CN205243851U - Compresser cylinder, rolling rotor formula compressing mechanism and compressor - Google Patents

Abstract

The utility model provides a compressor cylinder, a rolling rotor type compression mechanism and a compressor. The compressor cylinder includes a cylinder body with a central hole, the cylinder body is provided with a vane slot for accommodating a blade, and the vane slot includes a first slot communicated with the central hole and a second slot communicated with the first slot The first tank body includes first and second inner walls parallel to each other and radially symmetrical along the central hole, and the first inner wall of the first tank body extends straight to form an inner wall of the second tank body. The rolling rotor type compression mechanism reduces the inclination angle of the blades during operation through the above-mentioned compressor cylinder, thereby improving the stress on the blade grooves and blades, and at the same time improving the contact position between the blades and the blade grooves. Surface quality reduces wear and ensures reliability of the compression mechanism.

Description

Compressor cylinder, rolling rotor type compression mechanism and compressor

technical field

The utility model relates to a compressor cylinder, a rolling rotor type compression mechanism and a compressor.

Background technique

Rolling rotor compressor, also known as rolling piston compressor or fixed vane compressor, uses the rotation of an eccentric rotor in the compressor cylinder to change the working volume of the compressor cylinder, thereby realizing the suction, compression and exhaust of gas .

The compression mechanism commonly used in rolling rotor compressors is shown in Figure 1. The compression mechanism includes an eccentric shaft 1, a compressor cylinder 2, a rotor 3, and blades 4. The compressor cylinder 2 includes a connected blade groove 5 and a spring. The hole 6, wherein, the rotor 3 is driven by the eccentric shaft 1 to make a rotary motion in the compressor cylinder 2, and the vane 4 slides in the vane groove 5 and presses the rotor 3, so as to be separated in the compressor cylinder 2 working cavity.

Fig. 2 is a schematic diagram of the working compression mechanism (referred to as the rolling rotor compression mechanism) adopted by the rolling rotor compressor shown in Fig. 1 . As shown in FIG. 2 , when the rotor 3 rotates in the compressor cylinder 2 , the blade 4 divides the working chamber into a low-pressure chamber 7 on the left and a high-pressure chamber 8 on the right.

Based on the working principle of the compression mechanism, the compression mechanism adopted by the existing rolling rotor compressor has many friction pairs, such as the rolling friction between the rotor 3 and the inner wall of the compressor cylinder 2, the blade 4 and the blade groove 5 Among them, the friction condition between the blade 4 and the blade groove 5 is the worst. Specifically, in the width direction of the blade 4, since there is a certain sliding gap between the blade 4 and the blade groove 5, under the action of high and low pressure, the two sides of the blade 4 (that is, along the width of the blade 4 The two opposite sides in the direction) will be deflected due to the unbalanced force, so as to contact the inner walls on both sides of the vane groove 5 .

The inventors found that the actual stress on the tail part a of the high-pressure surface (that is, the inner wall that is subjected to high pressure) and the head b of the low-pressure surface (that is, the inner wall that is subjected to low pressure) of the blade groove 5 is the largest, that is, the The contact position between the blade 4 and the blade groove 5 is specifically shown in FIG. 3 . FIG. 3 is a partially enlarged view at point A of the rolling rotor type compression mechanism shown in FIG. 2 . Further, the inventors have also found that at the joint between the vane groove 5 and the spring hole 6, since they are all blank surfaces (unprocessed surfaces), sometimes for powder metallurgy parts, there may also be a black skin layer here, resulting in The poor surface quality of the contact parts of the blade 4 and the blade groove 5, combined with the wear caused by the long-term contact between the two, will easily cause the wear of the blade groove 5 and the blade 4, and affect the reliability of use.

Utility model content

The purpose of the utility model is to provide a compressor cylinder, a rolling rotor type compression mechanism and a compressor to solve the problem of low reliability of the existing rolling rotor type compression mechanism.

In order to solve the above technical problems, the utility model provides a compressor cylinder, which includes a cylinder body with a central hole, and a blade groove for accommodating a blade is opened on the cylinder body, and the blade groove includes a A first tank connected to the hole and a second tank communicated with the first tank, the first tank includes a first inner wall and a second inner wall that are parallel to each other and symmetrical along the radial direction of the central hole, Moreover, the first inner wall of the first tank extends straightly to form the first inner wall of the second tank.

Preferably, in the compressor cylinder, the shapes of the cross sections of the first groove body and the second groove body parallel to the radial direction of the central hole are different.

Preferably, in the compressor cylinder, the second tank body further includes a second inner wall parallel to the second inner wall of the first tank body, and the second inner wall of the second tank body passes through an inclined plane It is connected to the second inner wall of the first tank body, and the distance between the first inner wall and the second inner wall of the second tank body is greater than the distance between the first inner wall and the second inner wall of the first tank body.

Preferably, in the compressor cylinder, the second tank body further includes an arc-shaped inner wall, and the arc-shaped inner wall is connected with two inner walls of the first tank body in a smooth transition.

Preferably, in the compressor cylinder, the cross-sections of the first groove body and the second groove body parallel to the radial direction of the central hole have the same shape.

Preferably, in the compressor cylinder, the second tank body further includes a second inner wall parallel to the second inner wall of the first tank body, and the second inner wall of the second tank body passes through The vertical transverse wall is connected to the second inner wall of the first tank body, and the distance between the first inner wall and the second inner wall of the second tank body is greater than the distance between the first inner wall and the second inner wall of the first tank body spacing.

Preferably, in the compressor cylinder, a groove is formed on the first inner wall and/or the second inner wall of the first tank for storing lubricating oil.

Preferably, in the compressor cylinder, the cross-sectional shape of the groove parallel to the radial direction of the central hole is semicircular or semielliptical.

Preferably, in the compressor cylinder, the cylinder body is further provided with a suction hole and an exhaust hole communicating with the central hole.

Preferably, in the compressor cylinder, the compressor cylinder is a cast iron compressor cylinder or a powder metallurgy compressor cylinder.

In addition, the utility model also provides a rolling rotor type compression mechanism, which includes the compressor cylinder as described in any one of the above items.

Preferably, the rolling rotor type compression mechanism further includes a rotor, an eccentric shaft, blades and a driving member, the rotor is driven by the eccentric shaft to perform rotary motion in the central hole, and the driving member is set In the second groove and connected to the blade, the blade is driven by the driving member to reciprocate in the first groove and press against the rotor, so that the compressor cylinder A working chamber is separated inside.

Preferably, in the rolling rotor type compression mechanism, the driving member is a spring structure.

In addition, the utility model further provides a compressor comprising the above-mentioned rolling rotor type compression mechanism.

Compared with the prior art, the compressor cylinder of the utility model can reduce the inclination angle of the blades when they are working by extending the first inner wall of the first groove body matched with the blade straightly to form the first inner wall of the second groove body , so as to improve the stress of the vane groove and the vane, and the surface quality of the contact part of the vane and the vane groove has also been improved, thereby reducing wear and tear. Combining the two aspects, the reliability of the rolling rotor compression mechanism is finally ensured;

In addition, the compressor cylinder of the utility model is provided with two first grooves and second grooves with different shapes in the cross section parallel to the radial direction of the central hole, which facilitates the circulating flow of lubricating oil and more effectively ensures that the rolling rotor type compression mechanism The reliability of the work, and also can reduce the processing cost;

In addition, the compressor cylinder of the utility model is made of cast iron material, which is convenient for processing and reduces manufacturing cost.

Description of drawings

Fig. 1 is a schematic diagram of a compression mechanism used in an existing rolling rotor compressor;

Fig. 2 is a schematic diagram of the working compression mechanism adopted by the rolling rotor compressor shown in Fig. 1;

Fig. 3 is a partial enlarged view at A of the compression mechanism used in the rolling rotor compressor shown in Fig. 2;

Fig. 4 is a schematic diagram of a rolling rotor type compression mechanism according to a preferred embodiment of the present invention;

Fig. 5 is a schematic diagram of the blades tilting when the rolling rotor type compression mechanism shown in Fig. 4 works;

Fig. 6 is a partial enlarged view at B of the rolling rotor type compression mechanism shown in Fig. 5;

Fig. 7 is a schematic diagram of a vane groove according to an embodiment of the present invention;

Fig. 8 is a schematic diagram of a vane groove according to another embodiment of the present invention;

Fig. 9 is a schematic diagram of a vane slot according to yet another embodiment of the present invention.

The reference numerals of the utility model embodiment are as follows:

10-rolling rotor type compression mechanism; 20-eccentric shaft; 30-compressor cylinder; 31-cylinder body; 32-blade groove; 321-first groove body; 321a-first inner wall; 321b-second inner wall; 322a-second inner wall; 322b-transverse wall; 322c-slope; 322d-arc inner wall; 33-groove; 34-exhaust hole; 40-rotor; 50-blade; 50a-head; 50b - Tail.

detailed description

Below in conjunction with accompanying drawing 4～9, the compressor cylinder, rolling rotor type compression mechanism and compressor that the utility model proposes are described in further detail. It should be noted that all the drawings are in very simplified form and use inaccurate scales, which are only used to facilitate and clearly illustrate the purpose of the embodiment of the present utility model.

Fig. 4 shows the structure of a rolling rotor type compression mechanism 10 according to a preferred embodiment of the present invention. In the figure, in order to show the principle of the present invention more clearly, the driving member, the intake device and the exhaust device are omitted and other components known to those skilled in the art.

As shown in FIG. 4 , the rolling rotor type compression mechanism 10 includes an eccentric shaft 20 , a compressor cylinder 30 , a rotor 40 , blades 50 and a driving member (not shown, mainly a spring).

The working principle of the above-mentioned rolling rotor type compression mechanism 10 is: the rotor 40 is driven by the eccentric shaft 20 to make a rotary motion in the compressor cylinder 30, and at the same time, the blade 50 is driven by the driving member to rotate in the compressor cylinder. 30 to reciprocate and press against the rotor 40 to separate the working chamber in the compressor cylinder 30 .

One improvement of the rolling rotor type compression mechanism 10 according to the present invention lies in the compressor cylinder 30 .

Specifically, the compressor cylinder 30 includes a cylinder body 31 with a central hole, and the cylinder body 31 is provided with a blade groove 32 communicated with the central hole and arranged radially (also referred to as a vane groove in the industry). ), the vane slot 32 is used to accommodate the above-mentioned driving member and the vane 50, and the vane slot 32 includes a first slot body 321 and a second slot body 322, and one end of the first slot body 321 is connected to the center The holes communicate with each other, and the other end communicates with the second groove body 322 . When in use, the above-mentioned driving part is arranged in the second groove body 322 and connected to the blade 50. Driven by the driving part, the blade 50 reciprocates in the first groove body 321 and presses against the rotor 40, thereby compressing High and low pressure chambers are separated in the engine cylinder 30. It should be noted here that the "high-pressure chamber" refers to a space under a high-pressure environment, and the "low-pressure chamber" refers to a space under a low-pressure environment, such as a space connected to an air intake device (abbreviated as a suction chamber). Air cavity) is usually a low-pressure cavity, the space connected to the exhaust device (referred to as the exhaust cavity), and the "high pressure" and "low pressure" are only the comparison between the two, and do not limit the difference between the two Specific pressure ranges, that is, the "high pressure" refers to a higher pressure than the "low pressure", and the "low pressure" refers to a lower pressure than the "high pressure".

As shown in Figures 5 and 6, the first groove body 321 includes two first inner walls 321a and second inner walls 321b that are parallel and symmetrical along the radial direction of the central hole, and the vanes 50 are formed on the two inner walls. Radial reciprocating motion in the space. Here, the vane groove 32 is set to have a structure with two groove bodies, so as to accommodate the blade 50 and the above-mentioned driving member respectively, so as to reduce the pressure on the inner wall of the second groove body 322 accommodating the driving member which at least bears the low pressure. Surface quality requirements, thereby reducing the amount of processing and reducing manufacturing costs. In this embodiment, taking the second inner wall 321b of the first tank body 321 as an inner wall subjected to low pressure as an example, the compressor cylinder 30 of the present invention will be described in detail. Moreover, those skilled in the art can easily understand that since the inner wall of the second tank body 322 subjected to the low pressure hardly has frictional contact with other components, the processing accuracy can be appropriately reduced. Moreover, it can also be understood that the two inner walls 321a, 321b of the first groove body 321 are preferably finished planes to reduce contact wear. The finishing plane refers to a surface after precision machining.

Next, based on the description in the background technology, when the above-mentioned rolling rotor type compression mechanism 10 is working, because the blade 50 is under the action of high and low pressure, the two sides of the blade 50 (that is, two opposite sides along the width direction) will be Due to the unbalanced force, it tilts and contacts the two inner walls of the vane slot 32 , as shown in FIG. 5 . FIG. 5 shows a schematic diagram of blades 50 tilting when the rolling rotor type compression mechanism 10 shown in FIG. 4 is in operation.

In order to reduce the inclination angle of the blade 50, the inventors extended the first inner wall 321a of the first groove body 321 straight to form the first inner wall 321a of the second groove body 322, and the first inner wall of the first groove body 321 321a is an inner wall that withstands high pressure, and correspondingly, the second inner wall 321b of the first tank 321 is an inner wall that withstands low pressure.

In the rolling rotor type compression mechanism 10 of the present utility model, the first inner wall 321a of the first tank body 321 that is matched with the vane 50 to withstand the high pressure is extended straight to form the first inner wall 321a of the second tank body 322. On the one hand, it can reduce The angle of inclination of the small blade 50 when it is subjected to high and low pressure can improve the stress of the blade groove 32 and the blade 50. On the other hand, the straightly extended first inner wall 321a becomes a working surface from beginning to end, because the working surface usually It is a non-blank surface, so that the surface quality of the contact portion between the vane 50 and the vane groove 32 can be improved, thereby reducing wear and thereby ensuring the reliability of the rolling rotor type compression mechanism 10 .

FIG. 6 shows a partial enlarged view at point B of the rolling rotor type compression mechanism 10 shown in FIG. 5 . As shown in Figure 6, the head 50a of the blade 50 (near the rotor 40) is against the second inner wall 321b of the first groove 321, and its tail 50b (the end away from the rotor 40) is against the first On the first inner wall 321 a of the tank body 321 . In order to show the improvement of the inclination angle of the blade 50 more clearly, Fig. 6 shows the state of the blade groove 32 before and after the improvement of the blade 50 when it is inclined, wherein the thin dashed line shows the inclination state of the blade 50 before the improvement , the thick solid line shows the inclination posture of the improved rear blade 50 . Obviously, the inclination angle of the improved rear blade 50 is smaller than the inclination angle of the improved front blade 50 .

In this embodiment, the straight extension length of the first inner wall 321a of the first groove body 321 can be set according to the working stroke of the blade 50 in actual use, which is not limited by the present invention. Preferably, when the blade 50 is at the minimum reciprocating stroke, that is, the farthest distance into the blade groove 32 , the tail portion 50 b of the blade 50 still reliably abuts against the first inner wall 321 a of the first groove body 321 .

In addition, in order to reduce the amount of wear and frictional heat when the blades 50 move, the rolling rotor type compression mechanism 10 usually also provides lubricating oil. Here, the inventors set the opening sizes of the first groove body 321 and the second groove body 322 to be different, which facilitates the circulation of lubricating oil in the vane groove 32 , thereby improving the working conditions of each friction surface and improving reliability. It should be noted that the opening size is the size of the cross-section parallel to the radial direction of the central hole, such as the width and length of the groove body.

Optionally, the cross-sections of the first groove body 321 and the second groove body 322 parallel to the radial direction of the central hole have the same shape. For example, the second tank body 322 further includes a second inner wall 322a parallel to the second inner wall 321b of the first tank body 321, and the second inner wall 322a of the second tank body 322 is connected to the second inner wall 322a through a transverse wall 322b perpendicular thereto. The second inner wall 321b of a groove body 321 is connected, and the distance between the first inner wall 321a and the second inner wall 322a of the second groove body 322 is greater than the distance between the first inner wall 321a and the second inner wall 321b of the first groove body 321 , as shown in Figure 7. FIG. 7 shows a schematic view of the vane groove 32 of one embodiment. At this time, the width of the second groove body 322 along the width direction of the first groove body 321 is greater than the width of the first groove body 321, so as to provide enough lubricating oil storage space, so as to ensure smooth flow of lubricating oil, and It also enables the blade 50 to enter the second groove 322 smoothly.

In other embodiments, the shapes of the cross sections of the first groove body 321 and the second groove body 322 parallel to the radial direction of the central hole are different. For example, the second tank body 322 further includes a second inner wall 322a parallel to the second inner wall 321b of the first tank body 321, and the second inner wall 322a of the second tank body 322 is connected to the first tank body 321 through an inclined surface 322c. The second inner wall 321b is connected, and the distance between the first inner wall 321a and the second inner wall 322a of the second groove body 322 is greater than the distance between the first inner wall 321a and the second inner wall 321b of the first groove body 321, as shown in Figure 8 shown. FIG. 8 shows a schematic view of another embodiment of the vane groove 32 . The inclined transition connection is used to facilitate the rapid flow of lubricating oil to ensure the lubricating effect.

In another embodiment, the second tank body 322 further includes an arc-shaped inner wall 322d, and the arc-shaped inner wall 322d is smoothly connected with the two inner walls 321a, 321b of the first tank body 321, as shown in FIG. 9 In this way, on the one hand, the resistance to lubricating oil flow can be reduced, and on the other hand, stress concentration can be eliminated to ensure structural strength. FIG. 9 shows a schematic diagram of a vane slot 32 in yet another embodiment. Preferably, along the width direction of the first groove body 321 , the minimum width of the area adjacent to the first groove body 321 of the second groove body 322 is greater than the width of the first groove body 321 , so as to ensure sufficient flow of lubricating oil.

Continuing to refer to FIG. 7 to FIG. 9 , at least one of the two inner walls 321 a , 321 b of the first groove body 321 is provided with a groove 33 to store lubricating oil and further improve the lubricating condition. Preferably, at least one groove 33 is formed on the first inner wall 321 a of the first groove body 321 , and at least one groove 33 is also formed on the second inner wall 321 b of the first groove body 321 . Optionally, the cross-sectional shape of the groove 33 parallel to the central hole is semi-circular or semi-elliptical, which is convenient for processing.

Continuing to refer to Fig. 4 and Fig. 5, an air suction hole (not shown in Fig. 4 and Fig. 5 ) and an exhaust hole 34 are provided on the cylinder body 31, and the air suction hole is arranged on the blade 50 that bears the low pressure. One side, which communicates with the above-mentioned center hole, so that the gas outside the compressor cylinder 30 enters the above-mentioned center hole, and the exhaust hole 34 is arranged on the side where the blade 50 bears high pressure, and is also communicated with the center hole , to discharge the gas in the compressor cylinder 30.

Based on the above, the compressor cylinder 30 of the present invention is especially suitable for the compressor cylinder 30 made of powder metallurgy materials. Because powder metallurgy parts are prone to black skin layer, the surface quality is poor, therefore, for the compressor cylinder 30 made of powder metallurgy materials, the surface quality of the contact parts of the blade 50 and the blade groove 32 is more obvious, effectively ensuring the blade 50 working reliability. Of course, the materials for making the compressor cylinder 30 include but are not limited to powder metallurgy materials, such as cast iron materials can also be used, the specific utility model is not limited, as long as those skilled in the art face the same technical problems, the utility model is applicable . Among them, the cast iron material is used, which is convenient for processing and low in manufacturing cost.

In addition, the rolling rotor type compression mechanism 10 of the present invention is especially suitable for compressors with small size and large displacement, such as compressors used in air conditioners, refrigerators and other equipment. In addition, since the rolling rotor compression mechanism 10 of the present invention adopts the improved compressor cylinder 30 , please refer to the above-mentioned embodiments for the beneficial effects brought by the compressor cylinder 30 of the rolling rotor compression mechanism 10 .

Further, based on the above-mentioned rolling rotor compression mechanism, the present utility model also provides a compressor including the rolling rotor compression mechanism 10 . Since the compressor adopts the rolling rotor type compression mechanism 10 of the above-mentioned embodiment, the beneficial effect brought by the rolling rotor type compression mechanism 10 of the compressor should refer to the above embodiment accordingly.

To sum up, in the rolling rotor type compression mechanism 10 of the present invention, the first inner wall 321a of the first groove body 321 that cooperates with the vane 50 is straightly extended to form the first inner wall 321a of the second groove body 322. On the one hand, it can Reduce the inclination angle of the vane 50 when it is subjected to high and low pressure, thereby improving the stress on the vane groove 32 and the vane 50. On the other hand, the straightly extended inner wall becomes a working surface from beginning to end. The blank surface, in this way, can improve the surface quality of the blade 50 and the blade groove 32 contacting parts, thereby reducing wear and tear. Combining the above two aspects, the reliability of the rolling rotor type compression mechanism 10 is finally ensured.

In addition, the compressor cylinder 30 of the utility model is provided with two first grooves 321 and second grooves 322 with different shapes in the cross section parallel to the radial direction of the center hole, so as to facilitate the circulation of lubricating oil and ensure the compression mechanism more effectively. Reliability of work, moreover, can also reduce processing costs. In addition, the compressor cylinder 30 of the present invention is made of cast iron material, which facilitates processing and reduces manufacturing costs.

The above description is only a description of the preferred embodiments of the present utility model, and is not any limitation to the scope of the present utility model. Any changes and modifications made by those of ordinary skill in the field of the utility model according to the above disclosures all belong to the protection scope of the claims .

Claims (14)

1. A compressor cylinder, comprising a cylinder body with a central hole, the cylinder body is provided with a vane slot for accommodating a blade, and the vane slot includes a first groove communicated with the central hole and a The second tank connected to the first tank is characterized in that the first tank includes a first inner wall and a second inner wall that are parallel to each other and symmetrical along the radial direction of the central hole, and the first The first inner wall of a tank extends straightly to form the first inner wall of the second tank. 2 . The compressor cylinder according to claim 1 , wherein the shapes of the cross sections of the first groove body and the second groove body parallel to the radial direction of the central hole are different. 3 . 3. The compressor cylinder according to claim 2, wherein the second tank body further comprises a second inner wall parallel to the second inner wall of the first tank body, and the second inner wall of the second tank body The two inner walls are connected to the second inner wall of the first tank body through a slope, and the distance between the first inner wall and the second inner wall of the second tank body is larger than the first inner wall and the second inner wall of the first tank body. Spacing of inner walls. 4. The compressor cylinder according to claim 2, wherein the second tank body further comprises an arc-shaped inner wall, and the arc-shaped inner wall transitions smoothly with the two inner walls of the first tank body connect. 5 . The compressor cylinder according to claim 1 , wherein the cross-sections of the first groove body and the second groove body parallel to the radial direction of the central hole have the same shape. 6. The compressor cylinder according to claim 5, wherein the second tank body further comprises a second inner wall parallel to the second inner wall of the first tank body, and the second inner wall of the second tank body The two inner walls are connected to the second inner wall of the first tank body through a transverse wall perpendicular thereto, and the distance between the first inner wall and the second inner wall of the second tank body is larger than the first inner wall of the first tank body Distance from the second inner wall. 7. The compressor cylinder according to claim 1, wherein a groove is formed on the first inner wall and/or the second inner wall of the first groove for storing lubricating oil. 8 . The compressor cylinder according to claim 7 , wherein the cross-sectional shape of the groove parallel to the radial direction of the central hole is a semicircle or a semiellipse. 9. The compressor cylinder according to claim 1, characterized in that, the cylinder body is further provided with a suction hole and a discharge hole communicating with the central hole. 10. The compressor cylinder according to claim 1, wherein the compressor cylinder is a cast iron compressor cylinder or a powder metallurgy compressor cylinder. 11. A rolling rotor type compression mechanism, characterized by comprising the compressor cylinder according to any one of claims 1 to 10. 12. The rolling rotor type compression mechanism according to claim 11, further comprising a rotor, an eccentric shaft, blades and a driving member, the rotor is driven by the eccentric shaft to make a rotary motion in the central hole , the driving member is arranged in the second groove and connected to the blade, the blade is driven by the driving member to reciprocate in the first groove and press against the rotor, so as to A working chamber is separated in the cylinder of the compressor. 13. The rolling rotor type compression mechanism according to claim 12, wherein the driving member is a spring structure. 14. A compressor, characterized by comprising the rolling rotor type compression mechanism according to any one of claims 11-13.