CN215256800U - Rotor structure, compressor and air conditioner - Google Patents
Rotor structure, compressor and air conditioner Download PDFInfo
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- CN215256800U CN215256800U CN202120436247.3U CN202120436247U CN215256800U CN 215256800 U CN215256800 U CN 215256800U CN 202120436247 U CN202120436247 U CN 202120436247U CN 215256800 U CN215256800 U CN 215256800U
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Abstract
The utility model provides a rotor structure, compressor and air conditioner relates to compression equipment technical field. The rotor structure includes: a first rotor assembly including first and second rotors coaxially disposed and having opposite thread turns, the first and second rotors being engaged at end faces thereof adjacent to each other; the second rotor assembly comprises a third rotor meshed with the first rotor and a fourth rotor meshed with the second rotor, the third rotor and the fourth rotor are coaxially arranged, and a spacer is arranged between the third rotor and the fourth rotor to separate the end faces, close to each other, of the third rotor and the fourth rotor; wherein 1/2 of the width of the spacer in the axial direction is greater than the sum of the maximum assembly offset of the first rotor in the first direction and the maximum assembly offset of the fourth rotor in the second direction when the rotor structure is assembled into the compressor, the first direction being opposite to the second direction. The utility model provides a dislocation meshing problem of rotor can be improved to the rotor structure, prevents that the rotor from scotching or even twisting to die.
Description
Technical Field
The utility model relates to a compression equipment technical field particularly, relates to a rotor structure, compressor and air conditioner.
Background
The screw compressor generally adopts a double-screw structure, and in the working process, radial force is generated due to different pressures on two sides of a rotor, wherein the radial force is related to the diameter, the length-diameter ratio, the internal pressure ratio and the operation working condition of the rotor; the axial force is generated due to the different pressures of the gas suction and exhaust ends, and forms the main load when the compressor operates. The direction of the axial force is always directed from the exhaust end to the suction end, the general improvement mode is to balance the stress through a bearing, but too much bearing can cause excessive operation loss and reduce the efficiency of the compressor, so that the excessive axial force is a great factor for limiting the development of the double compressors.
The four-rotor compressor is designed based on the principle of axial force balance, and axial force is balanced on the suction side through synchronous operation of two groups of male and female rotors with opposite rotation directions and symmetrical tooth profiles, and the four-rotor compressor is shown in figure 1.
However, due to the actual size error, the respective air suction end faces of the male rotor and the female rotor cannot be ensured to be in the same plane, and there is a problem of misalignment during operation, and therefore, interference occurs, that is, the male rotor at the upper left position in fig. 2 meshes with the female rotor at the lower right position or the male rotor at the upper right position in fig. 3 meshes with the female rotor at the lower left position, and the rotors are scratched or even twisted.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a rotor structure, compressor and air conditioner to improve the dislocation meshing problem of rotor, thereby prevent that the rotor from scotching or even twisting to die.
The technical problem of the utility model is solved and following technical scheme is adopted to realize.
A rotor structure comprising:
a first rotor assembly including first and second rotors coaxially disposed and having opposite thread turns, the first and second rotors being engaged at end faces thereof adjacent to each other; and
the second rotor assembly comprises a third rotor meshed with the first rotor and a fourth rotor meshed with the second rotor, the third rotor and the fourth rotor are coaxially arranged, and a spacer is arranged between the third rotor and the fourth rotor to separate the end faces, close to each other, of the third rotor and the fourth rotor;
wherein 1/2 of the width of the spacer in the axial direction is greater than the sum of the maximum assembly offset of the first rotor in the first direction and the maximum assembly offset of the fourth rotor in the second direction when the rotor structure is assembled into the compressor, the first direction being opposite to the second direction.
In a preferred embodiment of the present invention, the spacer is integrally formed with the second rotor assembly.
In a preferred embodiment of the present invention, the spacer is integrally formed with the third rotor and/or the fourth rotor.
In a preferred embodiment of the present invention, the spacer is integrally formed with the rotating shaft of the second rotor assembly.
In a preferred embodiment of the present invention, the first rotor assembly is a male rotor assembly and the second rotor assembly is a female rotor assembly; or the first rotor assembly is a female rotor assembly and the second rotor assembly is a male rotor assembly.
A rotor structure comprising:
a first rotor assembly including a first shaft, a first portion and a second portion, the first portion and the second portion being rotatable along a first axis of the first shaft, the first portion having a thread of a direction opposite to a thread of the second portion;
a second rotor assembly including a second shaft, a third portion engaged with the first portion, and a fourth portion engaged with the second portion, the third and fourth portions being rotatable independently of each other along a second axis of the second shaft,
and the spacing part is integrally formed with the second rotor assembly and is used for preventing the first part from being meshed with the fourth part and preventing the second part from being meshed with the third part.
In a preferred embodiment of the invention, the spacer is integrally formed with the first part and/or the second part.
In a preferred embodiment of the present invention, the spacer and the second shaft are integrally formed.
A compressor, comprising:
a housing;
a first rotor assembly rotatably disposed within the housing and including first and second coaxially disposed rotors of opposite hand, the first and second rotors being engaged at mutually adjacent end faces; and
the second rotor assembly is rotatably arranged in the shell and comprises a third rotor and a fourth rotor which are coaxially arranged, the third rotor and the fourth rotor are respectively meshed with the first rotor and the second rotor, and a spacer is arranged between the third rotor and the fourth rotor so as to separate the end faces, close to each other, of the third rotor and the fourth rotor;
wherein 1/2 of the width of the spacer in the axial direction is greater than the sum of the maximum fitting offset of the first rotor in the first direction and the maximum fitting offset of the fourth rotor in the second direction, the first direction being opposite to the second direction.
In a preferred embodiment of the present invention, the spacer is integrally formed with the second rotor assembly.
In the preferred embodiment of the present invention, the maximum assembly offset of the first rotor is an absolute value of a lower deviation of the gap width between the second rotor and the housing, and the maximum assembly offset of the fourth rotor is an absolute value of a lower deviation of the gap width between the third rotor and the housing.
In a preferred embodiment of the present invention, the spacer is integrally formed with the rotating shaft of the second rotor assembly.
In the preferred embodiment of the present invention, the maximum assembly offset of the first rotor is an absolute value of a lower deviation of a gap width between the second rotor and the housing, and the maximum assembly offset of the fourth rotor is equal to zero.
An air conditioner comprises the rotor structure or the compressor.
The utility model provides a technical scheme's beneficial effect is: through setting up the spacer to the rotor structure to separate third rotor and fourth rotor, inject the width of spacer in the axial again, avoid the dislocation meshing between the rotor, prevent that the rotor from scotching even and dying, thereby guarantee the normal operating of compressor. Additionally, the utility model discloses a compressor simple structure, the cost is lower, and the running part is few, and comprehensive properties and reliability are high.
Drawings
For a clearer explanation of the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
FIG. 1 is a schematic illustration of a prior art four rotor compressor with axial force balancing on the suction side;
FIG. 2 is a schematic illustration of an interference situation in the meshing of the male and female rotors of a prior art four rotor compressor;
FIG. 3 is a schematic illustration of another interference situation in the meshing of the male and female rotors of a prior art four rotor compressor;
fig. 4 is a schematic diagram of a theoretical assembly state provided by the first embodiment of the present invention;
fig. 5 is a schematic diagram of a first maximum assembly deviation state from a theoretical assembly state according to a first embodiment of the present invention;
fig. 6 is a schematic diagram of a second maximum assembly deviation state from a theoretical assembly state provided by the first embodiment of the present invention;
fig. 7 is a schematic diagram of a theoretical assembly state provided by a second embodiment of the present invention;
fig. 8 is a schematic view of a first maximum assembly deviation state from a theoretical assembly state provided by a second embodiment of the present invention;
fig. 9 is a schematic diagram of a second maximum assembly deviation state from a theoretical assembly state according to the second embodiment of the present invention.
Wherein the reference numerals are summarized as follows:
a housing 10;
a first rotor assembly 11; a first rotor 111; a second rotor 112; a first gas-suction end face 113;
the second rotor assembly 12; a third rotor 121; a fourth rotor 122; a second left suction end face 123; a second right suction end face 124;
a spacer 13;
a first rotating shaft 14; a second shaft 15.
Detailed Description
The technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is to be understood that the embodiments described are only some embodiments of the invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses, as the embodiments are based on the disclosure, and all other embodiments obtained by those skilled in the art without undue experimentation may be within the scope of the disclosure.
Reference herein to "an embodiment" or "an implementation" means that a particular feature, structure, or characteristic described in connection with the embodiment or implementation can be included in at least one embodiment of the invention. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein can be combined with other embodiments.
The utility model discloses a first embodiment provides a rotor structure, and this rotor structure can assemble to the compressor in, and this embodiment carries out the detailed description based on the compressor, and this compressor includes:
a housing 10;
a first rotor assembly 11 rotatably disposed in the housing 10 and including a first rotor 111 and a second rotor 112 having opposite screw threads coaxially disposed, wherein end faces of the first rotor 111 and the second rotor 112 adjacent to each other are engaged to form a first air suction end face 113; and
a second rotor assembly 12 rotatably disposed in the housing 10 and including a third rotor 121 and a fourth rotor 122 coaxially disposed, where the third rotor 121 and the fourth rotor 122 are respectively engaged with the first rotor 111 and the second rotor 112, and a spacer 13 is disposed between the third rotor 121 and the fourth rotor 122 to separate an end surface of the third rotor 121 and the fourth rotor 122, which are close to each other, into two second air suction end surfaces (a second left air suction end surface 123 and a second right air suction end surface 124);
wherein 1/2 of the width of the spacer 13 in the axial direction is larger than the sum of the maximum fitting offset amount of the first rotor 111 in the first direction and the maximum fitting offset amount of the fourth rotor 122 in the second direction, the first direction being opposite to the second direction.
In the present embodiment, the assembly deviation refers to a deviation from a theoretical assembly start, and the maximum assembly deviation refers to a maximum deviation from the theoretical assembly start, wherein the theoretical assembly refers to an assembly when the central axis surface of the spacer 13 coincides with the first air suction end surface 113, and when the assembly is actually performed, there may be a positional deviation, which causes the first rotor 111 to be deviated in a first direction and the fourth rotor 122 to be deviated in a second direction, which may be opposite or opposite to each other, and when the first direction is opposite to the second direction, the first rotor 111 and the fourth rotor 122 approach each other, and when the first direction is opposite to the second direction, the first rotor 111 and the fourth rotor 122 move away from each other. With respect to the theoretical assembly, when the displacement of the first rotor 111 and the fourth rotor 122 toward each other occurs, since the first rotor 111 and the second rotor 112 are synchronously displaced, the maximum assembly displacement amount of the first rotor 111 is the absolute value of the lower deviation of the gap width between the second rotor 112 and the housing 10, and since the fourth rotor 122 and the third rotor 121 are synchronously displaced, the maximum assembly displacement amount of the fourth rotor 122 is the absolute value of the lower deviation of the gap width between the third rotor 121 and the housing 10.
For convenience of explanation, the present embodiment provides a schematic diagram of a theoretical assembly state of the compressor, see fig. 4, in which the first rotor 111 is in mesh with the third rotor 121, and the second rotor 112 is in mesh with the fourth rotor 122. The width of the spacer 13 in the axial direction is T, Tm1, Tm2, Tf1 and Tf2 are the gap widths between the first rotor 111, the second rotor 112, the third rotor 121 and the fourth rotor 122 and the housing 10, respectively, in this theoretical assembly state, Tm1 is equal to Tf1 and Tm2 is equal to Tf2, that is, the first rotor assembly 11 composed of the first rotor 111 and the second rotor 112 and the second rotor assembly 12 composed of the third rotor 121 and the fourth rotor 122 are at the same theoretical axial position. At this time, the distance between the first air suction end surface 113 and the second left air suction end surface 123 and the distance between the first air suction end surface 113 and the second right air suction end surface 124 are both t0, and in this theoretical assembly state, t0 is greater than 0, but if t0 is not greater than 0, the first air suction end surface 113 interferes with the second left air suction end surface 123 or the second right air suction end surface 124, that is, the second rotor 112 meshes with the third rotor 121 or the first rotor 111 meshes with the fourth rotor 122, and a fault occurs immediately.
In practical applications, Tm1, Tf1, Tm2, and Tf2 have respective ranges, that is, a tolerance zone with a certain width, which also causes the distance between the first air suction end surface 113 and the second left air suction end surface 123 and the distance between the first air suction end surface 113 and the second right air suction end surface 124 to change.
Referring to fig. 5, fig. 5 shows a case where the first rotor 111 and the fourth rotor 122 are close to each other. When Tm2 and Tf1 both reach the limit values corresponding to the respective lower deviations, i.e., the minimum values Tm2min and Tf 1min, the distance between the first air suction end surface 113 and the second right air suction end surface 124 is the minimum, i.e., t 1. Under the condition that the dimensional accuracy of each part is qualified, to avoid interference between the first air suction end surface 113 and the second right air suction end surface 124, namely the first rotor 111 is meshed with the fourth rotor 122, T1 is ensured to be greater than 0, and as can be seen from fig. 4, T/2 > (Tm2-Tm2min) + (Tf1-Tf 1min) and (Tm2-Tm2min) are ensured to be the absolute values of (Tm2min-Tm2), namely the absolute values of the lower deviation of the gap width between the second rotor 112 and the housing 10; (Tf1-Tf 1min), i.e. the absolute value of (Tf1 min-Tf1), i.e. the absolute value of the lower deviation of the gap width between the third rotor 121 and the housing 10, so T/2 > (Tm2-Tm2min) + (Tf1-Tf 1min), i.e. the width of the spacer 13 in the axial direction 1/2 is greater than the sum of the maximum assembly deviation of the first rotor 111 in the first direction and the maximum assembly deviation of the fourth rotor 122 in the second direction, the first direction being opposite to the second direction.
Referring to fig. 6, fig. 6 shows the case where the first rotor 111 and the fourth rotor 122 are far away from each other, but when the two rotors of the first rotor assembly 11 are named as "first" and "second" in sequence from right to left and the two rotors of the second rotor assembly 12 are named as "third" and "fourth" in sequence from right to left, the case where the first rotor 111 and the fourth rotor 122 are far away from each other in fig. 6 becomes the case where the two rotors are close to each other after being named from right to left. In fig. 6, when Tm1 and Tf2 both reach the respective limit values corresponding to the lower deviation, i.e., the minimum values Tm1min and Tf 2min, the distance between the first air suction end face 113 and the second left air suction end face 123 is the minimum, i.e., t 2. Under the condition that the dimensional accuracy of each part is qualified, to avoid interference between the first air suction end surface 113 and the second left air suction end surface 123, namely the second rotor 112 is meshed with the third rotor 121, T2 > 0 is ensured, and as can be seen from fig. 4, T/2 > (Tm1-Tm1min) + (Tf2-Tf 2min) and (Tm1-Tm1min), namely, absolute values of (Tm1min-Tm1), namely, absolute values of lower deviation of the gap width between the first rotor 111 and the housing 10 are ensured; (Tf2-Tf 2min), i.e., the absolute value of (Tf2 min-Tf2), i.e., the absolute value of the lower deviation of the gap width between the fourth rotor 122 and the housing 10, so T/2 > (Tm1-Tm1min) + (Tf2-Tf 2min), i.e., the maximum assembly deviation amount when the width 1/2 of the spacer 13 in the axial direction is greater than the sum of the maximum assembly deviation amounts when the second rotor 112 and the third rotor 121 approach each other.
In practical applications, the selection of the T value may be determined comprehensively by combining the tolerance range, thermal expansion and other influences of the spacer 13 itself.
In the present embodiment, the first rotor assembly 11 is a male rotor assembly, and both the first rotor 111 and the second rotor 112 are male rotors; the second rotor assembly 12 corresponds to a female rotor assembly, and the third rotor 121 and the fourth rotor 122 are both female rotors. In other embodiments, if the first rotor assembly 11 is a female rotor assembly, the first rotor 111 and the second rotor 112 are female rotors, the second rotor assembly 12 is a male rotor assembly, and the third rotor 121 and the fourth rotor 122 are male rotors.
In this embodiment, the spacer 13 and the second rotor assembly 12 are integrally formed, but in other embodiments, the spacer 13 and the second rotor assembly 12 may be separate components, and are configured by an assembly completion structure. Specifically, in the present embodiment, the spacer 13 is integrally formed on the end surface of the third rotor 121 close to the fourth rotor 122, and in other embodiments, the spacer 13 may also be disposed on the end surface of the fourth rotor 122 close to the third rotor 121. Even the spacer 13 may be integrally formed on the third rotor 121 and the fourth rotor 122, that is, the spacer 13 includes a first spacing portion and a second spacing portion, the first spacing portion and the second spacing portion are respectively disposed on the third rotor 121 and the fourth rotor 122 — for example, the first spacing portion is integrally formed on an end surface of the third rotor 121 close to the fourth rotor 122, and the second spacing portion is integrally formed on an end surface of the fourth rotor 122 close to the third rotor 121, as long as the sum of the widths of the first spacing portion and the second spacing portion in the axial direction is equal to the width of the spacer 13 in the axial direction. In other embodiments, the spacer 13 may be disposed in a rotating shaft where the second rotor assembly 12 is located, and the outer diameter of the spacer 13 is larger than the inner diameter of a hole where the rotating shaft penetrates through the second rotor assembly 12, in this structure, the maximum assembly offset amount of the first rotor 111 is still the absolute value of the lower deviation of the gap width between the second rotor 112 and the housing 10, and the maximum assembly offset amount of the fourth rotor 122 is the absolute value of the lower deviation of the gap width between the third rotor 121 and the housing 10.
In the second embodiment of the present invention, the assembly deviation also refers to a deviation from the theoretical assembly start, and the maximum assembly deviation refers to a maximum deviation from the theoretical assembly start of the actual assembly, wherein the theoretical assembly refers to the assembly when the central axial plane of the spacer 13 coincides with the first air suction end surface 113. In actual assembly, there may also be a position shift, which causes the first rotor 111 to shift in a first direction and the fourth rotor 122 to shift in a second direction, where the first direction and the second direction may be opposite or opposite, when the first direction and the second direction are opposite, the first rotor 111 and the fourth rotor 122 are close to each other, and when the first direction and the second direction are opposite, the first rotor 111 and the fourth rotor 122 are far away from each other.
For convenience of illustration, the present embodiment provides a schematic diagram of a theoretical assembly state of the compressor, and refer to fig. 7, wherein the first rotor 111 is in mesh with the third rotor 121, the second rotor 112 is in mesh with the fourth rotor 122, the rotation axis of the first rotor assembly 11 is the first rotation axis 14, the rotation axis of the second rotor assembly 12 is the second rotation axis 15, and the third rotor 121 and the fourth rotor 122 rotate around the second rotation axis 15 respectively. In this embodiment, the width of the spacer 13 in the axial direction is T, Tm1, Tm2, Tf1 and Tf2 are the widths of the gaps between the first rotor 111, the second rotor 112, the third rotor 121 and the fourth rotor 122 and the housing 10, respectively, in this theoretical assembly state, Tm1 is equal to Tf1, and Tm2 is equal to Tf2, that is, the first rotor assembly 11 composed of the first rotor 111 and the second rotor 112 and the second rotor assembly 12 composed of the third rotor 121 and the fourth rotor 122 are located at the same theoretical axial position. At this time, the distance between the first air suction end surface 113 and the second left air suction end surface 123 and the distance between the first air suction end surface 113 and the second right air suction end surface 124 are both t0, and in this theoretical assembly state, t0 is greater than 0, but if t0 is not greater than 0, the first air suction end surface 113 will interfere with the second left air suction end surface 123 or the first air suction end surface 113 will interfere with the second right air suction end surface 124, that is, the second rotor 112 is meshed with the third rotor 121 or the first rotor 111 is meshed with the fourth rotor 122, and a fault occurs immediately.
In practical applications, Tm1 and Tm2 have respective ranges, that is, a tolerance band with a certain width, which also causes the distance between the first air suction end face 113 and the second left air suction end face 123 and the distance between the first air suction end face 113 and the second right air suction end face 124 to change.
Since the assembly offset is an offset from the theoretical assembly start, and in the present embodiment, the spacer 13 is integrally formed with the rotating shaft where the second rotor assembly 12 is located, and the spacer 13 plays a role of blocking between the third rotor 121 and the fourth rotor 122, when the first rotor 111 forms the assembly offset in the first direction and the fourth rotor 122 forms the assembly offset in the opposite second direction, that is, when the first rotor 111 and the fourth rotor 122 approach each other, the maximum assembly offset of the fourth rotor 122 from the theoretical assembly start is zero. Therefore, 1/2, which is the width of the spacer 13 in the axial direction, is larger than the maximum fitting offset amount when the first rotor 111 is close to the fourth rotor 122. Whereas, with respect to the theoretical assembly, when the offset in which the first rotor 111 and the fourth rotor 122 approach each other occurs, since the first rotor 111 and the second rotor 112 are synchronously offset, the maximum assembly offset amount of the first rotor 111 is the absolute value of the lower deviation of the gap width between the second rotor 112 and the housing 10. That is, 1/2 of the width of the spacer 13 in the axial direction is larger than the absolute value of the lower deviation of the gap width between the second rotor 112 and the housing 10.
Referring to fig. 8, fig. 8 shows a case where the first rotor 111 approaches the fourth rotor 122. When Tm2 reaches a limit value corresponding to the lower deviation, i.e. the minimum value Tm2min, the distance between the first air suction end surface 113 and the second right air suction end surface 124 is the minimum value, i.e. t 1. Under the condition that the dimensional accuracy of each component is qualified, to avoid interference between the first air suction end surface 113 and the second right air suction end surface 124, that is, to mesh the first rotor 111 and the fourth rotor 122, T1 > 0 is ensured, and as can be seen from fig. 7, T/2 > (Tm2-Tm2min) is ensured, and (Tm2-Tm2min) is the absolute value of (Tm2min-Tm2), that is, the absolute value of the lower deviation of the gap width between the second rotor 112 and the housing 10, so T/2 > (Tm2-Tm2min) is the maximum assembly deviation of the width 1/2 of the spacer 13 in the axial direction, which is greater than the maximum assembly deviation of the first rotor 111 when the fourth rotor 122 approaches.
Referring to fig. 9, fig. 9 shows the case where the first rotor 111 and the fourth rotor 122 are far away from each other, but when the two rotors of the first rotor assembly 11 are named as "first" and "second" in sequence from right to left and the two rotors of the second rotor assembly 12 are named as "third" and "fourth" from right to left, the case where the first rotor 111 and the fourth rotor 122 are far away from each other in fig. 9 becomes the case where the two rotors are close to each other after being named from right to left. In fig. 9, when Tm1 reaches a limit value corresponding to the lower deviation, i.e., the minimum value Tm1min, the distance between the first air suction end face 113 and the second left air suction end face 123 is the minimum, i.e., t 2. Under the condition that the dimensional accuracy of each component is qualified, t2 is ensured to be greater than 0 to avoid the interference between the first air suction end surface 113 and the second left air suction end surface 123, namely, the engagement between the second rotor 112 and the third rotor 121. Referring to fig. 7, it can be seen that T/2 > (Tm1-Tm1min) is required to be ensured, and (Tm1-Tm1min) is an absolute value of (Tm1min-Tm1), that is, an absolute value of a lower deviation of a gap width between the first rotor 111 and the housing 10, so that T/2 > (Tm1-Tm1min) is a maximum assembly deviation amount when the width 1/2 of the spacer 13 in the axial direction is greater than that of the second rotor 112 approaching the third rotor 121.
In practical applications, the selection of the value T may be determined in combination with the tolerance range of the spacer 13 itself, the length tolerance of each rotor, the thermal expansion, and the like.
In the present embodiment, the first rotor assembly 11 is a male rotor assembly, and both the first rotor 111 and the second rotor 112 are male rotors; the second rotor assembly 12 corresponds to a female rotor assembly, and the third rotor 121 and the fourth rotor 122 are both female rotors. In other embodiments, if the first rotor assembly 11 is a female rotor assembly, the first rotor 111 and the second rotor 112 are female rotors, the second rotor assembly 12 is a male rotor assembly, and the third rotor 121 and the fourth rotor 122 are male rotors.
In this embodiment, the spacer 13 is integrally formed with the second rotating shaft 15, and the height of the spacer 13 on the plane parallel to the first air suction end surface 113 is greater than the inner diameter of the hole through which the second rotating shaft 15 penetrates the fourth rotor 122. However, in other embodiments, the spacer 13 and the second shaft 15 may be separate components, and may be provided as an assembled structure.
In addition, in order to reduce the friction force between the spacer 13 and the rotor and further improve the mechanical performance of the compressor, a non-metal material may be selected as the material of the second rotating shaft 15 and/or the second rotor assembly 12, in this embodiment, the material of the second rotating shaft 15 is a non-metal material, specifically, a peek material, and since the spacer 13 and the second rotating shaft 15 are integrally molded, the material of the spacer 13 is also a peek material. In other embodiments, other materials may be selected for the second shaft 15 and/or the second rotor assembly 12.
The first and second rotors 111 and 112 in one or more of the above embodiments may be understood as a first portion and a second portion, the third and fourth rotors 121 and 122 may be understood as a third portion and a fourth portion, the spacer 13 may be understood as a spacer, the first rotating shaft 14 may be understood as a first shaft body, and the second rotating shaft 15 may be understood as a second shaft body.
The embodiment of the utility model provides an air conditioner is still provided, including foretell compressor.
The compressor and the air conditioner provided by the embodiment of the present invention are described in detail above, and the principle and the implementation of the present invention are explained herein by applying a specific example, and the description of the above embodiment is only used to help understanding the method and the core idea of the present invention; meanwhile, for those skilled in the art, according to the idea of the present invention, there may be some changes in the specific implementation and application scope, and to sum up, the content of the present specification should not be understood as a limitation to the present invention.
Claims (14)
1. A rotor structure, comprising:
a first rotor assembly including first and second rotors coaxially disposed and having opposite thread turns, the first and second rotors being engaged at mutually adjacent end faces; and
a second rotor assembly including a third rotor engaged with the first rotor and a fourth rotor engaged with the second rotor, the third rotor and the fourth rotor being coaxially disposed, a spacer being disposed between the third rotor and the fourth rotor to separate end surfaces of the third rotor and the fourth rotor which are close to each other;
wherein 1/2 of the width of the spacer in the axial direction is greater than the sum of the maximum assembly offset of the first rotor in a first direction and the maximum assembly offset of the fourth rotor in a second direction when the rotor structure is assembled into a compressor, the first direction being opposite to the second direction.
2. The rotor structure of claim 1, wherein the spacer is integrally formed with the second rotor assembly.
3. The rotor structure of claim 2, wherein the spacer is integrally formed with the third rotor and/or the fourth rotor.
4. The rotor structure of claim 1, wherein the spacer is integrally formed with the shaft of the second rotor assembly.
5. The rotor structure according to any one of claims 1-4, wherein the first rotor assembly is a male rotor assembly and the second rotor assembly is a female rotor assembly; or
The first rotor assembly is a female rotor assembly and the second rotor assembly is a male rotor assembly.
6. A rotor structure, comprising:
a first rotor assembly including a first shaft, a first portion and a second portion, the first portion and the second portion being rotatable along a first axis of the first shaft, the first portion having a thread count opposite a thread count of the second portion;
a second rotor assembly including a second shaft, a third portion meshed with the first portion, and a fourth portion meshed with the second portion, the third portion and the fourth portion being rotatable independently of each other along a second axis of the second shaft,
a spacer integrally formed with the second rotor assembly and configured to prevent the first portion from engaging the fourth portion and prevent the second portion from engaging the third portion.
7. The rotor structure of claim 6, wherein the spacer is integrally formed with the first portion and/or the second portion.
8. The rotor structure of claim 6, wherein the spacer is integrally formed with the second shaft body.
9. A compressor, comprising:
a housing;
a first rotor assembly rotatably disposed within the housing and including coaxially disposed first and second rotors of opposite thread direction, the first and second rotors being engaged at mutually adjacent end faces; and
the second rotor assembly is rotatably arranged in the shell and comprises a third rotor and a fourth rotor which are coaxially arranged, the third rotor and the fourth rotor are respectively meshed with the first rotor and the second rotor, and a spacer is arranged between the third rotor and the fourth rotor so as to separate the end faces, close to each other, of the third rotor and the fourth rotor;
wherein 1/2 of the width of the spacer in the axial direction is larger than the sum of the maximum fitting offset amount of the first rotor in a first direction and the maximum fitting offset amount of the fourth rotor in a second direction, the first direction being opposite to the second direction.
10. The compressor of claim 9, wherein the spacer is integrally formed with the second rotor assembly.
11. The compressor of claim 10, wherein the maximum fitting displacement amount of the first rotor is an absolute value of a lower deviation of a gap width between the second rotor and the housing, and the maximum fitting displacement amount of the fourth rotor is an absolute value of a lower deviation of a gap width between the third rotor and the housing.
12. The compressor of claim 9, wherein the spacer is integrally formed with the shaft on which the second rotor assembly is located.
13. The compressor of claim 12, wherein the maximum fitting offset amount of the first rotor is an absolute value of a lower deviation of a gap width between the second rotor and the housing, and the maximum fitting offset amount of the fourth rotor is equal to zero.
14. An air conditioner characterized by comprising a rotor structure according to any one of claims 1 to 8; or
Comprising a compressor according to any one of claims 9-13.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120436247.3U CN215256800U (en) | 2021-02-26 | 2021-02-26 | Rotor structure, compressor and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202120436247.3U CN215256800U (en) | 2021-02-26 | 2021-02-26 | Rotor structure, compressor and air conditioner |
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| CN215256800U true CN215256800U (en) | 2021-12-21 |
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| CN202120436247.3U Active CN215256800U (en) | 2021-02-26 | 2021-02-26 | Rotor structure, compressor and air conditioner |
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