Rotary air conditioning compressor

Abstract

The present invention provides a rotary air-conditioning compressor, which belongs to the field of mechanical technology. It solves the problem of large friction energy consumption between the blades and the piston of the existing rotary air-conditioning compressor. The rotary air-conditioning compressor includes a cylinder, a crankshaft and a blade. The cylinder is provided with an intake channel and an exhaust channel, and the intake channel and the exhaust channel are respectively located on both sides of the blade; an increasing spring is provided in the cylinder to abut against the tail end of the blade, and during the movement of the piston from the intake channel to the exhaust channel, the compression stroke of the increasing spring first gradually decreases and then gradually increases; during the gradual increase of the compression stroke of the increasing spring, the pressure increase per unit length gradually increases. Before the exhaust valve of the rotary air-conditioning compressor is opened, the increasing spring significantly reduces the force of the blade on the piston, thereby reducing the friction between the blade and the piston, thereby reducing the operating energy consumption of the rotary air-conditioning compressor.

Description

Technical Field

[0001] The invention belongs to the technical field of compressors and relates to a rotary compressor, in particular to a rotary air-conditioning compressor. Background Art

[0002] The motor of the rotary compressor directly drives the rotary piston to rotate to complete the compression of the refrigerant vapor. Since the piston rotates, the compression work is smooth, stable and balanced. In addition, the rotary air compressor has no clearance volume and no interference from the re-expansion gas. Therefore, it has the advantages of high compression efficiency, few parts, small size, light weight, good balance performance, low noise, complete protection measures and low power consumption.

[0003] The R surface of the blade in the rotary compressor contacts the outer circle of the piston and divides the inner cavity of the cylinder into a compression chamber and a suction chamber. When the rotary compressor is running, as the volume of the suction chamber gradually expands, low-pressure refrigerant is sucked in; the volume of the compression chamber gradually decreases, and the refrigerant is gradually compressed. When the pressure value set by the exhaust valve is reached, the refrigerant is discharged. Usually, when the exhaust valve is opened, the piston rotates to the 330°-335° stage. In the 0-270° stage of piston rotation, the refrigerant pressure changes very little, that is, it increases slightly; in the 270°-330° stage, the refrigerant pressure changes significantly, especially after 300°, that is, it increases significantly.

[0004] There are many related documents about rotary compressors, such as the setting structure of the leaf spring of the rotary compressor (application number 200510084041.4), a rotary piston compressor with a stepped spring hole (application number 200720069526.0). The leaf springs currently used in rotary compressors have different shapes, such as equal diameter columnar springs, conical springs, and leaf springs, but their function is to reduce the friction between the spring and the spring hole wall and the stability of the spring operation.

[0005] With the development of society, the requirements for energy saving and consumption reduction of air conditioners are getting higher and higher; for this reason, new refrigerants are continuously promoted and applied, and the output working pressure of compressors is also continuously increased. At present, the output working pressure of some compressors has been increased to 26-28Kg / cm², and even exceeded 40Kg / cm². As the output working pressure of the compressor increases, the pressure of the blades on the outer circle of the piston is also adaptively increased, and the friction between the blades and the piston is objectively present. Reducing the friction loss between the blades and the piston is what the technicians in this field pursue. For this reason, the applicant has proposed a rotary translation piston compressor (application number 201310738478.X); of course, the technicians in this field hope to propose more different technical solutions so that people have more choices. Summary of the invention

[0006] The present invention provides a rotary air-conditioning compressor. The technical problem to be solved by the present invention is how to reduce the energy consumed by the friction between the blades and the piston in the rotary air-conditioning compressor.

[0007] The technical problem to be solved by the present invention can be achieved through the following technical solutions: a rotary air-conditioning compressor, including a cylinder, a crankshaft and blades, the crankshaft is inserted into the chamber of the cylinder, and a piston is sleeved on the crankshaft; the blades are slidingly connected to the cylinder, and the arc-shaped end faces of the blades abut against the outer circumferential surface of the piston, and the cylinder is provided with an intake channel and an exhaust channel, and the intake channel and the exhaust channel are respectively located on both sides of the blades; it is characterized in that an incremental spring abutting against the tail end of the blade is provided in the cylinder, and during the movement of the piston from the intake channel to the exhaust channel, the compression stroke of the incremental spring first gradually decreases and then gradually increases; as the compression stroke of the incremental spring gradually increases, the pressure increase per unit length gradually increases.

[0008] Compared with the existing rotary air-conditioning compressor using linear springs, before the exhaust valve of the rotary air-conditioning compressor opens, the incremental spring significantly reduces the force of the blade on the piston, thereby reducing the friction between the blade and the piston, thereby reducing the operating energy consumption of the rotary air-conditioning compressor.

[0009] The following scheme can make the elastic force increase curve of the incremental spring more consistent with the blade thrust increase curve caused by the refrigerant. As a priority, in the process of gradually increasing compression stroke of the incremental spring, there is a gentle section with a gentle pressure increase and a surge section with a rapid pressure increase. The absolute difference coefficient of the pressure increase values ​​of adjacent unit compression lengths in the gentle section is K1, and the absolute difference coefficient of the pressure increase values ​​of adjacent unit compression lengths in the surge section is K3, and K3>K1.

[0010] Preferably, the progressive spring has a transition section between the gentle section and the sharp section during the gradual increase of the compression stroke, and the absolute difference coefficient of the pressure increase value of adjacent unit compression lengths in the transition section is K2, K3>K2>K1.

[0011] As a priority, the position of the minimum gap between the outer cylindrical surface of the piston and the side of the chamber of the cylinder corresponding to the starting point of the surge section is L1, and the position of the minimum gap between the outer cylindrical surface of the piston and the side of the chamber of the cylinder corresponding to the starting point of the blade thrust surge caused by the operation of the rotary air-conditioning compressor is L2, and the distance between L1 and the exhaust channel is greater than the distance between L2 and the exhaust channel. This solution can not only reduce the absolute difference coefficient of the pressure increase value of adjacent unit compression lengths in the surge section, but also reduce the maximum pressure of the incremental spring.

[0012] In the above-mentioned rotary air-conditioning compressor, the incremental spring includes an equal-pitch cylindrical section and a conical section, the end face of the equal-pitch cylindrical section abuts against the spring seat, and the small end face of the conical section abuts against the blade.

[0013] In the above-mentioned rotary air-conditioning compressor, the incremental spring includes an equal-pitch cylindrical section, a variable-pitch cylindrical section and a conical section. The equal-pitch cylindrical section and the conical section are connected through the variable-pitch cylindrical section. The pitches of the equal-pitch cylindrical section and the variable-pitch cylindrical section are different; the end face of the equal-pitch cylindrical section abuts against the spring seat, and the small end face of the conical section abuts against the blade.

[0014] Preferably, when the pressure of the incremental spring increases rapidly, the equal pitch cylindrical section is in a fully compressed state.

[0015] Preferably, a trapezoidal avoidance groove is provided at the tail end of the blade, and the conical section is embedded in the avoidance groove.

[0016] Preferably, a positioning groove is provided on the bottom surface of the avoidance groove, and the top ring of the cone section is embedded in the positioning groove. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figures 1 to 3 It is a schematic diagram of the cross-sectional structure when the piston is in different states.

[0018] Figure 4 It is a schematic diagram of the structure of the incremental spring and the blade.

[0019] Figure 5 It is a schematic diagram of the relationship between the spring force and the thrust of the refrigerant on the blades and the rotation angle of the piston.

[0020] In the figure, 1, cylinder; 1a, intake passage; 1b, exhaust passage; 2, crankshaft; 3, blade; 3a, avoidance groove; 3b, positioning groove; 4, piston; 5, incremental spring; 5a, equal pitch cylindrical section; 5b, conical section; 6, spring seat. DETAILED DESCRIPTION

[0021] The following are specific embodiments of the present invention and the accompanying drawings to further describe the technical solution of the present invention, but the present invention is not limited to these embodiments.

[0022] Embodiment 1: Figure 1 As shown, the rotary air-conditioning compressor includes a cylinder 1 , a crankshaft 2 , a vane 3 , a piston 4 and an incremental spring 5 .

[0023] The cylinder 1 has a cylindrical chamber, and also has an intake passage 1a, an exhaust passage 1b and a blade slide groove connected to the chamber. The blade slide groove is located between the intake passage 1a and the exhaust passage 1b.

[0024] The crankshaft 2 is inserted into the chamber of the cylinder 1. The piston 4 is sleeved on the eccentric part of the crankshaft 2. The outer side of the piston 4 and the inner side of the cylinder 1 usually leave a gap of less than 0.1 mm, which not only avoids the friction between the outer cylindrical surface of the piston 4 and the inner side of the cylinder 1, but also ensures the sealing performance. The blade 3 is embedded in the blade slot of the cylinder 1. The blade 3 is slidably connected with the cylinder 1, so that the intake channel 1a and the exhaust channel 1b are respectively located on both sides of the blade 3.

[0025] A rectangular coordinate system is established, and the center of the rectangular coordinate system coincides with the center of the cylinder 1 chamber; the blade 3 is defined to be located at 0° of the rectangular coordinate system. When the rotary air-conditioning compressor is running, the crankshaft 2 rotates in the direction indicated by the arrow; then the center line of the intake channel 1a coincides with the 25° line of the rectangular coordinate system, that is, the angle α between the center line of the intake channel 1a and the 0° line of the rectangular coordinate system is 25°; the center line of the exhaust channel 1b coincides with the 345° line of the rectangular coordinate system, that is, the angle β between the center line of the exhaust channel 1b and the 0° line of the rectangular coordinate system is 15°.

[0026] The cylinder 1 also has a spring mounting hole, in which the incremental spring 5 is arranged, and one end of the incremental spring 5 abuts against the tail end of the blade 3. The cylinder 1 is provided with a shell, and a spring seat 6 is provided on the shell, and the other end of the incremental spring 5 abuts against the spring seat 6, so that under the elastic force of the incremental spring 5, the arc end face of the blade 3 always abuts against the outer circumferential surface of the piston 4.

[0027] like Figures 1 to 3 As shown, when the crankshaft 2 rotates, the piston 4 is driven to move, changing the position of the minimum gap between the outer side of the piston 4 and the inner side of the cylinder 1. When the above-mentioned minimum gap is located on the 0° line of the rectangular coordinate system, the compression stroke of the incremental spring 5 is the largest, and when the above-mentioned minimum gap is located on the 180° line of the rectangular coordinate system, the compression stroke of the incremental spring 5 is the smallest; when the above-mentioned minimum gap moves from the 0° line of the rectangular coordinate system to the 180° line in the direction indicated by the arrow, the compression stroke of the incremental spring 5 gradually decreases; when the above-mentioned minimum gap moves from the 180° line of the rectangular coordinate system to the 0° line in the direction indicated by the arrow, the compression stroke of the incremental spring 5 gradually increases. As the compression stroke of the incremental spring 5 gradually increases, the pressure increase per unit length gradually increases.

[0028] like Figure 5 As shown, line X1 indicates the magnitude of the refrigerant thrust on blade 3 at the corresponding angle in the rectangular coordinate system when the above-mentioned minimum gap is located, line X2 indicates the theoretical optimal elastic force of the incremental spring 5 at the corresponding angle in the rectangular coordinate system when the above-mentioned minimum gap is located, and line X3 indicates the elastic force of the linear spring in the prior art at the corresponding angle in the rectangular coordinate system when the above-mentioned minimum gap is located.

[0029] During the gradual increase of the compression stroke of the incremental spring 5, 180° to 270° is a gentle section, and the absolute difference coefficient of the pressure increase value of adjacent unit compression length in the gentle section is set to K1; 270° to 290° is a transition section, and the absolute difference coefficient of the pressure increase value of adjacent unit compression length in the transition section is set to K2; 290° to 0° is a surge section, and the absolute difference coefficient of the pressure increase value of adjacent unit compression length in the surge section is set to K3; thus K3>K2>K1. By comparison, it can be seen that the change state of the elastic force of the incremental spring 5 is consistent with the change state of the thrust force of the refrigerant on the blade 3, that is, within the range of 180° to 270°, the thrust force of the refrigerant on the blade 3 changes relatively slowly, and the change of the elastic force of the incremental spring 5 is also relatively slow. The thrust of the refrigerant on the blade 3 increases significantly after 300°, while the elastic force of the incremental spring 5 increases significantly after 290°; that is, the starting angle at which the elastic force of the incremental spring 5 increases significantly is smaller than the starting angle at which the thrust of the refrigerant on the blade 3 increases significantly, which is not only conducive to controlling the absolute difference coefficient K3 of the pressure increase value of adjacent unit compression lengths in the surge section, but also reduces the maximum elastic force value of the incremental spring 5, thereby reducing the requirements of the rotary air-conditioning compressor on the motor and reducing energy consumption. The transition section allows the elastic force of the incremental spring 5 to transition slowly, avoiding instantaneous changes in the spring, thereby helping to improve the movement stability of the blade 3 and avoid unnecessary noise.

[0030] Compared with the existing linear spring, before the exhaust valve opens, the incremental spring 5 significantly reduces the force of the blade 3 on the piston 4, thereby reducing the friction between the blade 3 and the piston 4, thereby reducing energy consumption. Although the maximum elastic force of the incremental spring 5 is slightly greater than the maximum elastic force of the linear spring, the piston 4 is usually in high-speed rotation and can slide smoothly under the action of inertia and motor driving force. Theoretical calculations and experiments show that the rotary air-conditioning compressor can reduce energy consumption by 2%-3.5%; due to the extremely high popularity of rotary compressors, a small reduction in energy consumption is still of great significance to society.

[0031] like Figure 4As shown, the incremental spring 5 includes an equal pitch cylindrical section 5a and a conical section 5b, the end surface of the equal pitch cylindrical section 5a abuts against the spring seat 6, and the lower end surface of the conical section 5b abuts against the blade 3. A trapezoidal avoidance groove 3a is provided at the tail end of the blade 3, so as to avoid friction between the conical section 5b and the blade 3 after the conical section 5b is compressed. A positioning groove 3b is provided on the bottom surface of the avoidance groove 3a, and the top ring of the conical section 5b is embedded in the positioning groove 3b, so as to significantly improve the consistency of the installation position of the incremental spring 5, improve the compression stability, and achieve the improvement of the operating stability of the rotary air-conditioning compressor. According to the moving stroke of the blade 3 and the compression stroke of the equal-pitch cylindrical segment 5a, the equal-pitch cylindrical segment 5a can be completely compressed when the above-mentioned minimum gap is located in the 270°-290° area of ​​the rectangular coordinate system, that is, the equal-pitch cylindrical segment 5a is used to make the elastic force of the incremental spring 5 form a smooth section, and the conical segment 5b is used to make the elastic force of the incremental spring 5 form a surge section; in other words, by controlling the compression stroke of the equal-pitch cylindrical segment 5a, it is possible to control the position where the elastic force of the incremental spring 5 surges significantly.

[0032] Embodiment 2: The structure and principle of this embodiment are basically the same as those of Embodiment 1. The basic similarities are no longer described in detail, and only the differences are described. The differences are: the incremental spring 5 includes an equal-pitch cylindrical section 5a, a variable-pitch cylindrical section and a conical section 5b, the equal-pitch cylindrical section 5a and the conical section 5b are connected by a variable-pitch cylindrical section, the pitch of the equal-pitch cylindrical section 5a is different from that of the variable-pitch cylindrical section, and the variable-pitch cylindrical section is conducive to forming a smoother elastic force change.

Claims

1. A rotary air-conditioning compressor, comprising a cylinder (1), a crankshaft (2) and a blade (3), wherein the crankshaft (2) is inserted into a chamber of the cylinder (1), and a piston (4) is sleeved on the crankshaft (2); the blade (3) is slidably connected to the cylinder (1), and the arcuate end surface of the blade (3) abuts against the outer circumferential surface of the piston (4); an intake passage (1a) and an exhaust passage (1b) are provided on the cylinder (1), and the intake passage (1a) and the exhaust passage (1b) are respectively located on two sides of the blade (3); and the characteristics are as follows: An incremental spring (5) is provided in the cylinder (1) and abuts against the rear end of the blade (3). The incremental spring (5) comprises an equal pitch cylindrical section (5a) and a conical section (5b). The end face of the equal pitch cylindrical section (5a) abuts against the spring seat (6), and the small end face of the conical section (5b) abuts against the blade (3). In the process of gradually increasing the compression stroke of the incremental spring (5), there is a gentle section in which the pressure rises gently and a surge section in which the pressure rises rapidly. The absolute difference coefficient of the pressure increase value of adjacent unit compression lengths in the gentle section is K1, and the pressure increase value of adjacent unit compression lengths in the surge section is K2. The absolute difference coefficient of the added value is K3, K3>K1; the equal pitch cylindrical section (5a) causes the elastic force of the incremental spring (5) to form a gentle section, and the conical section (5b) causes the elastic force of the incremental spring (5) to form a sharp increase section; in the process of the minimum gap between the outer cylindrical surface of the piston (4) and the chamber side of the cylinder (1) moving from the intake channel (1a) to the exhaust channel (1b), the compression stroke of the incremental spring (5) first gradually decreases and then gradually increases; in the process of the compression stroke of the incremental spring (5) gradually increasing, the pressure increase value per unit compression stroke length of the incremental spring (5) gradually increases.

2. The rotary air-conditioning compressor according to claim 1, characterized in that: In the process of gradually increasing the compression stroke of the incremental spring (5), there is also a transition section between the gentle section and the sharp increase section, and the absolute difference coefficient of the pressure increase values ​​of adjacent unit compression lengths in the transition section is K2, K3>K2>K1.

3. The rotary air-conditioning compressor according to claim 2, characterized in that: The position of the minimum gap between the outer cylindrical surface of the piston (4) and the side surface of the chamber of the cylinder (1) corresponding to the starting point of the surge section is L1, and the position of the minimum gap between the outer cylindrical surface of the piston (4) and the side surface of the chamber of the cylinder (1) corresponding to the starting point of the thrust surge of the blade (3) caused by the operation of the refrigerant of the rotary air-conditioning compressor is L2, and the distance between L1 and the exhaust channel (1b) is greater than the distance between L2 and the exhaust channel (1b).

4. The rotary air-conditioning compressor according to claim 2, characterized in that: The incremental spring (5) further comprises a variable pitch cylindrical section, the equal pitch cylindrical section (5a) and the conical section (5b) are connected via the variable pitch cylindrical section, and the pitches of the equal pitch cylindrical section (5a) and the variable pitch cylindrical section are different.

5. The rotary air-conditioning compressor according to claim 1, 2, 3 or 4, characterized in that: When the pressure of the incremental spring (5) rises rapidly, the equal pitch cylindrical section (5a) is in a completely compressed state.

6. The rotary air-conditioning compressor according to claim 1, 2, 3 or 4, characterized in that: A trapezoidal avoidance groove (3a) is provided at the tail end of the blade (3), and the conical section (5b) is embedded in the avoidance groove (3a).

7. The rotary air-conditioning compressor according to claim 6, characterized in that: A positioning groove (3b) is provided on the bottom surface of the avoidance groove (3a), and the top ring of the cone section (5b) is embedded in the positioning groove (3b).

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