CN201326543Y - Vane type rotary compressor - Google Patents

Abstract

A vane-type rotary compressor, including a rotor 1, a cylinder 2, vanes 3 and an end cover; the rotor 1 is biased in the cylinder 2, the outer surface of the rotor 1 is in tangential contact with the inner surface of the cylinder 2, and the rotor 1 There is an arc groove 8 on the top; the blade 3 is connected with the cylinder 2 and both sides by fastening and sealing; it is characterized in that it is provided with a first slider 4a and a second slider 4b, and the first slider 4a and the second The slider 4b is fitted in the arc groove 8 and rotates with it; because two independent sliders are used instead of the integral rotating column, the mating surfaces of the first slider 4a and the second slider 4b and the blade 3 can be very convenient Processing and processing, including grinding and various surface treatments, so that high-precision size, shape, position, surface roughness, flatness and surface hardness can be obtained, so they cooperate with the blade 3 more smoothly and reduce friction loss And leakage loss can be reduced, which is beneficial to reduce the shaft power consumption of the compressor.

Description

A vane rotary compressor

technical field

The utility model relates to a compressor, in particular to a vane type rotary compressor, more specifically to a vane type rotary compressor with a rotary column structure.

Background technique

The vane compressor has the advantages of small size, light weight, simple structure and good dynamic balance performance, so it is widely used in the fields of air compression, refrigeration and air conditioning. However, the vane of the traditional vane compressor has relative motion relative to the cylinder and the end cover, so there must be a certain movement gap between them, which brings hidden dangers such as leakage loss and friction loss. In order to overcome the above-mentioned disadvantages of the traditional vane compressor, a rotary compressor that fastens and seals the vane, the cylinder and the end cover together has appeared, which includes the cylinder, the rotor, the vane, the end cover and the rotating column; The cylinder has a circular hole-shaped inner surface, the rotor has a cylindrical outer surface, the rotor is offset in the cylinder, the axis of the rotor is arranged parallel to the axis of the cylinder, and the outer surface of the rotor is in rotational contact with the inner surface of the cylinder Fitting; the rotating column is cylindrical, and a flat groove is opened on the rotating column, and the blade is flat, and an arc groove is opened on the rotor along the axial direction, and the rotating column is fitted on the arc The blades are inserted into the flat grooves of the rotating column and slidably matched with them, the outer ends of the blades are tightly and sealed connected with the cylinder, and the side ends of the blades are tightly and sealed connected with the end cover; the above-mentioned compressor There are two modes of operation: one is that the axis of the cylinder is a fixed axis, and the axis of the rotor rotates around the axis of the cylinder, and the rotor also swings around its own axis, and the blades, cylinder and end cover Both are in a stationary state, which is the so-called stationary vane compressor; another way is that the axis of the cylinder and the axis of the rotor are both fixed axes, and the rotor and the cylinder rotate around their respective axes respectively. When the blades, cylinder and end cover are in a rotating state, this is the so-called rotary cylinder rotary compressor; the biggest feature of the above compressor is that the blades, cylinder and end cover are tightly and sealed together, so there is no longer any gap between them. Clearance of movement, i.e. absence of leakage losses and frictional losses. However, the actual physical prototype test found that whether the above-mentioned compressors are stationary vane compressors or fastened vane compressors, there is a large friction loss between their rotors and vanes, resulting in the shaft of the compressor The main reason for the increase in work is that the above-mentioned rotary column adopts an integral structure, and the mating surface between the flat groove of the rotary column and the blade is difficult to process with high precision, and the roughness and flatness of the flat groove are not easy to ensure, resulting in compression The friction power consumption of the machine increases.

Contents of the invention

Aiming at the above-mentioned problems existing in the vane compressor with the rotary column structure, the utility model provides a vane rotary compressor, the purpose of which is to effectively solve the problem of high frictional power consumption between the flat groove of the rotary column and the vane, which causes the shaft of the compressor to The problem of power increase.

In order to achieve the above object, the technical solution adopted by the utility model is: provide a vane type rotary compressor, which includes a rotor, a cylinder, vanes and end covers; the rotor has a cylindrical outer surface, and the cylinder There is a circular hole-shaped inner surface, and the blades are flat; the rotor is biased in the cylinder, the axis of the rotor is parallel to the axis of the cylinder, and the outer surface of the rotor is in tangential contact with the inner surface of the cylinder; the said The outer end of the vane is tightly and sealed connected with the cylinder, and the side end of the vane is tightly and sealed connected with the corresponding end cover. The outer surface of the two sliders includes a cylindrical arc surface, a planar sliding surface and two parallel column end surfaces; a circle parallel to the rotor axis is provided on the rotor. arc groove, the slider is fitted in the arc groove, the arc surface of the slider is in rotational contact with the arc groove, and the sliding mating surfaces of the two sliders are arranged face to face and parallel to the blades respectively. The two working surfaces of the slider are in sliding contact and fit, and the column end faces of the slider are in sliding contact with the end covers on both sides.

The utility model adopts the structural scheme of two independent sliders instead of the integral rotating column, so the mating surface of the slider and the blade can be processed and processed very conveniently, including grinding and various surface treatments, so high-precision dimensions can be obtained , shape, position, surface roughness, flatness and surface hardness, etc., so they cooperate with the blades more smoothly, friction loss and leakage loss can be reduced, and the result is very beneficial to reduce the shaft work consumption of the compressor.

Description of drawings

Fig. 1 is a structural schematic diagram of an embodiment of a vane type rotary compressor of the present invention;

Fig. 2 is an axonometric view of a slider of a vane rotary compressor shown in Fig. 1;

Fig. 3 is a schematic diagram of a vane rotary compressor of the present invention using stationary vanes;

Fig. 4 is a schematic diagram of a vane rotary compressor adopting a rotary cylinder scheme of the utility model;

Fig. 5 is a schematic diagram of the assembly structure of a pair of sliders of a vane rotary compressor of the present invention;

Fig. 6 is a schematic diagram of another assembly structure of a pair of sliders of a vane rotary compressor of the present invention;

Fig. 7 is a schematic diagram of another assembly structure of a pair of sliders of a vane rotary compressor of the present invention;

Fig. 8 is a schematic diagram of another assembly structure of a pair of sliders of a vane rotary compressor of the present invention.

Detailed ways

Fig. 1 and Fig. 2 respectively show a structural schematic view of an embodiment of a vane type rotary compressor of the present invention and an axonometric view of a slider. In this embodiment, the vane rotary compressor includes a rotor 1, a cylinder 2, a vane 3, a first slider 4a, a second slider 4b, and an end cover (not shown); the rotor 1 has A cylindrical outer surface, the cylinder 2 has a circular hole-shaped inner surface, the blade 3 is flat and its two working surfaces are parallel to each other, and the first slider 4a and the second slider 4b have cylindrical arc-shaped arc surface 5, planar sliding mating surfaces 6a and 6b, two column end faces 7a and 7b parallel to each other and perpendicular to sliding mating surfaces 6a and 6b; the rotor 1 is biased in the cylinder 2, and the axis of the rotor 1 is The rotor axis O1, the axis of the cylinder 2 is the cylinder axis O2, the rotor axis O1 and the cylinder axis O2 are set parallel to each other, the distance between the two axes is the eccentricity of the rotor 1 relative to the cylinder 2, the outer surface of the rotor 1 and the inner surface of the cylinder 2 The hole surface is tangentially matched (movement gap or oil film gap is allowed); the vane 3 is parallel to the cylinder axis O2, and its outer end is tightly and sealed with the cylinder 2. The best position of the vane 3 is arranged along the radial direction of the cylinder 2. The two sides of the blade 3 are respectively fastened and sealed with the corresponding two end covers (not shown in the figure); Connection structures such as rivet connection, welding connection or interference connection, adhesive connection, etc. can also be tightly sealed, and even elastic sealing bodies such as rubber, plastic, copper sheet, paper pad, fiber, sealant, etc. can be laid on the connection. etc., the blade 3 of the embodiment shown in Fig. 1 adopts a connection structure embedded into the cylinder 2; an arc groove 8 parallel to the rotor axis O1 is opened on the rotor 1, and the first slider 4a and the second slider 4a The second sliding block 4b is fitted in the arc groove 8 and rotates with it through the arc surface 5, wherein the sliding matching surface 6a of the first sliding block 4a and the sliding matching surface 6b of the second sliding block 4b face each other parallel to each other. Set and combine into a chute, the blade 3 is inserted into the chute and slidably fit with it; taking the first slider 4a as an example, its circular arc surface 5 and sliding mating surface 6a are perpendicular to the column end surfaces 7a and 7b, The column end surfaces 7a and 7b are slidingly fitted with the end covers on both sides; in order to drive the rotor 1 to move, a rotating shaft 9 is coaxially arranged at the center of the rotor 1, and the rotating shaft 9 can directly drive the rotor 1 (not shown in the figure) or The rotor 1 is driven by the bearing 10 (as shown in the figure), the bearing 10 can be a rolling bearing or a sliding bearing, and the rotating shaft 9 can be directly driven by a motor, or indirectly driven by the motor through a coupling, a belt or a gear; As far as the cylinder axis O2 is concerned, the rotating shaft 9 belongs to the eccentric journal structure; obviously, a closed crescent-shaped space is surrounded by the outer surface of the rotor 1, the inner surface of the cylinder 2 and the end covers on both sides, and the blade 3 will The space is divided into two working chambers, that is, the suction chamber 11 and the compression chamber 12. When the compressor is working, the volume of the suction chamber 11 gradually increases, and the volume of the compression chamber 12 gradually decreases. A suction port 13 is provided on the cylinder 2 to communicate with the suction chamber 11, and an exhaust port 14 and a compression chamber 12 are arranged on the end cover. Stomach and air intake hole are set on the end cover, in order to prevent gas from going back in the cylinder 2, an exhaust check valve (not shown) can be set at the exhaust port 14; In the event of overcompression, it is very necessary to reduce the exhaust back pressure. One of the measures is to set an exhaust expansion chamber (not shown in the figure) immediately behind the exhaust check valve, so that the instantaneously discharged high-pressure gas has a Temporarily accommodate the transitional space to alleviate the excessive back pressure caused by the blockage caused by the small flow section of the exhaust pipe. Practice has proved that this structural scheme can effectively prevent the compressor from overpressure, and the exhaust pressure of the compressor is set The ratio to the intake pressure is ε, and the displacement per revolution of the compressor is Vh, so the volume Vp of the exhaust expansion chamber should be greater than or equal to the ratio of Vh to ε, that is, Vp≥Vh/ε, of course, the higher the value of Vp The larger it is, the better the effect of eliminating overpressure, but this will cause the volume of the compressor to increase excessively;

Figure 3 shows the working principle diagram of a vane-type rotary compressor of the present invention adopting the scheme of stationary vanes (the turning direction of the compressor is clockwise). Obviously, the rotor 1 rotates around the cylinder axis O2 on the one hand and on the other hand It also swings around its rotor axis O1 at the same time. It is easy to see that the cylinder axis O2 is a fixed axis at this time (allowing the shaking caused by the existence of the fit gap), while the blade 3, cylinder 2 and end cover are all in a static state , the stationary vane compressor gets its name from this;

Figure 4 shows the working principle diagram of a vane type rotary compressor of the present invention adopting the rotary cylinder scheme (the direction of rotation of the compressor is counterclockwise), it is not difficult to find that the rotor 1 is fixed around its rotor axis O1 Rotate, the cylinder 2, blade 3 and end cover rotate around the cylinder axis O2, at this time, the rotor axis O1 and the cylinder axis O2 are both fixed axes (shaking caused by the fit gap is allowed), due to the cylinder 2 It is in a rotating state, so the rotary cylinder rotary compressor gets its name;

Figure 5 is a schematic diagram of the assembly structure of a pair of sliders of a vane type rotary compressor of the present invention. In this embodiment, the outer edges of the first slider 4a and the second slider 4b are covered by A plane is cut to form a small flat top 15, this structure can reduce the clearance volume of the compressor, thereby reducing the power consumption of the compressor;

Figure 6 is a schematic diagram of another assembly structure of a pair of sliders of a vane type rotary compressor of the present invention. In this embodiment, the same as the embodiment described in Figure 1 is the first slider The radius of the arc surface 5 of the block 4a and the second slide block 4b is equal, but the difference is that the first slide block 4a and the second slide block 4b are in an asymmetric state, that is, the first slide block 4a and the second slide block The layout of the block 4b is offset relative to the vane 3, especially the second slider 4b is located on the side of the compression chamber 12, so it can be appropriately enlarged to increase the sealing performance and reduce the distance between it and the vane 3. Specific pressure;

Fig. 7 is a schematic diagram of another assembly structure of a pair of sliders of a vane type rotary compressor of the present invention, which is different from the embodiment described in Fig. 1 and Fig. 6, in this embodiment, The radius of the arc surface 5 of the first slide block 4a and the second slide block 4b is unequal, because the second slide block 4b is positioned at this side of the compression chamber, so the radius of its arc surface can be selected to be larger, so it can be Reduce its specific pressure on the blade 3 and increase the sealing performance, similar to the embodiment described in Figure 6, at this time the layout of the first slider 4a and the second slider 4b is also in an offset state relative to the blade 3;

Figure 8 is a schematic diagram of another assembly structure of a pair of sliders of a vane type rotary compressor of the present invention. In this embodiment, the first slider 4a and the second slider 4b are at the root There is a contact surface 16, which can coordinate and distribute the stress conditions of the first slider 4a and the second slider 4b;

The utility model adopts the structural scheme of two independent sliders of the first slider 4a and the second slider 4b to replace the integral rotating column, so the mating surfaces of the first slider 4a, the second slider 4b and the blade 3 can be very conveniently Processing and treatment, including grinding and various surface treatments, so that high-precision size, shape, position, surface roughness, flatness and surface hardness can be obtained, so they cooperate with the blade 3 more smoothly, friction loss and The leakage loss can be reduced, which is very beneficial to reduce the shaft work consumption of the compressor.

Claims (10)

1. A vane type rotary compressor, comprising a rotor (1), a cylinder (2), blades (3) and an end cover; the rotor (1) has a cylindrical outer surface, and the cylinder (2) has a The inner surface of the circular hole, the blade (3) is flat; the rotor (1) is offset in the cylinder (2), the rotor axis (O1) is set parallel to the cylinder axis (O2), and the outer surface of the rotor (1) The surface is in tangential contact with the inner surface of the cylinder (2), and the rotor (1) is provided with an arc groove (8); the outer end of the blade (3) is tightly and sealed connected with the cylinder (2), and the blade (3) ) are tightly and sealedly connected with the corresponding end cap respectively; it is characterized in that a first slider (4a) and a second slider (4b) are provided, and the first slider (4a) and the second The sliders (4b) are fitted in the circular arc groove (8) and rotated with it, and the first slider (4a) and the second slider (4b) respectively have planar sliding mating surfaces (6a) (6b ), the sliding mating surfaces (6a) (6b) are arranged face-to-face in parallel and constitute a chute, and the blade (3) is inserted into the chute and slidably fits with it. 2. A vane type rotary compressor according to claim 1, characterized in that the cylinder axis (O2) is a fixed axis, and the rotor (1) rotates around the cylinder axis (O2) on the one hand, and on the other hand At the same time, it swings around its rotor axis (O1), and the blades (3), the cylinder (2) and the end cover are all in a static state. 3. A vane type rotary compressor according to claim 1, characterized in that the rotor axis (O1) and the cylinder axis (O2) are both fixed axes, and the rotor (1) moves around the rotor axis (O1). Fixed axis rotation, cylinder (2), blade (3) and end cover carry out fixed axis rotation around cylinder axis (O2). 4. A vane type rotary compressor according to any one of claims 1 to 3, characterized in that a discharge expansion chamber is arranged behind the discharge check valve. 5. A vane type rotary compressor according to any one of claims 1 to 4, characterized in that the outer edges of the first slider (4a) and the second slider (4b) are small flat tops (15) shape. 6. A vane type rotary compressor according to any one of claims 1 to 4, characterized in that the first slider (4a) and the second slider (4b) are asymmetrical, that is, the first The slider (4a) and the second slider (4b) are not equal in size and their layout is offset relative to the blade (3). 7. A vane type rotary compressor according to any one of claims 1 to 4, characterized in that the first slider (4a) and the second slider (4b) have a contact surface (16) at the root. 8. A vane type rotary compressor according to any one of claims 1 to 7, characterized in that a rotating shaft (9) is coaxially arranged at the central part of the rotor (1). 9. A vane type rotary compressor according to claim 8, characterized in that the rotating shaft (9) is directly driven by a motor. 10. A vane type rotary compressor according to claim 9, characterized in that the rotating shaft (9) is indirectly driven by a motor through couplings, belts or gears.

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