CN207920858U - A Double Discharge Pressure Rolling Rotor Compressor - Google Patents

Abstract

The utility model discloses a double exhaust pressure rolling rotor compressor, which belongs to the technical field of compressors, and is characterized in that an arc-shaped exhaust groove is arranged on the end surface of the eccentric part of the eccentric wheel shaft close to the front end cover of the cylinder, and the inner surface of the front end cover of the cylinder Radial exhaust grooves are arranged near the sliding plate, and two exhaust ports of high and low pressure are arranged on the front end cover of the cylinder. When working, the motor drives the eccentric shaft to rotate, and the arc-shaped exhaust groove moves with the eccentric shaft; during the process of high-pressure compression and low-pressure compression, the radial exhaust groove and the high- and low-pressure exhaust ports are not connected to ensure the compression; During low-pressure exhaust, the arc-shaped exhaust groove connects the radial exhaust groove with the low-pressure exhaust port; during high-pressure exhaust, the arc-shaped exhaust groove connects the radial exhaust groove with the high-pressure exhaust port. The effect and benefit of the utility model is to make the rolling rotor compressor control the connection between the radial exhaust groove and the high (low) pressure exhaust port through the change of the mutual position of the eccentric wheel shaft and the front end cover of the cylinder, so as to realize double exhaust pressure .

Description

A Double Discharge Pressure Rolling Rotor Compressor

technical field

The utility model relates to the technical field of compressors, in particular to a double exhaust pressure rolling rotor compressor.

Background technique

The rolling rotor compressor has the characteristics of simple structure and easy processing, and is often used as a domestic air energy heat pump compressor. The working principle of the traditional rolling rotor compressor is that the wall of the inner cavity of the cylinder, the outer wall of the rolling rotor and the sliding vane form a closed cylinder volume, that is, the elementary volume. The size of the element volume changes, thus completing the working process of the compressor. In the case of simultaneous heating and heating (providing domestic hot water and heating respectively), in order to save energy, the compressor is required to provide two different exhaust pressures. The traditional rolling rotor compressor can only provide one exhaust pressure, and a single device cannot meet the needs of double exhaust pressure.

Utility model content

In order to overcome the disadvantage that the rolling rotor compressor cannot provide double exhaust pressure, the utility model provides a rolling rotor compressor that realizes two-stage exhaust by relying on the change of the mutual position of the eccentric wheel shaft and the front end cover of the cylinder. The dual exhaust pressure referred to is low pressure when the compression ratio reaches 1.5-2, and high pressure when the compression ratio reaches 3-4 (the compression ratio is the ratio of the exhaust pressure to the suction pressure).

The technical solution adopted by the utility model is: a double exhaust pressure rolling rotor compressor, including a cylinder body, a rolling rotor, an eccentric wheel shaft, an air suction port, a spring, a sliding plate, a front end cover of the cylinder, and a rear end cover of the cylinder. It is characterized in that: the eccentric part of the eccentric wheel shaft is provided with an arc-shaped exhaust groove on the end surface of the front end cover of the cylinder, the inner surface of the front end cover of the cylinder is provided with a radial exhaust groove near the sliding plate, and the cylinder The front cover is provided with a high-pressure exhaust port and a low-pressure exhaust port, and neither the high-pressure exhaust port nor the low-pressure exhaust port is in contact with the radial exhaust groove, and they are respectively located on both sides of the straight line where the radial exhaust groove is located.

Further, positioning pins are embedded on the side of the cylinder block near the front end cover of the cylinder, and positioning holes are provided on the inner side of the front end cover of the cylinder.

When working, the motor drives the eccentric shaft to rotate, and the arc-shaped exhaust groove on the end surface of the eccentric part of the eccentric shaft moves with the eccentric shaft; during high-pressure compression and low-pressure compression, the radial exhaust groove on the front end cover of the cylinder and the high, The low-pressure exhaust ports are not connected to ensure the compression; at the end of the low-pressure compression, the arc-shaped exhaust groove moves to the position where both the radial exhaust groove and the low-pressure exhaust port are in contact, and the radial exhaust groove and the low-pressure exhaust port are connected. The low-pressure exhaust port is connected to ensure the low-pressure exhaust; when the high-pressure compression ends, the arc-shaped exhaust groove moves to the position where it is in contact with both the radial exhaust groove and the high-pressure exhaust port, and the radial exhaust groove and the high-pressure exhaust port are connected. The high-pressure exhaust port is connected to ensure the high-pressure exhaust.

The specific design parameters are:

The shortest distance from the point on the circle of the high-pressure exhaust port and the low-pressure exhaust port to the center of the front end cover is equal, and equal to the distance from the inner end point of the radial exhaust groove to the center of the cylinder front end cover, and equal to the radius of the inner arc of the arc exhaust groove. To ensure that the radial exhaust grooves can be communicated with the high (low) pressure exhaust ports during the rotation of the arc-shaped exhaust grooves. The distance from the outer end point of the radial exhaust groove to the center of the cylinder front end cover is equal to the radius in the cylinder body.

The angle between the line connecting the center of the high-pressure exhaust port and the center of the front end cover of the cylinder and the straight line where the radial exhaust groove body is located is 100-120°; the line connecting the center of the low-pressure exhaust port and the center of the front end cover of the cylinder and the radial exhaust The included angle of the straight line where the groove body is located is 100-120°. The maximum distance from the point on the circle of the high-pressure exhaust port and the low-pressure exhaust port to the center of the front end cover of the cylinder is equal, and less than the shortest distance from the point on the eccentric part of the eccentric wheel shaft to the center of the rotation circle plus the thickness of the rolling rotor, so as to ensure Under the condition of not passing through the arc-shaped exhaust groove, the inner cavity of the cylinder and the high and low pressure exhaust ports will not be connected.

The line connecting the rotation center of the eccentric wheel shaft and the point on the eccentric part of the cylindrical surface of the eccentric wheel shaft farthest from the center of the eccentric wheel shaft rotation is defined as the reference line; The included angle between line and reference line is 140～180 °, and the included angle between the line formed by the dead point of the arc exhaust groove along the opposite direction of rotation and the center of rotation of the eccentric wheel shaft and the reference line is 5～15 °.

Through the above design scheme, the radial exhaust grooves on the front end cover of the cylinder and the high and low pressure exhaust ports are not connected when high-pressure compression and low-pressure compression are required; The air groove and the low-pressure exhaust port are connected by the arc-shaped exhaust groove on the eccentric wheel shaft; during high-pressure exhaust, the radial exhaust groove on the front end cover of the cylinder and the high-pressure exhaust port are connected by the arc-shaped exhaust port on the eccentric wheel shaft connected.

The beneficial effect of the utility model is that, by adopting the above-mentioned technical scheme, the rolling rotor compressor controls the radial exhaust groove and the high (low) pressure exhaust port on the front end cover of the cylinder through the change of the mutual position of the eccentric wheel shaft and the front end cover of the cylinder. Connected or not, the dual exhaust pressure is realized.

Description of drawings

Fig. 1 is the structural representation of the utility model.

Figure 2 is an inside view of the front end cover of the cylinder.

Figure 3 is an end view of the eccentric shaft.

Fig. 4 is an end view of the rolling rotor.

Fig. 5 is a schematic diagram of suction and low-pressure compression process.

Fig. 6 is a schematic diagram of the suction and low-pressure exhaust process.

Fig. 7 is a schematic diagram of the suction and high-pressure compression process.

Fig. 8 is a schematic diagram of the suction and high-pressure exhaust process.

Fig. 9 is a schematic diagram of the end of high-pressure exhaust.

In the figure: 1. Cylinder front end cover, 2. High pressure exhaust port, 3. Suction chamber, 4. Suction port, 5. Sliding plate, 6. Spring, 7. Compression chamber, 8. Cylinder rear end cover, 9 .Cylinder block, 10. Arc exhaust groove, 11. Positioning pin, 12. Rolling rotor, 13. Eccentric wheel shaft, 14. Radial exhaust groove, 15. Positioning hole, 16. Low pressure exhaust port.

Detailed ways

Below in conjunction with accompanying drawing, the utility model is further described.

Please refer to the structural diagram of the utility model shown in accompanying drawing 1, the rolling rotor compressor is mainly composed of a cylinder body 9, a rolling rotor 12, an eccentric wheel shaft 13, an air inlet 4, a spring 6, a sliding plate 5, a cylinder front cover 1, and a cylinder The rear end cover 8, the rolling rotor 12, the arc-shaped exhaust groove 10 on the end surface of the eccentric part of the eccentric wheel shaft 13 close to the front end cover 1 of the cylinder, the high-pressure exhaust port 2 on the front end cover 1 of the cylinder, and the exhaust port 1 on the front end cover 1 of the cylinder The low-pressure exhaust port 16, the positioning hole 15 on the inner surface of the cylinder front cover 1 and the radial exhaust groove 14 (see Figure 2) near the slide plate 5, and the cylinder block 9 are formed by the positioning pin 11 on the cylinder front cover 1 side.

When working, the motor drives the eccentric shaft 13 to rotate, and the arc-shaped exhaust groove 10 on the end surface of the eccentric part of the eccentric shaft 13 moves with the eccentric shaft 13; during high-pressure compression and low-pressure compression, the radial exhaust on the cylinder front end cover 1 Groove 14 is not connected with high-pressure exhaust port 2 and low-pressure exhaust port 16, which ensures the carrying out of high-pressure compression and low-pressure compression; The position where the low-pressure exhaust port 16 is in contact communicates the radial exhaust groove 14 with the low-pressure exhaust port 16 to ensure the low-pressure exhaust; when the high-pressure compression ends, the arc-shaped exhaust groove 10 moves to the radial direction The position where the exhaust groove 14 and the high-pressure exhaust port 2 are in contact communicates the radial exhaust groove 14 and the high-pressure exhaust port 2 to ensure the high-pressure exhaust.

Please refer to attached drawings 2-4. A radial exhaust groove 14 is provided on the inner surface of the cylinder front end cover 1 close to the sliding plate 5 (see Figure 1), and a high-pressure exhaust port 2 and a low-pressure exhaust port 16 are arranged on the cylinder front end cover 1, and the high-pressure exhaust The port 2 and the low-pressure exhaust port 16 are located on both sides of the radial exhaust groove 14 , and neither is in contact with the radial exhaust groove 14 .

The shortest distances from the points on the circle of the high-pressure exhaust port 2 and the low-pressure exhaust port 16 to the center of the cylinder front end cover 1 are equal, both being R ₁ , and equal to the distance R from the inner end point of the radial exhaust groove 14 to the center of the cylinder front end cover 1 ₂ , equal to the arc radius R ₅ inside the arc exhaust groove 10, that is, R ₁ = R ₂ = R ₅ , to ensure that the radial exhaust groove 14 and the high pressure exhaust Air port 2 (low pressure exhaust port 16) communicates. The distance _R3 from the outer end point of the radial exhaust groove 14 to the center of the cylinder front cover 1 is equal to the inner radius of the cylinder block 9 (see Fig. 1).

The angle between the line m between the center of the high-pressure exhaust port 2 and the center of the cylinder front cover 1 and the straight line o where the radial exhaust groove 14 is located is α = 116°; the connection between the center of the circle of the low-pressure exhaust port 16 and the center of the cylinder front cover 1 The angle θ between the line n and the straight line o where the radial exhaust groove 14 is located is 114°. The maximum distances from the points on the high-pressure exhaust port 2 and the low-pressure exhaust port 16 circle to the center of the front end cover of the cylinder are equal, both R ₄ , and are smaller than the shortest distance L ₁ plus the shortest distance from the point on the eccentric part of the cylinder of the eccentric wheel shaft to the center of the rotation circle. The wall thickness δ of the upper rolling rotor, that is, R ₄ <L ₁ + δ, ensures that the inner cavity of the cylinder and the high and low pressure exhaust ports are not connected without passing through the arc exhaust groove.

The eccentric part of the eccentric axle 13 is provided with an arc-shaped exhaust groove 10 on the end surface of the front end cover 1 of the cylinder. The line connecting the center of rotation of the eccentric wheel shaft 13 and the point on the eccentric part of the cylindrical surface of the eccentric wheel shaft 13 farthest from the center of the eccentric wheel shaft 13 rotation circle is defined as the reference line q; 13 The included angle between the line h formed by the center of rotation and the reference line q is γ=160°, and the angle between the dead point of the arc-shaped exhaust groove 10 in the opposite direction of rotation and the center of rotation of the eccentric wheel shaft 13 and the line k formed by the center of the circle and the reference line q Angle β=10°.

Fig. 5 is a schematic diagram of suction and low-pressure compression process. When the rolling rotor 12 crosses the suction port 4, a working cycle starts, and the compressor starts to compress and a new round of suction. The radial exhaust groove 14 on the front end cover 1 of the cylinder is not connected to the high-pressure exhaust port 2 and the low-pressure exhaust port 16. The suction chamber 3 performs suction through the continuous increase in volume, and the compression chamber 7 performs suction through the continuous decrease in volume. compression.

Fig. 6 is a schematic diagram of the suction and low-pressure exhaust process. When the low-pressure compression ends, the arc-shaped exhaust groove 10 on the eccentric shaft 13 moves to a position in contact with both the radial exhaust groove 14 and the low-pressure exhaust port 16, and the low-pressure exhaust port 16 and the radial exhaust groove 14 begin to communicate , low-pressure exhaust begins. During this process, the suction chamber 3 further increases for suction.

Fig. 7 is a schematic diagram of the suction and high-pressure compression process. When the low-pressure exhaust is completed, the compressor immediately performs high-pressure compression. In this process, the radial exhaust groove 14 on the front end cover 1 of the cylinder is not connected to the high-pressure exhaust port 2 and the low-pressure exhaust port 16. The suction chamber 3 continues to inhale, and the volume of the compression chamber 7 is continuously reduced to further compress the gas. .

Fig. 8 is a schematic diagram of the suction and high-pressure exhaust process. After the high-pressure compression ends, the arc-shaped exhaust groove 10 on the eccentric shaft 13 moves to the position where it contacts both the radial exhaust groove 14 and the high-pressure exhaust port 2, and the high-pressure exhaust port 2 and the radial exhaust groove 14 begin to communicate , the high-pressure exhaust starts. During this process, the suction chamber 3 further increases for suction.

Fig. 9 is a schematic diagram of the end of high-pressure exhaust. After the compressor rotates until the arc-shaped exhaust groove 10 on the eccentric wheel shaft 13 and the radial exhaust groove 14 on the cylinder front cover 1 no longer contact each other, the high-pressure exhaust ends. When the rolling rotor 12 further crosses the suction port 4, the suction ends, and the compressor enters the next working cycle.

Through the description and the accompanying drawings, a typical embodiment of a specific structure of the specific implementation is given. Based on the spirit of the utility model, other conversions can also be made. Although the above-mentioned utility model has proposed an existing preferred embodiment, however, these The content is not intended to be limiting.

Various changes and modifications will no doubt become apparent to those skilled in the art upon reading the foregoing description. Therefore, the appended claims should be considered to cover all changes and modifications within the true intent and scope of the present invention. Any and all equivalent scope and content within the scope of the claims should still be regarded as within the intent and scope of the present utility model.

Claims (5)

1. A double exhaust pressure rolling rotor compressor, comprising a cylinder block, a rolling rotor, an eccentric shaft, an air inlet, a spring, a slide plate, a cylinder front end cover, and a cylinder rear end cover, characterized in that: the eccentric shaft The eccentric part of the cylinder is provided with an arc-shaped exhaust groove on the end surface of the front end cover of the cylinder, and the inner surface of the front end cover of the cylinder is provided with a radial exhaust groove near the sliding piece, and the front end cover of the cylinder is provided with a high-pressure exhaust gas The outlet and the low-pressure exhaust port, the high-pressure exhaust port and the low-pressure exhaust port are not in contact with the radial exhaust groove, and are respectively located on both sides of the straight line where the radial exhaust groove is located. 2. A double exhaust pressure rolling rotor compressor according to claim 1, characterized in that: the shortest distances from the points on the circles of the high-pressure exhaust port and the low-pressure exhaust port to the center of the front end cover are equal, and equal to the radial The distance from the inner end point of the exhaust groove to the center of the cylinder front end cover is equal to the radius of the inner arc of the arc exhaust groove; the distance from the outer end point of the radial exhaust groove to the center of the cylinder front end cover is equal to the radius in the cylinder body. 3. A double exhaust pressure rolling rotor compressor according to claim 1, characterized in that: the angle between the line connecting the center of the high-pressure exhaust port and the center of the front end cover of the cylinder and the straight line where the radial exhaust groove body is located The angle between the line connecting the center of the low-pressure exhaust port and the center of the front end cover of the cylinder and the straight line where the radial exhaust groove body is located is 100-120°; The maximum distance from the point to the center of the front end cover of the cylinder is equal and less than the shortest distance from the point on the eccentric portion of the eccentric wheel shaft to the center of the rotating circle plus the thickness of the rolling rotor. 4. A dual-discharge pressure rolling rotor compressor according to claim 1, characterized in that: define the line connecting the center of rotation of the eccentric shaft and the point on the cylinder surface of the eccentric part of the eccentric shaft farthest from the center of rotation of the eccentric shaft is the reference line; the included angle between the line formed by the dead point of the arc-shaped exhaust groove along the rotation direction and the center of rotation of the eccentric wheel shaft and the reference line is 140-180°, and the dead point of the arc-shaped exhaust groove along the opposite direction of rotation is The included angle between the connecting line formed by the rotation center of the eccentric wheel shaft and the reference line is 5-15°. 5. A double exhaust pressure rolling rotor compressor according to claim 1, characterized in that: positioning pins are embedded in the cylinder body near the front end cover of the cylinder, and positioning holes are provided on the inner side of the front end cover of the cylinder.