Oil baffle assembly, rotor assembly and compressor

Abstract

An oil baffle assembly, a rotor assembly and a compressor. The oil baffle assembly comprises: a first-stage oil baffle (1), wherein a flange (11), a first counterweight (12) and a plurality of support columns (13) are provided on the side of the first-stage oil baffle (1) that faces a rotor core (3), the flange (11) is configured to accommodate an end portion of a crankshaft (7), mounting holes (14) are provided in the first counterweight (12) and the support columns (13), and a connecting member (8) connects the first-stage oil baffle (1) to the rotor core (3) by means of the mounting holes (14); and a second-stage oil baffle (2) which is arranged on the side of the first-stage oil baffle (1) that faces away from the rotor core (3). The oil baffle assembly enlarges the coverage space of a rotational flow field in radial and axial directions, and can enable frozen oil dissolved in gas to be separated out in a large proportion and flow back into a compressor oil pool, thereby improving an oil-gas separation effect of an oil-gas separation baffle.

Description

Oil baffle assembly, rotor assembly and compressor

[0001] The present application claims priority to Chinese Patent Application CN202410532910.8, filed on April 29, 2024, entitled "Oil baffle assembly, rotor assembly and compressor", the entire contents of which are incorporated herein by reference. TECHNICAL FIELD

[0002] The present application relates to the field of compressors, and specifically provides an oil baffle assembly, a rotor assembly and a compressor. BACKGROUND

[0003] The refrigeration oil plays a role of lubrication, cooling, sealing and the like in the compressor. During the operation of the compressor, if a large amount of refrigeration oil is discharged from the compressor exhaust pipe along with the refrigerant, enters the condenser, the evaporator and the system pipeline, and then condenses an oil film on the heat transfer wall of the condenser and the evaporator, the heat conductivity coefficient of the oil film is small, which reduces the heat exchange efficiency of the condenser and the evaporator. In particular, when the oil discharge amount of the compressor is too large, the part of the refrigeration oil cannot return to the oil pool of the compressor in time, which causes the oil surface of the oil pool to be too low, so that the lubrication and sealing of each moving pair and each matching surface of the pump body assembly cannot be guaranteed, thereby affecting the reliability and performance of the compressor.

[0004] One of the existing conventional technical solutions for reducing the oil discharge amount of the compressor is to install only one layer of oil baffle on the upper end of the rotor. The one layer of oil baffle generates a one-level rotating flow field space at the upper end of the rotor during the operation of the compressor. The rotating flow field covers a small space in the radial and axial directions of the compressor, so that the centrifugal force generated is limited, and the refrigeration oil dissolved in the gas cannot be separated out in a large proportion.

[0005] For example, Chinese Patent Application CN101769257 B discloses an oil-gas separation baffle for an air conditioner compressor. The oil-gas separation baffle is arranged at the upper end of the rotor, and includes a circular plate and a plurality of blades arranged uniformly around the edge of the circular plate. The surface of the circular plate is provided with a plurality of riveting holes for riveting with the rotor. The blade is a C-shaped thin plate, the lower part of which is fixed to the edge of the circular plate in a perpendicular manner to the surface of the circular plate, and the middle part and above thereof extends radially outward in a manner that forms an acute angle α with the lower part. When the rotor operates at a high speed, the blade of the oil-gas separation baffle can form a strong centrifugal force, so that the oil droplets are thrown to the shell and fall down, thereby achieving the purpose of being separated from the refrigerant and lubricating oil mixture. However, the rotating flow field formed by the oil-gas separation baffle in the above-mentioned application covers a small space in the radial and circumferential directions of the compressor, so that the proportion of the refrigeration oil separated from the gas is small. In addition, the distance between the blades is too large, which further reduces the oil-gas separation effect.

[0006] Correspondingly, there is a need in the art for a new technical solution to solve the above problems. SUMMARY

[0007] The present application aims to solve the above technical problems, i.e., to solve the problem of poor oil-gas separation effect of the existing compressor oil-gas separation baffle. To this end, the present application provides an oil baffle assembly, comprising: a primary oil baffle, the primary oil baffle being provided with a flange, a first balance block and a plurality of struts on one side facing the rotor core, the flange being used to accommodate the end of the crankshaft, the first balance block and the struts being provided with mounting holes, and a connecting piece connecting the primary oil baffle and the rotor core through the mounting holes; and a secondary oil baffle, the secondary oil baffle being provided on the side of the primary oil baffle away from the rotor core.

[0008] In the above specific embodiment with the oil baffle assembly, the secondary oil baffle comprises: an axial oil baffle extending in the axial direction; and an outwardly expanding oil baffle, the two ends of the axial oil baffle being connected with the primary oil baffle and the outwardly expanding oil baffle respectively, and the outwardly expanding oil baffle extending radially outwardly at an acute angle of θ with the axial oil baffle.

[0009] In the above specific embodiment with the oil baffle assembly, the outwardly expanding oil baffle forms an acute angle of θ with the axial oil baffle, wherein 10°≤θ≤30°.

[0010] In the above specific embodiment with the oil baffle assembly, the outer diameter of the outwardly expanding oil baffle is smaller than the diameter of the circle on which the struts are located.

[0011] In the above specific embodiment with the oil baffle assembly, the height of the axial oil baffle in the axial direction is H1, wherein 8mm≤H1≤15mm; and / or the height of the outwardly expanding oil baffle in the axial direction is H2, wherein 5mm≤H2≤15mm.

[0012] In the above specific embodiment with the oil baffle assembly, the inner diameter of the flange is D1, and the inner diameter of the axial oil baffle is D3, wherein D3-D1≥5mm.

[0013] In the above specific embodiment with the oil baffle assembly, the secondary oil baffle is provided with a baffle groove extending in the axial direction.

[0014] In the above specific embodiment with the oil baffle assembly, the width of the baffle groove in the radial direction is H3, wherein 1.5mm≤H3≤3mm.

[0015] A rotor assembly comprising a rotor core and a second balance block, further comprising the oil baffle assembly of any one of the above, the second balance block and the oil baffle assembly being respectively provided on the two sides of the rotor core.

[0016] A compressor comprises a housing, a stator arranged in the housing, a rotor assembly rotating in the stator, and a crankshaft arranged in the center of the rotor assembly, wherein the rotor assembly is the rotor assembly described above.

[0017] In the case of adopting the technical scheme, the rotation of the primary oil baffle, the flange, the first balance block and the plurality of struts forms a layer of rotating flow field, and the frozen oil dissolved in the gas is separated for the first time, the rotation of the secondary oil baffle forms a second layer of rotating flow field, and the frozen oil not separated is separated again, and the two times of separation increases the probability of separation of the frozen oil. In addition, the primary oil baffle increases the covering space of the layer of rotating flow field in the radial direction, and the secondary oil baffle increases the covering space of the second layer of rotating flow field in the axial direction on the basis of the primary oil baffle 1. Since the double-layer rotating flow field has a larger space in the radial direction and the axial direction, the centrifugal force generated is also larger, so that the frozen oil in the gas can be separated more effectively, and the double-layer rotating flow field contacts more gas, so that more gas can be separated for the frozen oil, and the oil-gas separation effect of the oil-gas separation baffle is improved. BRIEF DESCRIPTION OF DRAWINGS

[0018] The preferred embodiments of the present application will be described below with reference to the accompanying drawings, in which:

[0019] Fig. 1 is a structural schematic view of the compressor in the present application, wherein the flow direction of the frozen oil is shown;

[0020] Fig. 2 is a structural schematic view of the rotor assembly in the present application;

[0021] Fig. 3 is a structural schematic view of the oil baffle assembly in the present application;

[0022] Fig. 4 is a bottom view of the oil baffle assembly in the present application;

[0023] Fig. 5 is a sectional view at A-A in Fig. 4.

[0024] In the drawings: 1, primary oil baffle, 11, flange, 12, first balance block, 13, strut, 14, mounting hole, 2, secondary oil baffle, 21, axial oil baffle, 22, outwardly expanded oil baffle, 23, baffle groove, 3, rotor core, 4, second balance block, 5, housing, 6, stator, 7, crankshaft, 8, connecting piece, 91, exhaust pipe, 92, compressor oil pool, 93, distributor, 94, pump body assembly. DETAILED DESCRIPTION

[0025] The preferred embodiments of the present application will be described below with reference to the accompanying drawings, in which:

[0026] It should be noted that in the description of the present application, the terms "upper", "lower", "left", "right", "inner", "outer" and the like indicating the direction or positional relationship are based on the direction or positional relationship shown in the drawings, which is merely for the convenience of description, and does not indicate or imply that the related devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application. In addition, the ordinal numbers "first", "second" and the like are only for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0027] In addition, it should also be noted that in the description of the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connection" should be understood broadly, for example, it can be fixed connection, or detachable connection or integral connection; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through intermediate medium. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0028] Furthermore, in order to more clearly show the core technical scheme of the present application, the description of the well-known structure of the compressor is omitted in the following description, but this omission only means that the compressor can not have these structures.

[0029] As shown in Figure 1, the present application proposes a kind of compressor, including shell 5, stator 6 being arranged in shell 5, rotating rotor assembly in stator 6 and crankshaft 7 being arranged in the center of rotor assembly, it also includes exhaust pipe 91 being arranged on shell 5, compressor oil pool 92 being arranged at the bottom of shell 5, distributor 93 being arranged at one side of shell 5 and pump body assembly 94 being arranged below crankshaft 7.

[0030] As shown in Figures 1-2, the present application proposes a kind of rotor assembly, including rotor core 3 and second balance block 4, it also includes oil baffle assembly, second balance block 4 and oil baffle assembly are respectively arranged at both sides of rotor core 3.

[0031] As shown in Figures 3-5, the present application proposes an oil baffle assembly, including: first oil baffle 1, first oil baffle 1 is provided with flange 11, first balance block 12 and a plurality of struts 13 on the side towards rotor core 3, flange 11 is used to accommodate the end of crankshaft 7, first balance block 12 and strut 13 are provided with mounting hole 14, connecting piece 8 connects first oil baffle 1 with rotor core 3 through mounting hole 14;Second oil baffle 2, second oil baffle 2 is arranged on the side of first oil baffle 1 away from rotor core 3.

[0032] In the embodiment, in order to solve the problem of poor oil-gas separation effect of the existing compressor oil-gas separation baffle, two-stage oil baffle plates are arranged to form two layers of rotating flow fields. The rotation of the first-stage oil baffle plate 1, the flange 11, the first balance block 12 and the plurality of struts 13 forms a layer of rotating flow field, and the refrigeration oil dissolved in the gas is separated for the first time. The rotation of the second-stage oil baffle plate 2 forms a second layer of rotating flow field, and the refrigeration oil that is not separated is separated again. The two-time separation increases the probability of separation of the refrigeration oil. In addition, the first-stage oil baffle plate 1 increases the coverage space of the layer of rotating flow field in the radial direction. The second-stage oil baffle plate 2 increases the coverage space of the second layer of rotating flow field in the axial direction on the basis of the first-stage oil baffle plate 1. Since the double-layer rotating flow field has a larger space in the radial direction and the axial direction, the centrifugal force generated is also larger, so that the refrigeration oil in the gas can be more effectively separated. In addition, the double-layer rotating flow field contacts more gas, and can separate more refrigeration oil from the gas. The separated refrigeration oil flows along the inner wall of the shell 5 into the compressor oil pool 92.

[0033] The oil baffle plate assembly in the embodiment increases the coverage space of the rotating flow field in the radial direction and the axial direction, can separate a large proportion of the refrigeration oil dissolved in the gas, and flow back to the compressor oil pool 92, improves the oil-gas separation effect of the oil-gas separation baffle, and minimizes the amount of oil flowing into the condenser, the evaporator and the system pipeline.

[0034] In order to enable the first-stage oil baffle plate 1 to be flatly installed on the surface of the rotor core 3, the lower edge of the flange 11, the lower edge of the first balance block 12 and the lower edge of the strut 13 are flush.

[0035] The outer diameter of the rotor core 3 is d, and the outer diameter of the first-stage oil baffle plate 1 is D2. In order to avoid interference between the first-stage oil baffle plate 1 and other components of the compressor, D2 is generally set to be slightly smaller than d, for example, 0 < d-D2 < 2 mm.

[0036] It should be noted that although the cross section of the flange 11 shown in FIG. 3 is circular, this is not a limitation of the present application. Those skilled in the art can use other shapes of flanges, such as a cross section of a quincunx-shaped flange, without departing from the basic principles of the present application. These do not deviate from the principles of the present application, and therefore fall within the scope of the present application.

[0037] Further, in order to increase the coverage space of the second layer of rotating flow field generated by the rotation of the second-stage oil baffle plate 2, the second-stage oil baffle plate 2 comprises: an axial oil baffle plate 21 extending in the axial direction; and an outwardly extending oil baffle plate 22 connected with the first-stage oil baffle plate 1 and the outwardly extending oil baffle plate 22 at both ends of the axial oil baffle plate 21, and extending outwardly in the radial direction at an acute angle of θ with the axial oil baffle plate 21. The cross section of the axial oil baffle plate 21 is a circular ring, and the cross section of the outwardly extending oil baffle plate 22 is also a circular ring.

[0038] In the embodiment, the axial baffle plate 21 further increases the height of the baffle plate assembly in the axial direction, so that the coverage space of the two-layer rotating flow field in the axial direction is larger; the outwardly expanding baffle plate 22 extends outwardly in the radial direction in a manner of forming an acute angle θ with the axial baffle plate 21, which can increase the coverage space of the two-layer rotating flow field in the axial direction and the coverage space of the two-layer rotating flow field in the radial direction. The larger the coverage space of the two-layer rotating flow field is, the greater the centrifugal force generated is, and the better the oil-gas separation effect is. The rotating flow field generated by the outwardly expanding baffle plate 22 is a circular truncated cone, which is relatively stable, and the effect of the rotating flow field on gas separation is relatively uniform.

[0039] Further, as shown in FIG. 5, the outwardly expanding baffle plate 22 forms an acute angle θ with the axial baffle plate 21, wherein 10°≤θ≤30°. In the embodiment, although increasing the height of the baffle plate assembly can increase the coverage space of the rotating flow field, thereby increasing the separation ratio of the refrigeration oil, the height of the baffle plate assembly that is too high may interfere with other components in the compressor, affect the normal operation of the compressor, and also may cause the cooling liquid to be unable to flow into the compressor oil pool 92 along the inner wall of the shell 5 in time. Therefore, the height and the radial width of the two-stage baffle plate 2 need to be limited. If the θ angle is too small, the radial width of the two-stage baffle plate 2 will be small, which will result in a small coverage space of the rotating flow field in the radial direction, and the oil-gas separation effect is not ideal. If the θ angle is too large, the radial width of the two-stage baffle plate 2 will be too large, the radial coverage range of the rotating flow field generated will also be too large, which will result in that the pressure below the separated refrigeration oil is larger than the pressure above the separated refrigeration oil, thereby causing the separated refrigeration oil to be unable to flow into the compressor oil pool 92 along the inner wall of the shell 5 in time. When 10°≤θ≤30°, the height and the radial width of the two-stage baffle plate 2 are appropriate.

[0040] As shown in FIG. 3, the first-stage baffle plate 1 has two support columns 13, each of which is provided with one mounting hole 14, the first balance block 12 is provided with two mounting holes 14, the mounting holes 14 are rivet holes, and the connecting pieces 8 are rivets; the rotor core 3 is provided with connecting holes corresponding to the four mounting holes 14, and the second balance block 4 is provided with mounting holes corresponding to the mounting holes 14 on the two support columns 13. During installation, the two connecting pieces 8 pass through the mounting holes 14 on the support columns 13, pass through the connecting holes and the mounting holes 14 on the second balance block 4, and connect the support columns 13, the rotor core 3 and the second balance block 4 together; the two connecting pieces 8 pass through the two mounting holes 14 on the first balance block 12 and the corresponding connecting holes on the rotor core 3, and connect the first balance block 12 and the rotor core 3 together.

[0041] As shown in Fig. 5, in order to avoid the radial dimension of the outer expanded oil baffle 22 being too large to affect the installation of the connecting piece 8, the outer diameter of the outer expanded oil baffle 22 is smaller than the diameter of the circle where the strut 13 is located. The outer diameter of the outer expanded oil baffle 22 at the highest position in the axial direction is the largest, the largest outer diameter of the outer expanded oil baffle 22 is D5, and the diameter of the circle where the strut 13 is located is D4, wherein D4-D5>4mm.

[0042] It should be noted that although four mounting holes are shown in Fig. 3, this is not a limitation of the present application, and those skilled in the art can use other numbers of mounting holes without departing from the essential principles of the present application, as long as the primary oil baffle 1 can be connected with the rotor core 3 and the first balance block 12, and the balance of the rotor is not affected. For example, two mounting holes 14 are provided on the first balance block 12, one strut 13 is provided on the primary oil baffle 1, or one mounting hole 14 is provided on the first balance block 12, two struts 13 are provided on the primary oil baffle 1, and the like, which do not deviate from the principles of the present application and thus fall within the scope of protection of the present application.

[0043] Further, the height of the axial oil baffle 21 in the axial direction is H1, wherein 8mm≤H1≤15mm; and the height of the outer expanded oil baffle 22 in the axial direction is H2, wherein 5mm≤H2≤15mm.

[0044] Further, the inner diameter of the flange 11 is D1, and the inner diameter of the axial oil baffle 21 is D3. Since the flange 11 is provided with a through hole for accommodating the crankshaft 7, the inner diameter D3 of the axial oil baffle 21 is larger than the inner diameter D1 of the flange 11, and can be D3-D1≥5mm.

[0045] Further, as shown in Fig. 3, the secondary oil baffle 2 is provided with a baffle groove 23 extending in the axial direction. During shutdown or dynamic rotation of the compressor, a small amount of refrigeration oil falls into the secondary oil baffle 2. If the circumference of the secondary oil baffle 2 is not open, the refrigeration oil in the secondary oil baffle 2 will increase, and this part of the refrigeration oil cannot flow into the compressor oil pool 92. In order to enable this part of the refrigeration oil to flow out of the secondary oil baffle 2, the baffle groove 23 extending in the axial direction is provided on the secondary oil baffle 2. During shutdown or dynamic rotation of the compressor, this part of the refrigeration oil is thrown out of the secondary oil baffle 2 by the action of the rotating centrifugal force, and flows along the inner wall of the housing 5 to the compressor oil pool 92.

[0046] In order to enable the small amount of refrigeration oil in the secondary oil baffle 2 to be thrown out, the baffle groove 23 extends downward in the axial direction to be flush with the primary oil baffle 1.

[0047] Further, the width of the baffle groove 23 in the radial direction is H3, wherein 1.5mm≤H3≤3mm.

[0048] The baffle groove 23 has the function of throwing out a small amount of frozen oil in the second baffle 2, so it does not need to be too wide, and too wide will weaken the second layer of rotating flow field, resulting in reduced oil-gas separation effect, so the range of H is: 1.5mm≤H1≤3mm, which can throw out a small amount of frozen oil in the second baffle 2, and will not weaken the second layer of rotating flow field.

[0049] In addition, in another embodiment, the second baffle 2 can also only include the outer expansion baffle 22, which is arranged on the first baffle 2, and the outer expansion baffle 22 forms a certain angle with the axis.

[0050] Those skilled in the art can understand that although some embodiments described herein include certain features included in other embodiments rather than other features, the combination of features of different embodiments means that it is within the scope of the present application and forms different embodiments. For example, in the claims of the present application, any one of the claimed embodiments can be used in any combination.

[0051] So far, the technical solutions of the present application have been described in combination with the preferred embodiments shown in the drawings, but those skilled in the art can easily understand that the protection scope of the present application is obviously not limited to these specific embodiments. Those skilled in the art can make equivalent changes or replacements to related technical features without departing from the principles of the present application, and the technical solutions after the changes or replacements will fall within the protection scope of the present application.

Claims

1. A windscreen wiper assembly characterized by, The first oil baffle (1) is provided with a flange (11), a first balance block (12) and a plurality of support columns (13) on the side facing the rotor core (3), the flange (11) is used to accommodate the end of the crankshaft (7), the first balance block (12) and the support column (13) are provided with mounting holes (14), and the connecting piece (8) connects the first oil baffle (1) and the rotor core (3) through the mounting holes (14). The second oil baffle (2) is arranged on the side of the first oil baffle (1) away from the rotor core (3). The second oil baffle (2) comprises:

2. The windscreen deflector assembly of claim 1, wherein, An axial oil baffle (21) extending in the axial direction; An outwardly expanded oil baffle (22) connected with the first oil baffle (1) and the axial oil baffle (21) respectively, and extending radially outwardly at an acute angle of θ with the axial oil baffle (21).

3. The oil baffle assembly according to claim 2, wherein The outwardly expanded oil baffle (22) forms an acute angle of θ with the axial oil baffle (21), and 10°≤θ≤30°.

4. The oil baffle assembly according to claim 2, wherein The outer diameter of the outwardly expanded oil baffle (22) is smaller than the diameter of the circle where the support column (13) is located.

5. The oil baffle assembly according to claim 2, wherein The height of the axial oil baffle (21) in the axial direction is H1, and 8mm≤H1≤15mm; and / or The height of the outwardly expanded oil baffle (22) in the axial direction is H2, and 5mm≤H2≤15mm.

6. The oil baffle assembly according to claim 2, wherein The inner diameter of the flange (11) is D1, and the inner diameter of the axial oil baffle (21) is D3, and D3-D1≥5mm.

7. The oil baffle assembly according to claim 1, wherein The second oil baffle (2) is provided with a baffle groove (23) extending in the axial direction.

8. The oil baffle assembly according to claim 7, wherein The radial width of the baffle groove (23) is H3, and 1.5mm≤H3≤3mm. The rotor assembly comprises a rotor core (3) and a second balance block (4), and further comprises the oil baffle assembly according to any one of claims 1-8, and the second balance block (4) and the oil baffle assembly are arranged on the two sides of the rotor core (3) respectively.

9. A rotor assembly characterized by, The rotor assembly is the rotor assembly described in claim 9.

10. A compressor comprising a housing (5), a stator (6) arranged in said housing (5), a rotor assembly rotating in said stator (6) and a crankshaft (7) arranged in the center of said rotor assembly, characterized in that, ​

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