 is easy to process, for example, by milling.

As shown in Figure 4, the exhaust flange 10 has a mounting hole 40 for installing a valve plate. 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 circle of the main exhaust port 20 is O ₁ , the center of the preset circle is O ₂ , and the center of the mounting hole 40 is O ₃ ; the connection between O ₁ and O ₂ is the first connection, and the connection between O ₁ and O ₃ is the second connection. Line, the angle between the first connecting line and the second connecting line is θ, where θ≤90°. In this way, the position of the auxiliary exhaust port 30 is limited to the vicinity of the second connection line. Within this range, most of the axial projection of the auxiliary exhaust port 30 falls within the cylinder compression chamber, and the auxiliary exhaust port 30 is arranged at the second connecting line. The range on both sides of the second connection line can effectively increase the exhaust flow area, reduce high-frequency exhaust loss, improve compressor efficiency while ensuring valve reliability.

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

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, where 0.2<h/H≤0.5. If the height of the auxiliary exhaust port 30 is too high, on the one hand, it will increase the clearance volume and reduce the volumetric efficiency of the compressor and thus reduce the energy efficiency. At the same time, if the height is too high, the exhaust flange 10 will weaken locally at the auxiliary exhaust port 30, causing high-frequency During high-load operation, the exhaust flange 10 is prone to deformation and insufficient strength, leading to 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, it will cause The high-frequency exhaust space is reduced, the exhaust loss increases, thereby reducing the compressor indication efficiency, and the compressor energy efficiency will also decrease, so the height of the auxiliary exhaust port 30 needs to be greater than 20% of the height of the main exhaust port.

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.

Another embodiment of the present invention also provides a compressor, which includes the above exhaust structure. In this solution, the main exhaust port 20 and the auxiliary exhaust port 30 jointly form an exhaust channel. By providing the auxiliary exhaust port 30, the exhaust area at one end of the exhaust channel connected to the compression chamber of the cylinder is increased, effectively reducing the The exhaust loss of the compressor during high-frequency operation is reduced. At the same time, the exhaust area of the end of the exhaust channel that matches the valve plate (that is, the exhaust end of the main exhaust port 20) is small, so that the pressure on both sides when the valve plate is closed The difference is small and the valve disc deformation is small, ensuring the reliability of the valve disc. Therefore, compared with the existing technology, this solution solves the problem that the exhaust structure is difficult to balance high-frequency exhaust loss and valve plate reliability, and achieves small high-frequency exhaust loss of the exhaust structure and high valve plate reliability.

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 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.

The above descriptions are only preferred embodiments of the present utility model and are not intended to limit the present utility model. For those skilled in the art, the present utility model may have various modifications and changes. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present utility model shall be included in the protection scope of the present utility model.

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 "comprising" and/or "including" are used in this specification, it indicates the presence of features, steps, operations, devices, components and/or combinations thereof.

Unless otherwise specifically stated, the relative arrangement, numerical expressions and numerical values of the parts and steps described in these embodiments do not limit the scope of the utility model. 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, methods and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, methods 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 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.

In the description of the present utility model, it should be understood that directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" indicate The orientation or positional relationship is usually based on the orientation or positional relationship shown in the drawings, which is only for the convenience of describing the present invention and simplifying the description. In the absence of contrary explanation, these positional words do not indicate or imply the device referred to. Or components must have a specific orientation or be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the scope of protection of the present invention; the orientation words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

For the convenience of description, spatially relative terms can be used here, such as "on...", "on...", "on the upper surface of...", "above", etc., to describe what is shown in the figure. The spatial relationship between one device or feature and other devices or features. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a feature in the figure is turned upside down, then one feature described as "above" or "on top of" other features or features would then be oriented "below" or "below" the other features or features. under other devices or structures". Thus, the exemplary term "over" may include both orientations "above" and "below." The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

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 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).