Horizontal fairing and horizontal compressor

Abstract

The utility model relates to a horizontal fairing and a horizontal compressor, the fairing comprises a fairing body, the bottom of the fairing body extends outwards to form a bottom edge, one end of the bottom edge far away from the fairing body is bent towards one side of the top of the fairing body to form a side turnup, and the side turnup is bent towards the other side of the top of the fairing body. The end, away from the bottom edge, of the side turnup is bent towards the side away from the cover body to form a top turnup, and the angle theta between the top turnup and the central axis of the cover body is larger than or equal to 70 degrees and smaller than or equal to 135 degrees. Compared with the prior art, the oil outlet quantity and the oil content of a system of the horizontal compressor are reduced, so that the cold force and the energy efficiency of the compressor are improved.

Description

Technical Field

[0001] The utility model belongs to the technical field of compressors, and relates to a horizontal fairing and a horizontal compressor. Background Technique

[0002] The horizontal compressor has the advantages of low center of gravity and small vibration, so it is widely used in application systems such as refrigerators and air conditioners. The structure of the horizontal compressor generally includes a housing, a motor, a compression component and a fairing. An exhaust port is provided on the housing. The motor includes a rotor and a stator, and a fairing is arranged between the motor and the compression component. The fairing is used to control the exhaust flow path of the compressor, so that the gas discharged from the compression component is discharged to the exhaust port in a predetermined path within the housing.

[0003] Patent CN208364336U discloses a fairing and its horizontal compressor. The fairing includes a cylinder body and fins. The cylinder body is a hollow structure with both ends open, and a plurality of the fins are arranged on the outer wall of the cylinder body at intervals in the circumferential direction. During actual use, when the exhaust gas flow passes through the space between the fairing and the compressor housing, it will be deflected by the fins, thereby generating a cyclone. During this process, due to the different masses of the oil droplets and the gaseous refrigerant, oil-gas separation will occur during the deflecting flow of the exhaust gas flow, thereby reducing the exhaust oil yield. However, this structure is relatively complex and the cost is relatively high.

[0004] At present, the common fairing structure of the horizontal compressor is that one section of the flanging fits the upper cylinder head for chamfering, and the other section of the flanging tilts upward. This design of the fairing of the existing horizontal compressor has a simple structure, but the cooperation gap between the fairing and the upper cylinder head is small, and the flow area is small, resulting in a large flow rate and easy oil entrainment in the exhaust. There is a problem of high oil spitting rate at high speeds, resulting in low cooling capacity and poor energy efficiency. Summary of the Utility Model

[0005] The purpose of the utility model is to overcome at least one defect existing in the above-mentioned prior art, and provide a horizontal fairing and a horizontal compressor, which reduce the oil output and the oil content rate of the system of the horizontal compressor, thereby improving the cooling capacity and energy efficiency of the compressor.

[0006] The purpose of the utility model can be realized by the following technical solutions:

[0007] One of the technical solutions of the present utility model is to provide a horizontal fairing. The fairing includes a housing body, which has an open end and a closed end. The open end of the housing body extends outward and turns over to form a bottom edge. One end of the bottom edge far from the housing body is bent towards the closed end side of the housing body to form a first flanging. One end of the first flanging far from the bottom edge is bent towards the side far from the housing body to form a second flanging. The angle θ between the second flanging and the central axis of the housing body satisfies 70° ≤ θ ≤ 135°. The second flanging structure ensures that the exhaust flow channel has an appropriate flow area and is conducive to the settlement of oil droplets. If the angle θ exceeds the set angle, it is not conducive to oil blocking, and at the same time, it will also cause the flow area to be too large and not conducive to the cooling of the motor. Therefore, it is necessary to ensure that the angle θ is within the set range.

[0008] Further, the angle α between the first flanging and the bottom edge satisfies 70° ≤ α ≤ 90°. Within the angle range of the first flanging structure, the first flanging can avoid the kidney-shaped hole on the upper cylinder head so that it will not cover the kidney-shaped hole on the upper cylinder head, thereby ensuring that the exhaust flow channel has an appropriate flow area. If the angle α exceeds the set angle, it will affect the flow area of the exhaust flow channel. Therefore, it is necessary to ensure that the angle α is within the set range.

[0009] Further, side holes for upward exhaust are provided on the side wall of the housing body. The gas discharged from the side holes can flow along the first flanging towards the motor side, so that the gas can collide with the gas flowing from the motor side to the pump body side, and reduce the ability of the gas flowing from the motor side to the pump body side to carry oil mist.

[0010] Further, in the plane perpendicular to the central axis of the housing body, in the plane rectangular coordinate system with the projection of the axis of the housing body as the origin, the angle Φ between the connection line of the projection of the side hole and the projection of the axis of the housing body and the horizontal axis x of the coordinate system satisfies: 45° ≤ Φ ≤ 135°. Within this angle range, it can be ensured that the gas discharged from the side holes is upward exhaust rather than downward blowing, and at the same time, the collision effect of the gas discharged upward from the side holes on the gas flowing from the motor side to the pump body side is better. If the angle Φ exceeds the set angle, it will affect the collision effect of the gas discharged from the side holes or even have no effect.

[0011] Further, a central hole is provided at the center of the closed end of the housing body. The central axis of the upper cylinder head passes through the central hole, and an exhaust channel is formed with the upper cylinder head.

[0012] Further, the center of the closed end of the housing body is turned over towards the side far from the bottom edge to form the central hole.

[0013] The second technical solution of the present utility model lies in providing a horizontal compressor, which includes an upper cylinder head and any one of the above-mentioned horizontal fairings. The upper cylinder head includes a cover body, and a central axis is provided at the center of one end face of the cover body. A groove is formed around the central axis on one end face of the cover body, and a top groove wall is provided on the outer periphery of the groove. The fairing is sleeved on the central axis.

[0014] Further, the bottom edge is attached to the groove, and a certain distance needs to be left between both the first flanging and the second flanging and the upper cylinder head.

[0015] Further, the cover body is provided with a kidney-shaped hole. The distance H between the central axis of the kidney-shaped hole and the central axis of the cover body, and the farthest distance h between the bottom edge and the central axis of the cover body satisfy: H≥h, so that the first flanging does not cover the kidney-shaped hole, thus affecting the exhaust flow passage and the flow area.

[0016] Further, the angle A between the groove wall and the groove is 90°≤A≤135°.

[0017] The third technical solution of the present utility model lies in providing an assembly method for the above-mentioned horizontal compressor, which includes the following steps:

[0018] Pass the central axis of the upper cylinder head through the central hole of the fairing. The bottom edge of the fairing is attached to the groove of the upper cylinder head. Adjust the distances between the first flanging and the second flanging of the fairing and the upper cylinder head so that both leave a certain distance from the upper cylinder head, and then fix the fairing on the upper cylinder head.

[0019] Compared with the prior art, the present utility model has the following beneficial effects:

[0020] (1) The flanging design of the present utility model includes two sections. The first section of the flanging design, that is, the flanging angle of the first flanging is relatively small. That is, the angle α between the first flanging and the bottom edge is controlled to be 70°≤α≤90°. Within this angle range, the first flanging can avoid the kidney-shaped hole on the upper cylinder head and will not cover the kidney-shaped hole of the above-mentioned upper cylinder head, thus ensuring that the exhaust flow passage has an appropriate flow area. The second section of the flanging design, that is, the second flanging is an outward flanging with a relatively large folding angle. That is, the angle θ between the second flanging and the central axis of the cover body ranges from 70°≤θ≤135°. While ensuring the motor-side circulation flow field, it is beneficial to the sedimentation of lubricating oil and reduces the oil spitting rate of the compressor;

[0021] (2) The upward exhaust side holes designed in the present utility model and the setting of their angles can, on the one hand, make the gas discharged from the side holes flow along the first flanging towards the motor side, and buffer the gas flowing from the motor side to the pump body side, so as to reduce the flow rate of the gas flowing from the motor side to the pump body side. At the same time, it can also reduce the oil mist carried in the gas and the oil discharge amount of the compressor. On the other hand, within the range of Φ angle, it can ensure that the gas discharged from the side holes is upward exhaust rather than downward blowing. At the same time, the gas discharged upward from the side holes has a better impact effect on the gas flowing from the motor side to the pump body side, thereby preventing the oil mist from entering the pump body side and being carried out of the compressor. Thus, the oil output and the oil content rate of the system of the compressor can be reduced, and the cooling capacity and energy efficiency of the compressor can be improved.

[0022] (3) The present utility model designs the angles of the two-stage flanging structure to increase the exhaust flow area and reduce the exhaust flow rate, thereby reducing oil carry-over in the exhaust. On this basis, combined with the upward exhaust side holes and their angle settings, while reducing the exhaust flow rate, it further changes the flow pattern of the exhaust flow path, so as to further reduce oil carry-over in the exhaust, greatly reduce the oil spitting rate of the compressor, and more effectively improve the performance. Description of the Drawings

[0023] Figure 1 is a schematic cross-sectional structure diagram of a horizontal fairing in the prior art;

[0024] Figure 2 is an assembly schematic diagram of a horizontal fairing and an upper cylinder head in the prior art;

[0025] Figure 3 is an oil-gas distribution cloud diagram of a horizontal fairing in the prior art;

[0026] Figure 4 is a schematic cross-sectional structure diagram of a horizontal fairing in Embodiment 1 of the present utility model;

[0027] Figure 5 is a schematic top view structure diagram of a horizontal fairing in Embodiment 1 of the present utility model;

[0028] Figure 6 is an assembly schematic diagram of a horizontal fairing and an upper cylinder head in Embodiment 1 of the present utility model;

[0029] Figure 7 is an oil-gas distribution cloud diagram of a horizontal fairing in Embodiment 1 of the present utility model;

[0030] Figure 8 is a comparison diagram of the single-cycle oil output of the exhaust pipe of a horizontal compressor in the prior art and Embodiment 1 of the present utility model;

[0031] Figure 9 is a diagram of the parameter improvement of the horizontal compressor in Embodiment 1 of the present utility model compared with the prior art;

[0032] Figure 10 This is a schematic cross-sectional structure diagram of the horizontal fairing in Embodiment 3 of the present utility model.

[0033] Explanation of the markings in the figure:

[0034] 1 - fairing, 11 - bottom edge, 12 - first flanging, 13 - second flanging, 14 - cover body, 15 - side hole, 16 - middle hole;

[0035] 2 - upper cylinder head, 21 - top surface groove, 22 - top surface groove wall, 23 - kidney-shaped hole, 24 - central axis. Specific embodiments

[0036] The present utility model will be described in detail below with reference to specific embodiments. This embodiment is implemented on the premise of the technical solution of the present utility model, and detailed implementation manners and specific operation processes are given, but the protection scope of the present utility model is not limited to the following embodiments.

[0037] In the description of the present utility model, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present utility model. In addition, the terms "first", "second", "third", etc. are used to describe common objects, and only represent different instances referring to the same object, rather than implying that the objects described in this way must be in a given order, whether in time, space, sorting or any other way.

[0038] In the description of the present utility model, it should be noted that unless otherwise clearly specified and limited, the terms "installation", "connection", "connection" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected, or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific situations.

[0039] Embodiment 1:

[0040] A horizontal fairing, as Figure 4 and Figure 5As shown, the fairing 1 includes a housing body 14 which has an open end and a closed end. The open end of the housing body 14 extends outwardly and turns over to form a bottom edge 11. One end of the bottom edge 11 away from the housing body 14 is bent towards the closed end side of the housing body 14 to form a first flanging 12. One end of the first flanging 12 away from the bottom edge 11 is bent towards the side away from the housing body 14 to form a second flanging 13;

[0041] The angle α between the first flanging 12 and the bottom edge 11 ranges from 70°≤α≤90°. Within the angle range of the first flanging 12 structure, the first flanging 12 can avoid the kidney-shaped hole 23 on the upper cylinder head and will not cover the above-mentioned kidney-shaped hole 23, thus ensuring that the exhaust passage has an appropriate flow area. If the angle α exceeds the set range, it will affect the flow area of the exhaust passage. Therefore, it is necessary to ensure that the angle α is within the set range, and preferably 90° in this embodiment;

[0042] The angle θ between the second flanging 13 and the central axis of the housing body 14 ranges from 70°≤θ≤135°. The second flanging 13 structure ensures that the exhaust passage has an appropriate flow area and is conducive to the settlement of oil droplets. If the angle θ exceeds the set range, it is not conducive to oil blocking, and at the same time, it will also make the flow area too large and not conducive to the cooling of the motor. Therefore, it is necessary to ensure that the angle θ is within the set range, and preferably 90° in this embodiment;

[0043] The side of the housing body 14 is provided with a side hole 15 for upward exhaust. Due to the reason of the view, the side hole 15 is not visible in Figure 5 The gas discharged from the side hole 15 can flow towards the motor side along the first flanging 12, so that the gas can collide with the gas flowing from the motor side to the pump body side, and reduce the ability of the gas flowing from the motor side to the pump body side to carry oil mist;

[0044] In the vertical plane of the central axis of the housing body 14, in the plane rectangular coordinate system with the projection of the axis of the housing body 14 as the origin, the angle Φ between the connection line of the projection of the side hole 15 and the projection of the axis of the housing body 14 and the horizontal axis x of the coordinate system ranges from 45°≤Φ≤135°. Within this angle range, it can be ensured that the gas discharged from the side hole 15 is upward exhaust rather than downward blowing, and at the same time, the collision effect of the gas discharged upward from the side hole 15 on the gas flowing from the motor side to the pump body side is better. If the angle Φ exceeds the set range, it will affect the collision effect of the gas discharged from the side hole 15 or even have no effect. In this embodiment, it is preferably 90°, that is, a side hole 15 for upward exhaust is provided at the center of the concave part of the side wall of the housing body 14;

[0045] In addition, the side hole 15 can be one or more. Setting multiple side holes 15 can increase the collision force on the gas flowing from the motor side to the pump body side, as long as the multiple side holes 15 are all within the Φ angle range;

[0046] A middle hole 16 is provided at the center of the closed end of the cover body 14 (i.e., the center of the closed end of the cover body 14 is folded away from the bottom edge 11 to form the middle hole 16). The middle hole 16 allows the central axis 24 of the upper cylinder head 2 to pass through and forms an exhaust passage with the upper cylinder head 2.

[0047] This embodiment also provides a horizontal compressor, as Figure 6 shown, which includes an upper cylinder head 2 and the above-mentioned horizontal fairing. The upper cylinder head 2 includes a cover body. At the center of one end face of the cover body, a central axis 24 is provided. Around the central axis 24 on one end face of the cover body, a groove 21 is formed. A groove wall 22 is provided on the outer periphery of the groove 21. The fairing 1 is sleeved on the central axis 24, that is, the central axis 24 of the upper cylinder head 2 passes through the middle hole 14 of the fairing 1. The bottom edge 11 of the fairing 1 is attached to the top surface groove 21 of the upper cylinder head 2. A certain distance needs to be left between the first flanging 12 and the second flanging 13 of the fairing 1 and the upper cylinder head 2, and the fairing 1 is fixed to the upper cylinder head 2;

[0048] Among them, the cover body is provided with an oval hole 23. The distance H between the central axis of the oval hole 23 and the central axis of the cover body and the farthest distance h between the bottom edge 11 and the central axis of the cover body satisfy: H≥h, so that the first flanging 12 does not cover the oval hole 23, thus affecting the exhaust flow channel and the flow area;

[0049] The angle A between the groove wall 22 and the groove 21 is 90°≤A≤135°. In this embodiment, the angle A is preferably 135°.

[0050] Prior art:

[0051] In the prior art, the structure of the horizontal fairing is as Figure 1 shown. The angle α between the first flanging 12 and the bottom edge 11 is 135°. The angle θ between the second flanging 13 and the central axis of the cover body 14 is 180°. And no side hole 15 is provided on the side wall of the cover body 14. The rest is the same as in Embodiment 1.

[0052] The horizontal compressor with the above-mentioned horizontal fairing structure is as Figure 2 shown. The angle A between the groove wall 22 and the groove 21 is 135°.

[0053] Compare the performance of the horizontal compressor described in the prior art and Embodiment 1:

[0054] Figure 3 is the oil-gas distribution cloud map of the horizontal fairing in the prior art, Figure 7 is the oil-gas distribution cloud map of the horizontal fairing in Embodiment 1 (light blue represents oil-gas). From Figure 3 and Figure 7In comparison, in the prior art, the clearance between the fairing and the upper cylinder head is small, resulting in a large flow rate and easy oil entrainment in the exhaust. A large amount of lubricating oil enters the left pump body side through the clearance. In Embodiment 1, the design of the two-stage flanging structure, that is, the setting of the first flanging 12 and its angle, and the setting of the second flanging 13 and its angle, increases the clearance between the fairing and the upper cylinder head, enlarges the exhaust flow area, and reduces the gas flow rate. As a result, oil entrainment in the exhaust is reduced. On this basis, combined with the upward exhaust side hole 15 and its angle setting, while reducing the exhaust flow rate, the exhaust flow path pattern is further changed, thereby further reducing oil entrainment in the exhaust. From Figure 7 it can be clearly seen that the amount of lubricating oil entering the left pump body side with the exhaust has been reduced a lot.

[0055] The horizontal compressor in the prior art and Embodiment 1 was tested, and the comparison of the average oil output per single cycle obtained is shown in Table 1.

[0056] Case Prior Art Example 1 Improvement Percentage Outlet Oil Flow Rate of Exhaust Pipe Opening (kg / s) 0.059 0.028 52.54％

[0057] Table 1 Comparison of the average oil output per single cycle of the horizontal compressor in the prior art and Embodiment 1

[0058] Figure 8 Figure for comparing the oil output per single cycle of the exhaust pipe of the horizontal compressor in the prior art and Embodiment 1; combined with Figure 8 as well as shown in Table 1, it can be seen that the oil output at the exhaust pipe port in Embodiment 1 has been significantly improved compared with the prior art, and the oil output rate has been reduced by 52.54%. The less oil output at the exhaust pipe port, the lower the oil spitting rate of the compressor, and the less oil in the system, the better the heat exchange effect of the heat exchanger and the higher the cooling capacity.

[0059] Further, trial production performance tests were carried out on the horizontal compressor in the prior art and Embodiment 1:

[0060] Figure 9 Figure for the parameter improvement of the horizontal compressor in Embodiment 1 compared with the prior art. It can be seen that compared with the horizontal compressor in the prior art, the OCR in Embodiment 1 is reduced by 39.02%, the cooling capacity is increased by 2.62%, and the COP is increased by 2.44%.

[0061] It can be seen that the horizontal compressor of the present utility model significantly reduces the oil output and the oil content rate of the system, and improves the cooling capacity and energy efficiency of the compressor.

[0062] Embodiment 2:

[0063] A horizontal fairing, which is different from that in Embodiment 1 in that the side wall of the housing 14 is not provided with a side hole 15.

[0064] The horizontal compressor with the structure described in Embodiment 2 was subjected to performance testing using the same method as in Embodiment 1. The average oil output per single cycle obtained was as follows: the oil output at the exhaust pipe outlet was 0.041 kg / s, and the oil output rate was reduced by 30.51% compared with the prior art.

[0065] It can be seen that in Embodiment 2, two-stage flanging was designed, and the angle α between the first flanging and the bottom edge 11 was controlled within the range of 70° ≤ α ≤ 90° (preferably 90° in this embodiment), and the angle θ between the second flanging 13 and the central axis of the cover body was within the range of 70° ≤ θ ≤ 135° (preferably 90° in this embodiment). Compared with the prior art, the oil output at the exhaust pipe outlet was significantly reduced.

[0066] Compared with Embodiment 1 where a side hole 15 was also designed, although the oil output rate in Embodiment 2 decreased quite a lot, it was obvious that Embodiment 1 had a greater improvement in the oil output at the exhaust pipe outlet. From this, it can be seen that controlling the angle α between the first flanging 12 and the bottom edge 11 and the angle θ between the second flanging 13 and the central axis of the cover body 14 within the set range can increase the exhaust flow area, reduce the exhaust flow velocity, thereby reducing oil entrainment in the exhaust. Coupled with the design of the side hole 15 and its angle, while reducing the exhaust flow velocity, it further changes the flow pattern of the exhaust flow path, thereby further reducing oil entrainment in the exhaust, significantly reducing the oil spitting rate of the compressor, and effectively improving the performance.

[0067] Embodiment 3:

[0068] A horizontal fairing, which is different from that in Embodiment 1 in that the angle α between the first flanging 12 and the bottom edge 11 is 70°, and the angle θ between the second flanging 13 and the central axis of the cover body is 70°. See Figure 10 . The horizontal compressor with the structure described in Embodiment 3 was subjected to performance testing using the same method as in Embodiment 1. The average oil output per single cycle obtained was as follows: the oil output at the exhaust pipe outlet was 0.055 kg / s, and the oil output rate was reduced by 6.78% compared with the prior art.

[0069] It can be seen that controlling the angle α between the first flanging 12 and the bottom edge 11 and the angle θ between the second flanging 13 and the central axis of the cover body 14 within the set range, and coupled with the design of the side hole 15 and its angle, can effectively reduce oil entrainment in the exhaust, effectively reduce the oil spitting rate of the compressor, and effectively improve the performance.

[0070] The above description of the embodiments is provided to enable those of ordinary skill in the art to understand and use the utility model. It is obvious that those skilled in the art can easily make various modifications to these embodiments and apply the general principles described herein to other embodiments without creative efforts. Therefore, the present utility model is not limited to the above embodiments, and the improvements and modifications made by those skilled in the art without departing from the scope of the present utility model according to the disclosure of the present utility model should be within the protection scope of the present utility model.

Claims

1. A horizontal fairing, characterized in that: The fairing (1) comprises a cover body (14), the cover body (14) having an open end and a closed end, the open end of the cover body (14) being folded outward to form a bottom edge (11), an end of the bottom edge (11) away from the cover body (14) being bent toward the closed end of the cover body (14) to form a first flange (12), an end of the first flange (12) away from the bottom edge (11) being bent toward the side away from the cover body (14) to form a second flange (13), and an angle θ between the second flange (13) and the central axis of the cover body (14) being 70°≤θ≤135°.

2. A horizontal fairing according to claim 1, characterized in that: The angle α between the first flange (12) and the bottom edge (11) is 70°≤α≤90°.

3. A horizontal fairing according to claim 1, characterized in that: The side wall of the cover body (14) is provided with a side hole (15).

4. A horizontal fairing according to claim 3, characterized in that: On a plane perpendicular to the central axis of the cover body (14), in a plane rectangular coordinate system with the projection of the axis of the cover body (14) as the origin, an angle Φ between a line connecting the projection of the side hole (15) and the projection of the axis of the cover body (14) and the horizontal axis x of the coordinate system satisfies: 45°≤Φ≤135°.

5. A horizontal fairing according to claim 1, characterized in that: A central hole (16) is provided at the center of the closed end of the cover body (14).

6. A horizontal fairing according to claim 5, characterized in that: The center of the closed end of the cover body (14) is folded toward a side away from the bottom edge (11) to form the center hole (16).

7. A horizontal compressor, characterized in that: The compressor comprises an upper cylinder head (2) and a horizontal fairing as described in any one of claims 1 to 6, wherein the upper cylinder head (2) comprises a cover body, a central axis (24) is arranged at the center of one end surface of the cover body, a groove (21) is arranged on one end surface of the cover body around the central axis (24), a groove wall (22) is arranged on the outer periphery of the groove (21), and the fairing (1) is sleeved on the central axis (24).

8. A horizontal compressor according to claim 7, characterized in that: The bottom edge (11) fits in the groove (21).

9. A horizontal compressor according to claim 7, characterized in that: The cover body is provided with a waist-shaped hole (23), and the distance H between the central axis of the waist-shaped hole (23) and the central axis of the cover body, and the farthest distance h between the bottom edge (11) and the central axis of the cover body, both satisfy: H≥h.

10. A horizontal compressor according to claim 7, characterized in that: An angle A between the groove wall (22) and the groove (21) is 90°≤A≤135°.

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