巴西专利BR102012005107B1 SPIRAL COMPRESSOR

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专利摘要:
spiral compressor. a spiral compressor includes a fixed spiral having a fixed shell, and an orbiting spiral having an orbiting shell embedded with the fixed shell to define a first compression chamber between an internal surface of the fixed shell and an external surface of the orbiting shell, and to define a second compression chamber between an internal surface of the orbiting envelope and an external surface of the fixed envelope. An axis of rotation is provided with an eccentric portion at one end thereof to add the orbiting spiral. a protruding portion protrudes into an inner end of the fixed sheath, and contacts the orbiting sheath. a distance between a center of the eccentric portion and a tangent line at a point of contact between the protruding portion and the orbiting envelope at one end of the first compression chamber is less than a radius of the eccentric portion.
公开号:BR102012005107B1
申请号:R102012005107-9
申请日:2012-03-07
公开日:2021-03-23
发明作者:Sanghun SEONG；Cheolhwan Kim；Byeongchul Lee；Samchul Ha
申请人:Lg Electronics Inc.；
IPC主号:

专利说明:

[0001] This invention relates to a spiral compressor, and more particularly, to a configuration of a fixed spiral and a spiral orbit of the spiral compressor capable of obtaining a sufficient compression ratio. 2. Background of the Invention
[0002] A spiral compressor is a compressor that includes a fixed spiral having a fixed envelope and an orbiting spiral having an orbiting envelope embedded in the fixed envelope. In this configuration of the spiral compressor, as the orbiting spiral orbits in the fixed spiral, the volumes of the compression chambers, which are formed between the fixed and the orbiting envelopes, consecutively change, thus sucking and compressing a refrigerant.
[0003] The spiral compressor allows suction, compression and discharge to be performed consecutively, so it is very favorable, when compared to other types of compressors, in the aspect of vibration and noise generated during operation.
[0004] The behavior of the spiral compressor can be dependent on the shapes of the fixed and orbiting envelopes. The fixed wrapping and the orbiting wrapping may have a random shape, but typically they have a shape of an involute curve that is easy to manufacture. The involute curve refers to a curve that corresponds to a line drawn by an end of a thread when unwinding the thread wrapped around a basic circle with a predetermined radius. When such an involute curve is used, the wrap has a uniform thickness, and a rate of change of volume of the compression chamber in response to a rotated angle of the orbiting spiral is constantly maintained. Consequently, the number of wrapping turns should increase to obtain a sufficient compression ratio that could, however, cause the compressor to be increased in size corresponding to the increased number of wrapping turns.
[0005] The orbiting shell typically includes a disc, and the orbiting shell is located on one side of the disc. A cube is formed on a rear surface of the disc opposite the side on which the orbiting shell is formed. The cube is connected to a rotation axis that allows the orbiting shell to perform an orbiting movement. Such an arrangement with the orbiting shell on one side of the disc and the hub on the other side of the disc allows the orbiting shell to be formed on almost an entire surface of the disc, thereby reducing a diameter of the disc to obtain a particular compression ratio. However, a point of application of a driving force on the hub that is opposed to a refrigerant force under compression between the fixed envelope and the orbiting envelope is perpendicularly spaced from the envelopes. Because the cube is not in the same plane on the same surface as the orbiting shell, the orbiting spiral is tilted during operation, thus generating more vibration and noise. Summary of the Invention
[0006] To overcome the drawbacks of the prior art, a spiral compressor is provided that is capable of reducing an entire size of the compressor while ensuring a sufficient compression ratio. The orbiting shell of the present invention is configured so that the orbiting shell and the coupling portion for the axis of rotation are located on the same surface in the same plane. This arrangement allows the repulsive force of the refrigerant and the reaction force to be applied in the same plane to solve the problem of inclination of the orbiting spiral of the prior art.
[0007] Because the axis of rotation extends to the orbiting envelope, an end portion of the axis of rotation is located in the central portion of the orbiting envelope, which was used as a compression chamber in the prior art. Therefore, to obtain a sufficient compression ratio, the fixed and the orbiting envelopes are exclusively configured.
[0008] In an exemplary embodiment, a spiral compressor includes a fixed spiral having a fixed casing, an orbiting spiral having an orbiting casing, the orbiting casing configured to define the first and second compression chambers on an external side surface and an internal side surface together with the fixed envelope, the orbiting envelope executing an orbiting movement with respect to the fixed spiral, an axis of rotation having an eccentric portion at one end of it, the eccentric portion coupled to the orbiting envelope to overlap in a lateral direction, and a drive unit configured to drive the axis of rotation.
[0009] According to one aspect of the invention, the first compression chamber is defined between two contact points P1 and P2 generated by the contact of an internal side surface of the fixed envelope and an external side surface of the orbiting envelope, where α <360 ° by less before starting a flush operation if a greater angle of the angles defined by two lines, which connect a center O of the eccentric portion to the two contact points P1 and P2 respectively, is α.
[0010] In addition, l> 0 if a distance between normal lines at the two contact points P1 and P2 is l. Also, the normal lines drawn at the two contact points P1 and P2 can be different from each other.
[0011] A coupling portion of the axis of rotation can be formed through a central portion of the orbiting spiral. The coupling portion of the axis of rotation may have an outer circumferential surface that defines a part of the orbiting envelope and may be coupled with the eccentric portion within it. If the first compression chamber is located on the outer circumferential surface of the coupling portion of the rotation axis α <360 ° and l> 0.
[0012] The second compression chamber can contact the outer circumferential surface of the coupling portion of the axis of rotation by moving internally along an inner circumferential surface of the orbiting shell and then communicating with the first compression chamber.
[0013] The axis of rotation may include a shaft portion connected to the driving unit, a pin portion formed at one end of the shaft portion to be concentric with the shaft portion, and an eccentric bearing eccentrically inserted into the pin portion. The eccentric bearing can be rotatorily coupled to the coupling portion of the axis of rotation. The pin portion may be formed to be asymmetric.
[0014] According to another aspect of the invention, if an internal contact point of the first compression chamber under discharge initiation is P3 and an internal contact point of the first compression chamber 150 ° before beginning the discharge operation is P4, a thickness fixed envelope is decreased and then increased by moving from P3 to P4. The fixed wrap can have the maximum thickness between P3 and an inner end portion of the fixed wrap.
[0015] According to another aspect of the invention, if a distance between an internal circumferential surface of the fixed envelope and a center axis of the rotation axis is DF, an internal contact point of the first compression chamber under discharge initiation is P3 and a point of internal contact of the first compression chamber 150 ° before starting the discharge operation for P4, the distance DF is increased and then decreased.
[0016] According to another aspect of the invention, if a distance between a center of the eccentric portion and an outer circumferential surface of the orbiting envelope is Do, an internal contact point of the first compression chamber under discharge initiation is P3 and an internal contact point from the first compression chamber 150 ° before starting the discharge operation is P4, the distance Do is increased and then decreased by moving from P3 to P4.
[0017] According to another aspect of the invention, a rotation axis coupling portion is formed in a central portion of the orbiting spiral, the eccentric portion coupled to the rotation axis coupling portion, in which a protruding portion protrudes from a surface inner circumferential of an inner end of the fixed envelope, and a recess portion is recessed into an outer circumferential surface of the coupling portion of the axis of rotation, the recess portion contacting at least part of the protruding portion.
[0018] According to another aspect of the invention, a coupling portion of the rotation axis is formed in a central portion of the orbiting spiral, the coupling portion of the rotation axis having an outer circumferential surface configuring a part of the orbiting envelope and having the eccentric portion coupled therein, where if an internal contact point of the first compression chamber under discharge initiation is P3 and an internal contact point of the first compression chamber 90 ° before discharge initiation is P5, Rm defined by the equation The following is less than an internal radius RH of the coupling portion of the rotation axis at an interval between P3 and P5:
[0019] According to another aspect of the invention, if an internal contact point of the first compression chamber under discharge initiation is P3, a distance between a tangent line at P3 and an O center of the eccentric portion is less than a diameter of the eccentric portion.
[0020] According to these aspects of the invention, the compression ratio of the first compression chamber can be increased when compared to a spiral compressor having a fixed wrap and an orbiting wrap having an involute shape. In addition, as the thickness of an inner end portion of the fixed wrap varies, the stiffness of the wrap can be enhanced and the leak prevention capability can be improved.
[0021] Furthermore, the scope of applicability of the present application will be more evident from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating particular modalities of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will be evident to those skilled in the art from detailed description. Brief Description of Drawings
[0022] The attached drawings, which are included to provide an additional understanding of the invention and are incorporated and form a part of this specification, illustrate exemplary modalities and together with the description serve to explain the principles of the invention. FIG. 1 is a sectional view schematically showing an internal structure of a spiral compressor according to an exemplary embodiment. FIG. 2 is a partially diagrammatic view showing a compression unit of the exemplary embodiment shown in FIG. 1. FIG. 3 is an exploded perspective view of the compression unit shown in FIG. two. FIGS. 4 (a) and 4 (b) are schematic views showing the first and second compression chambers just after suction and just before unloading in a spiral compressor having an orbiting shell and a fixed shell in involute form. FIG. 5 is a schematic planar view showing an orbiting wrap with an involute shape. FIGS. 6 (a) -6 (e) are seen showing a process for obtaining generating curves in the spiral compressor of an exemplary modality. FIG. 7 is a planar view showing the final generating curves shown in FIGS. 6 (a) -6 (e). FIG. 8 is a planar view showing an orbiting envelope and a fixed envelope formed by the generating curve shown in FIG. 7. FIG. 9 is an enlarged planar view of a central portion of FIG. 8. FIG. 10 is a graph showing a relationship between an angle α and a compression ratio. FIG. 11 is a planar view showing a state that the orbiting envelope contacts the fixed envelope at point P3. FIG. 12 is a planar view showing a state that the orbiting envelope contacts the fixed envelope at point P5. FIGS. 13 (a) and 13 (b) are schematic sectional views showing the modalities of a coupling portion of the axis of rotation of the orbiting spiral. FIG. 14 is a graph showing changes in compression ratios in response to an average radius of curvature Rm in the exemplary embodiment of FIG. 8. FIG. 15 is a planar view showing a state that the orbiting envelope contacts the fixed envelope at point P4. FIG. 16 is a planar view showing a time point when starting a discharge operation in a second compression chamber in the exemplary embodiment of FIG. 8. Detailed Description of the Invention
[0023] Hereinafter, the description will be made in detail to the exemplary modalities of a spiral compressor according to this invention with reference to the attached drawings.
[0024] As shown in FIG. 1, the exemplary embodiment may include a hermetic compressor 100 having a cylindrical housing 110, and an upper housing 112 and a lower housing 114 to cover the upper and lower portions of housing 110. The upper and lower housing 112 and 114 can be welded to the housing 110 to define a single hermetic space together with housing 110. A lower space of the hermetic compressor 100 can define a suction space, and an upper space of it can define a discharge space. The lower and upper spaces can be divided based on an upper structure 115 to be explained later.
[0025] A discharge pipe 116 can be connected to an upper side of the upper housing 112. The discharge pipe 116 can act as a path through which a compressed refrigerant is discharged outside. An oil separator (not shown) for separating the oil mixed with the discharged refrigerant can be connected to the discharge pipe 116. A suction pipe 118 can be installed on a side surface of the housing 110. The suction pipe 118 can act as a path through which a refrigerant to be compressed is introduced. Referring to FIG. 1, the suction pipe 118 is located at an interface between the housing 110 and the upper housing 116, but the position of the suction pipe 118 is not limited to this example. In addition, the lower housing 114 can function as an oil chamber for storing the oil that is provided to make the compressor run smoothly.
[0026] A motor 120 as a driving unit can be installed in an approximately central portion within housing 110. Motor 120 may include a stator 122 attached to an internal surface of housing 110, and a rotor 124 located within stator 122 and rotatable for interaction with stator 122. A axis of rotation 126 can be arranged in the center of rotor 124 to be rotatable together with rotor 124.
[0027] An oil passage 126a can be formed in the center of the axis of rotation 126 along a longitudinal direction of the axis of rotation 126. An oil pump 126b for inflating the oil stored in the lower housing 114 can be installed in a portion of the lower end of the axis of rotation 126. Oil pump 126b can be implemented by forming a spiral recess or by installing an impeller separately in the oil passage 126a, or it can be a separately welded pump.
[0028] A part of extended diameter 126c, which is inserted into a cube formed in a fixed spiral to be explained later, can be arranged in a portion of the upper end of the axis of rotation 126. The part of extended diameter 126c may have a diameter greater than the other parties. A pin portion 126d can be formed at one end of the extended diameter portion 126c. Alternatively, the extended diameter portion 126c may not be used, and the entire axis of rotation 126 may have a specific diameter.
[0029] An eccentric bearing 128 can be inserted into the pin portion 126d, as shown in FIG. 2. Referring to FIG. 3, eccentric bearing 128 can be eccentrically inserted into the pin portion 126d. A coupled portion between the pin portion 126d and the eccentric bearing 128 can be shaped like the letter "D" so that the eccentric bearing 128 cannot be rotated with respect to the pin portion 126d.
[0030] A fixed spiral 130 can be mounted on a boundary portion between the housing 110 and the upper housing 112. The fixed spiral 130 can have an outer circumferential surface that is fitted under shrinkage between the housing 110 and the upper housing 112. Alternatively, the fixed spiral 130 can be welded with housing 110 and upper housing 112.
[0031] Hub 132, into which the axis of rotation 126 is inserted, can be formed on a lower surface of the fixed spiral 130. A hollow hole through which the pin portion 126d of the axis of rotation 126 is inserted, can be formed through a upper surface of cube 132, as shown in FIG. 1. Consequently, the pin portion 126d may protrude to an upper side of a disk 134 of the fixed spiral 130 through the hollow hole.
[0032] A fixed sheath 136 which is set with an orbiting sheath to be explained later to define the compression chambers may be formed on an upper surface of the disc 134. A side wall 138 may be located on an outer circumferential portion of the disc 134. The side wall 138 can define a space to accommodate an orbiting spiral 140 to be explained later and be contactable with an inner circumferential surface of the housing 110. An orbiting spiral support 138a in which an outer circumferential portion of the orbiting spiral 140 is received , may be formed within a portion of the upper end of the side wall 138. A height of the orbiting spiral support 138a may be the same height as the fixed envelope 136 or may be slightly lower than the fixed envelope 136, so that a end of the orbiting shell may contact a surface of the disc 134 of the fixed spiral 130.
[0033] The orbiting envelope 140 can be arranged on the fixed spiral 130. The orbiting envelope 140 can include a disc 142 having an approximately circular shape and an orbiting envelope 144 set with the fixed envelope 136. A coupling portion of the axis of rotation 146 in a shape approximately circular can be formed in the central portion of the disk 142 so that the eccentric bearing 128 can be inserted rotationally into it. An outer circumferential portion of the coupling portion of the rotation axis 146 can be connected to the orbiting envelope 144 to define the compression chambers together with the fixed envelope 136 during compression that will be described later.
[0034] Eccentric bearing 128 can be inserted into the coupling portion of the axis of rotation 146, and the end portion of the axis of rotation 126 can be inserted through the disc 134 of the fixed spiral 130, so that the orbiting envelope 144, the fixed envelope 136 and eccentric bearing 128 can overlap in a lateral direction of the compressor. Under compression, a repulsive force of a refrigerant can be applied to the fixed shell 136 and the orbiting shell 144, while a compressive force as a reaction force against the repulsive force can be applied between the coupling portion of the axis of rotation 146 and the eccentric bearing 128. As such, when the shaft is partially inserted through the disc and superimposes the envelope, the repulsive force of the refrigerant and the compressive force can be applied to the same lateral surface based on the disc, thus being attenuated with each other. Therefore, the orbiting envelope 140 can be prevented from being tilted due to the compressive force and the repulsive force. As an alternate example, an eccentric bushing can be installed instead of the eccentric bearing. In this example, an inner surface of the coupling portion of the rotation shaft 146 into which the eccentric bushing is inserted, can be specifically processed to serve as a bearing. Also, another example of installing a separate bearing between the eccentric bushing and the rotating shaft coupling portion can be designed.
[0035] A discharge port 140a can be formed in disc 142 so that a compressed refrigerant can be discharged into the housing. The position and shape of the discharge port 140a can be determined by considering a required discharge pressure or others. The disk 142 may also include a bypass hole in addition to the discharge hole 140a. When the bypass orifice is further away from the center of the disc 142 than the discharge orifice 140a, the bypass may have a diameter greater than one third of an effective diameter of the discharge orifice 140a.
[0036] An Oldham ring 150 to prevent rotation of the orbiting spiral 140 can be installed on the orbiting spiral 140. The Oldham ring 150 can include a portion of the ring 152 having an approximately circular shape and inserted into a rear surface of the disk 142 of the orbiting shell 140 , and a pair of first keys 154 and a pair of second keys 156 that protrude to a lateral surface of the ring part 152. The first keys 154 can protrude much longer than a thickness of an outer circumferential portion of disk 142 of the orbiting shell 140, thus being inserted into the recesses of the first key 154a, which are recessed at an upper end of the side wall 138 of the fixed spiral 130 and of the orbiting shell support 138a. In addition, the second keys 156 can be inserted into the recesses of the second key 156a which are formed in the outer circumferential portion of the disk 142 of the orbiting shell 140.
[0037] Each of the recesses of the first key 154a can have a perpendicular portion that extends upwards and a horizontal portion that extends in a right-left-hand direction. During an orbit movement of the orbiting spiral 140, a portion of the lower end of each first key 154 remains inserted into the horizontal portion of the recess of the corresponding first key 154a while a portion of the outer end of the first key 154 in a radial direction is separated from the portion perpendicular to the recess of the first key 154a. That is, the recesses of the first key 154a and the fixed spiral 130 are coupled together in a perpendicular direction which can allow the reduction of a diameter of the fixed spiral 130.
[0038] In detail, a clearance (air gap) as wide as an orbit radius should be ensured between the disk 142 of the orbiting envelope 140 and an inner wall of the fixed spiral 130. If Oldham ring keys are attached to a fixed spiral in a radial direction, key recesses formed in the fixed spiral should be longer than at least the orbit radius to prevent the Oldham ring from being separated from the key recesses during orbiting movement. However, this structure can cause an increase in the size of the fixed spiral.
[0039] On the other hand, as shown in the exemplary embodiment, if the recess of the second key 156a extends to a lower side of a space between the disc 142 of the orbiting envelope 140 and the orbiting envelope 144, a sufficient length of the key recess 156a can be ensured even without increasing the size of the fixed spiral 130.
[0040] In addition, in the exemplary embodiment, all Oldham 150 ring keys are formed on a side surface of the ring portion 152. This structure can therefore reduce the perpendicular height of a compression unit when compared to the formation of keys in both side surfaces.
[0041] However, as shown in FIG. 1, a lower frame 113 for rotatorily supporting a lower side of the axis of rotation 126 can be installed on a lower side of the housing 110, and an upper structure 115 for supporting the orbiting envelope 140 and the Oldham ring 150 can be installed. in the orbiting spiral 140. An orifice 115a is formed in the upper structure 115. Orifice 115a can communicate with an outlet orifice 140a of orbiting shell 140 to allow a compressed refrigerant to be discharged into the upper housing 112.
[0042] Henceforth, before explaining the shape of a fixed spiral and an orbiting spiral of the present invention, a description will be given of an example with an orbiting and a fixed envelope each having an involute shape to help understand the invention.
[0043] FIGS. 4 (a) and 4 (b) are planar views showing a compression chamber just after a suction operation and a compression chamber just before a discharge operation in a spiral compressor having an orbiting and fixed casing formed as a involute curve and having an axis partially inserted through a disc. FIG. 4 (a) shows the alteration of a first compression chamber defined between an internal side surface of the fixed envelope and an external side surface of the orbiting envelope, and FIG. 4 (b) shows the alteration of a second compression chamber defined between an internal lateral surface of the orbiting envelope and an external lateral surface of the fixed envelope.
[0044] In the configuration of a spiral compressor, a compression chamber is defined between two points of contact generated by contact between the fixed envelope and the orbiting envelope. By having the fixed wrapping and the orbiting wrapping having an involute curve, as shown in FIGS. 4 (a) and 4 (b), two points of contact that define a compression chamber are present in a line. In other words, the compression chamber extends 360 ° with respect to the center of the axis of rotation.
[0045] With respect to a change in volume of the first compression chamber shown in FIG. 4 (a), the volume of the compression chamber is gradually reduced by moving to the central portion in response to the orbiting movement of the orbiting spiral. Thus, when it arrives at an external circumferential portion of a coupling portion of the axis of rotation located in the center of the orbiting spiral, the first compression chamber has the minimum volume value. For fixed wrapping and orbiting wrapping having the involute curve, the volume reduction rate linearly decreases as an orbiting angle (hereinafter referred to as the 'crank angle') of the rotation axis increases. Consequently, in order to obtain a high compression ratio, the compression chamber must orient itself as close to the center as possible. However, when the axis of rotation is present in the central portion, the compression chamber can only move inwardly in the outer circumferential portion of the axis of rotation. Consequently, the compression ratio is decreased. A compression ratio of about 2.13: 1 is shown in FIG. 4 (a).
[0046] However, the second compression chamber shown in FIG. 4 (b) has a much lower compression ratio than the first compression chamber, being approximately 1.46: 1. However, with respect to the second compression chamber, if the shape of the orbiting spiral is changed so that a portion connected between a coupling portion of the rotation axis P and the orbiting envelope is formed in an arcuate shape, a compression path of the second compression chamber even before a discharge operation extends, thereby increasing the compression ratio up to about 3.0. In this case, the second compression chamber can extend less than 360 ° just before the unloading operation. However, this method may not be applied to the first compression chamber.
[0047] Therefore, when the fixed wrapping and the orbiting wrapping are involute, the second compression chamber may have a high compression ratio but the first compression chamber cannot. Also, when the two compression chambers have a noticeable difference in their compression ratios, it can negatively affect the operation of the compressor and even decrease the overall compression ratio.
[0048] To solve the problem, the exemplary modality shows the fixed wrapping and the orbiting wrapping having a different curve (shape) than the involute curve. FIGS. 6 (a) - 6 (e) show a process of deciding the forms of fixed and orbiting wrapping according to the exemplary modality. In FIGS. 6 (a) -6 (e), a solid line indicates a generating curve for the first compression chamber and a dotted line indicates a generating curve for the second compression chamber.
[0049] Here, the generative curve refers to a line drawn by a particular shape during the movement. The solid line indicates a line drawn by the first compression chamber during the suction and discharge operations, and the dotted line indicates the line of the second compression chamber. Consequently, if the generating curve is moved in parallel to both sides as long as the orbit radius of the orbiting spiral based on the solid line, it shows the shapes of an internal side surface of the fixed envelope and an external side surface of the orbiting envelope. . If the generating curve is moved in parallel based on the dotted line, it shows the shapes of an external lateral surface of the fixed envelope and an internal lateral surface of the orbiting envelope.
[0050] FIG. 6 (a) shows a generatrix curve corresponding to having the wrapping shape shown in FIG. 5. Here, a part indicated by a bold line corresponds to the first compression chamber just before an unloading operation. As shown, a start point and an end point are present on one line. In this case, it is difficult to obtain a sufficient compression ratio. Thus, as shown in FIG. 6 (b), a portion of the end of the bolded line, located outside, is transferred in a direction to the right along the generating curve and a portion of the end located inside is transferred to be contactable to a certain extent with the coupling portion of the rotation axis. That is, a portion of the generating curve, adjacent to the coupling portion of the axis of rotation, can be curved to have a smaller radius of curvature.
[0051] As described above, in the aspect of the characteristic of the spiral compressor, the compression chamber is formed by two points of contact where the orbiting envelope and the fixed envelope come into contact with each other. Both ends of the line in bold in FIG. 6 (a) correspond to the two points of contact. Normal vectors at the respective points of contact are in parallel with each other according to the operational algorithm of the spiral compressor. Also, the normal vectors are parallel to a line that connects a center of the axis of rotation and a center of the eccentric bearing. Here, for the fixed wrapping and the orbiting wrapping having the involute shape, the two normal vectors are in parallel with each other and also present on the same line as shown in FIG. 6 (a).
[0052] In FIG. 6 (a), if it is assumed that the center of the coupling portion of the axis of rotation 146 is O and two points of contact are P1 and P2, P2 is located on a line connecting O and P1. If it is assumed that a greater angle of the angles formed by the lines OP1 and OP2 is a, a is 360 °. In addition, if it is assumed that a distance between the normal vectors in P1 and P2 is l, l is 0.
[0053] The inventors observed from the investigation that when P1 and P2 are transferred more internally along the generating curves, the compression ratio of the first compression chamber can be improved. For this purpose, when P1 is transferred to the coupling portion of the axis of rotation 146, namely, the generating curve for the first compression chamber is transferred by turning towards the coupling portion of the axis of rotation 146, P1, which has the normal vector in parallel to the normal vector at P2, then rotates in a right direction based on FIG. 6 (b), when compared to FIG. 6 (a), thus being located at the rotated point. As described above, the first compression chamber is reduced in volume and is transferred more internally along the generating curve. Consequently, the first compression chamber shown in FIG. 6 (b) can be transferred more internally when compared to FIG. 6 (a), and still compressed while being transferred, thus obtaining an increased compression ratio.
[0054] Referring to FIG. 6 (b), the point P1 is excessively close to the coupling portion of the axis of rotation 146, and therefore the coupling portion of the axis of rotation 146 becomes thinner in thickness. Consequently, point P1 is transferred back to modify the generating curve as shown in FIG. 6 (c). Here, in FIG. 6 (c), the generating curves of the first and second compression chambers are excessively close to each other making the envelope thickness too thin or preventing a envelope from being physically formed. Thus, as shown in FIG. 6 (d), the generating curve of the second compression chamber can be modified so that the two generating curves can maintain a predetermined interval between them.
[0055] In addition, the generating curve of the second compression chamber is modified, as shown in FIG. 6 (e), so that an arcuate portion A located at the end of the generating curve of the second compression chamber is contactable with the generating curve of the first compression chamber. Generator curves can be continuously modified to maintain a predetermined interval between them. When a radius of the arcuate portion A of the generating curve of the second compression chamber is increased to ensure rigidity of the wrapping at the end of the fixed wrapping, the generating curves that have the shape shown in FIG. 7 can be obtained.
[0056] FIG. 8 is a planar view showing an orbiting envelope and a fixed envelope obtained based on the generating curves of FIG. 7, and FIG. 9 is an enlarged planar view of the central portion of FIG. 8. For reference, FIG. 8 shows a position of the orbiting envelope at a point in time of the start of the discharge operation in the first compression chamber. Here, the point P1 in FIG. 8 indicates a point, which is present on the inside, of the two contact points that define a compression chamber, at the moment when starting the discharge in the first compressor chamber. Line S is a virtual line to indicate a position of the axis of rotation and circle C is a line drawn by line S. Henceforth, the crank angle is adjusted to 0 ° when line S is present in a state shown in FIG. 8, namely, when starting the discharge, set to a negative value (-) when turned to the left, and set to a positive value (+) when turned to the right.
[0057] Referring to FIGS. 8 and 9, it can be shown that an angle α defined by two lines connecting the two contact points P1 and P2 respectively to the center O of the coupling portion of the axis of rotation is less than 360 °, and a distance í between the vectors normal at each of the contact points P1 and P2 is greater than 0. Consequently, the first compression chamber just before a discharge operation may have a volume lower than that defined by the fixed wrapping and the orbiting wrapping having the invo-fight shape , which results in an increase in the compression ratio. In addition, the orbiting envelope and the fixed envelope shown in FIG. 8 have a shape that a plurality of arcs having different diameters and origins are connected and the outermost curve can be approximately oval in shape with a major geometric axis and a minor geometric axis.
[0058] In the exemplary mode, the angle α can be adjusted to have a value in the range of 270 ° to 345 °. FIG. 10 is a graph showing angle α and a compression ratio. From the perspective of improving a compression ratio, it may be advantageous to adjust the angle α to be low. However, if the angle α is less than 270 °, it can inhibit mechanical processing, thus resulting in poor productivity and increasing the price of a compressor. If the angle α exceeds 345 °, the compression ratio can be decreased below 2.1, thus not providing a sufficient compression ratio.
[0059] In addition, a protruding portion 160 may protrude from near an inner end of the fixed envelope to the coupling portion of the axis of rotation 146. A contact portion 162 may further be formed by protruding from the protruding portion 160. That is, the inner end of the fixed wrap 130 may be thicker than the other portions. Consequently, the wrapping rigidity of the inner end of the fixed wrapping under which the strongest compressive force is applied, can be improved, resulting in enhanced durability.
[0060] The thickness of the fixed envelope is gradually decreased, starting from the internal contact point P1 of the two contact points that define the first compression chamber when starting the discharge operation, as shown in FIG. 9. More particularly, a first part 164 can be formed adjacent to the contact point P1 and a second part 166 can extend from the first part 164. A rate of reduction in thickness in the first part 164 may be higher than in the second part 166 After the second part 166, the fixed wrap can be increased in thickness within a predetermined range.
[0061] If it is assumed that a distance between an internal lateral surface of the fixed envelope and a center O 'of the axis of rotation is Df, the distance Df can be increased and then decreased by moving away from P1 in a left direction (based on in FIG. 9), and such a gap is shown in FIG. 15. FIG. 15 is a planar view showing the position of the orbiting wrap 150 ° before starting the unloading operation, namely, when the crank angle is 210 °. If the axis of rotation rotates 150 ° more than the state of FIG. 15, arrives at the state shown in FIG. 9. Referring to FIG. 15, an internal contact point P4 of two contact points defining the first compression chamber is located above the coupling portion of the axis of rotation 146, and the DF is increased and then decreased in the range of P1 of FIG. 9 to P4 of FIG. 15.
[0062] The coupling portion of the rotation axis 146 may be provided with a recess portion 170 flush with the protruding portion 160. A side wall of the recess portion 170 may contact the contact portion 162 of the protruding portion 160 to define a point contact point of the first compression chamber. If it is assumed that a distance between the center O of the coupling portion of the axis of rotation 146 and an outer circumferential portion of the coupling portion of the axis of rotation 146 is Do, the distance Do can be increased and then decreased over the interval between P1 of FIG. 9 and P4 of FIG. 15. Similarly, the thickness of the coupling portion of the axis of rotation 146 can also be increased and then decreased over the interval between P1 of FIG. 9 and P4 of FIG. 15.
[0063] A side wall of the recess portion 170 may include a first augmentation part 172 in which a thickness is relatively substantially increased, and a second augmentation part 174 extending from the first augmentation part 172 and having an increased thickness at a relatively low rate. These correspond to the first part 164 and the second part 166 of the fixed wrapping 136. The first augmentation part 172, the first enlargement part 164, the second enlargement part 174 and the second part 166 can be obtained by turning the generatrix curve towards the portion of coupling the axis of rotation 146 in the step of FIG. 6 (b). Consequently, the internal contact point Pi that defines the first compression chamber can be located in the first and second enlargement parts 172, 174, and also the length of the first compression chamber just before the discharge operation can be shortened to intensify the compression ratio.
[0064] Another side wall of the recess portion 170 may have an arcuate shape. An arc diameter can be determined based on the thickness of the fixed envelope end wrap 136 and the orbiting radius of the orbiting envelope 144. When the thickness of the fixed wrap end increases, the arc diameter increases. Consequently, the thickness of the orbiting envelope close to the arc can increase to ensure durability, and the compression path can also extend to increase the compression ratio of the second compression chamber.
[0065] The central portion of the recess portion 170 can form a part of the second compression chamber. FIG. 16 is a planar view showing the position of the orbiting envelope when starting the discharge operation in the second compression chamber. Referring to FIG. 16, the second compression chamber is defined between two contact points P6 and P7 and contacts an arcuate side wall of the recess portion 170. When the axis of rotation rotates further, one end of the second compression chamber can pass through the center of the portion recess 170.
[0066] FIG. 11 is another planar view showing a state which is also shown in FIG. 9. Referring to FIG. 11, a tangent line T drawn at point P3, which is equal to point Pi in FIG. 9, traverses the inside of the coupling portion of the axis of rotation. This results from the behavior that the generating curve is curved inward during the process of FIG. 6 (b). Therefore, a distance between the tangent line T and a center of the coupling portion of the axis of rotation O is less than a radius RH within the coupling portion of the axis of rotation, so that a shorter distance between the tangent line T in P3 and an O center of eccentric bearing 128 is less than a radius of eccentric bearing 128.
[0067] Referring to FIGS. 13 (a) and 13 (b), the inner radius RH can be defined as an inner radius of the rotating shaft coupling portion when an inner circumferential surface of the rotating shaft coupling portion or an outer circumferential surface of the eccentric bearing is lubricated without a separate bearing, as shown in FIG. 13 (a), or can be defined as an external radius of the bearing when a separate bearing is additionally employed within the coupling portion of the axis of rotation as shown in FIG. 13 (b).
[0068] In FIGS. 11 and 12, a point P5 denotes an internal contact point when the crank angle is 270 °, as shown in FIG. 12. A radius of curvature of an outer circumference of the coupling portion of the axis of rotation can have various values depending on each position between points P3 and P5. Here, the average radius of curvature Rm defined by the following equation can influence the compression ratio of the first compression chamber:
[0069] FIG. 14 is a graph showing a relationship between an average radius of curvature and a compression chamber. In general, with respect to a rotary compressor, it can have a compression ratio greater than 2.3 when used for cooling and heating, and greater than 2.1 when used for cooling. Referring to FIG. 14, when the average radius of curvature is less than 10.5, the compression ratio can be greater than 2.1. Therefore, if Rm is set to be less than 10.5 mm, the compression ratio can be greater than 2.1. Here, Rm can be optionally adjusted to be suitable for the use of the spiral compressor. In the exemplary mode, the RH can have a value of approximately 15 mm. Therefore, the Rm can be adjusted to be less than RH / 1.4.
[0070] However, point P5 cannot always be limited when the crank angle is 270 °. In view of the spiral compressor's operational algorithm, a design variable with respect to a radius of curvature up to 270 ° is low. Consequently, to improve a compression ratio, it is advantageous to change a shape between 270 ° and 360 ° in which the design variable is relatively high.
[0071] The foregoing modalities and advantages are merely exemplary and are not to be construed as limiting the present revelation. The present teachings can be easily applied to other types of devices. This description is intended to be illustrative, and not to limit the scope of the claims. Many alternatives, modifications, and variations will be evident to those skilled in the art. The aspects, structures, methods, and other characteristics of the exemplary modalities described here can be combined in various ways to obtain additional and / or alternative exemplary modalities.
[0072] As the present aspects can be incorporated in various forms without abandoning their characteristics, it should also be understood that the modalities described above are not limited by any of the details of the previous description, unless otherwise specified, but should preferably be interpreted broadly within its scope as defined in the appended claims, and therefore all changes and modifications that fall within the limits and confrontations of the claims, or equivalents of such limits and confrontations, are therefore intended to be covered by the appended claims.

权利要求:
Claims (14)
[0001]
Spiral compressor, comprising: a fixed spiral (130) having a disc (134) and a fixed shell (136) being formed on an upper surface of the disc (134); an orbiting spiral (140) having an orbiting envelope (144), the orbiting envelope (144) being configured to define first and second compression chambers on an external lateral surface and an internal lateral surface thereof together with the fixed envelope ( 136), the orbiting spiral (140) being configured to perform an orbiting movement in relation to the fixed spiral (130); an axis of rotation (126c) having an eccentric portion, the eccentric portion being coupled to the orbiting envelope (144); and a driving unit (120) configured to drive the axis of rotation (126c), CHARACTERIZED by the fact that a portion of the axis of rotation (126c) having the eccentric portion (128) is inserted through the disc (134) of the fixed spiral (130) so that the orbiting envelope (144), the fixed envelope (136) and the eccentric portion (128) overlap in a lateral direction; the first compression chamber is defined between two contact points P1 and P2 generated by the contact between an internal lateral surface of the fixed envelope (136) and an external lateral surface of the orbiting envelope (144); where 0 ° <α <360 °, where α is an angle defined by two lines connecting an O center of the eccentric portion to the two contact points P1 and P2, respectively; and a distance l between the normal lines at the two contact points P1 and P2 is greater than 0.
[0002]
Spiral compressor according to claim 1, CHARACTERIZED by the fact that the normal lines at the two contact points P1 and P2 are different from each other.
[0003]
Spiral compressor according to claim 1, CHARACTERIZED by the fact that a coupling portion of the rotation axis (146) is formed in a central portion of the orbiting spiral (140), the coupling portion of the rotation axis (146) having an outer circumferential surface defining a part of the orbiting envelope (144), an inner side of the rotating axis coupling portion (146) being coupled to the eccentric portion (128), where 0 ° <α <360 ° el > 0 when the first compression chamber is located on the outer circumferential surface of the coupling portion of the axis of rotation (146) ..
[0004]
Spiral compressor according to claim 1, CHARACTERIZED by the fact that 270 ° <α <345 ° and l> 0.
[0005]
Spiral compressor according to claim 1, CHARACTERIZED by the fact that the axis of rotation (126) comprises: a shaft portion (126) connected to the driving unit (120); a pin portion (126d) formed at one end of the shaft portion (126) to be concentric with the shaft portion (126); an eccentric bearing (128) eccentrically provided in the pin portion (126d); and a rotating shaft coupling portion (126c) formed in a central portion of the orbiting spiral (140), wherein the eccentric bearing (128) is rotatorily coupled to the coupling portion of the rotation shaft (146).
[0006]
Spiral compressor according to claim 5, CHARACTERIZED by the fact that it additionally comprises: a protruding portion (160) protruding from an internal circumferential surface of an internal end of the fixed envelope (136); and a recess portion (170) recessed in an outer circumferential surface of the rotating shaft coupling portion (146), wherein the outer circumferential surface of the coupling portion of the axis of rotation (146) in the recess portion (170) contacts the protruding portion (160) of the fixed envelope (136).
[0007]
Spiral compressor according to claim 6, CHARACTERIZED by the fact that the recess portion (170) comprises: a first magnifying part (172) defining a side wall of the recess portion (170); and a second increase part (174) extending from the first increase part (172), wherein a rate of increase in thickness of the coupling portion of the axis of rotation (146) in the first augmentation part (172) is higher than in the second augmentation part (174).
[0008]
Spiral compressor according to claim 7, CHARACTERIZED by the fact that the thickness of the coupling portion of the rotation shaft (146) is reduced after the second augmentation part (174).
[0009]
Spiral compressor according to claim 7, CHARACTERIZED by the fact that another side wall of the recess portion (170) is arched.
[0010]
Spiral compressor according to claim 1, CHARACTERIZED by the fact that a shorter distance between an O center of the eccentric portion (128) and a tangent line in P3 is less than a radius of the eccentric portion, where P3 is a point of contact between the orbiting envelope (144) and the fixed envelope (136) defining an end of the first compression chamber, where a shorter distance between an O center of the eccentric portion (128) and a tangent line in P3 is less than a radius of the eccentric portion, where P3 is a point of contact between the orbiting envelope (144) and the fixed envelope (136) defining an end of the first compression chamber.
[0011]
Spiral compressor, according to claim 10, CHARACTERIZED by the fact that point P3 is defined as the internal contact point of the first compression chamber upon initiation of discharge from the first compression chamber.
[0012]
Spiral compressor according to claim 11, CHARACTERIZED by the fact that a thickness of the fixed envelope (136) is decreased and then increased by moving in a direction from P3 to P4, where P4 is an internal contact point of the first compression chamber 150 ° before starting the discharge operation of the first compression chamber.
[0013]
Spiral compressor according to claim 12, CHARACTERIZED by the fact that the fixed casing (136) is thicker at a location between P3 and an internal end of the fixed casing (136).
[0014]
Spiral compressor according to claim 13, CHARACTERIZED by the fact that a distance Do is increased and then decreased by moving from P3 to P4, where Do is a distance between a center of the eccentric portion (128) and an external circumferential surface orbiting envelope (144).

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引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

DE1935621A1|1968-07-22|1970-01-29|Leybold Heraeus Gmbh & Co Kg|Displacement pump|

AU545656B2|1980-09-30|1985-07-25|Sanden Corporation|Scroll pump seal|

JPH045832B2|1982-07-30|1992-02-03|Tokyo Shibaura Electric Co|

US4927341A|1987-11-23|1990-05-22|Copeland Corporation|Scroll machine with relieved flank surface|

JP2718295B2|1991-08-30|1998-02-25|ダイキン工業株式会社|Scroll compressor|

EP0682181B1|1994-03-15|1998-08-26|Denso Corporation|Scroll compressor|

JP3124437B2|1994-06-09|2001-01-15|株式会社日立製作所|Scroll compressor|

JP3708573B2|1994-12-16|2005-10-19|株式会社日立製作所|Shaft-through two-stage scroll compressor|

AU4645196A|1994-12-23|1996-07-19|Bristol Compressors, Inc.|Scroll compressor having bearing structure in the orbiting scroll to eliminate tipping forces|

JP3110970B2|1995-02-24|2000-11-20|株式会社日立製作所|Shaft penetrating scroll compressor|

JP3194076B2|1995-12-13|2001-07-30|株式会社日立製作所|Scroll type fluid machine|

US6120268A|1997-09-16|2000-09-19|Carrier Corporation|Scroll compressor with reverse offset at wrap tips|

JP2000027775A|1998-07-15|2000-01-25|Fujitsu General Ltd|Scroll compressor|

CN1164871C|2000-10-23|2004-09-01|Lg电子株式会社|Scroll compressor|

JP3693041B2|2002-06-17|2005-09-07|ダイキン工業株式会社|Scroll compressor|

US6736622B1|2003-05-28|2004-05-18|Scroll Technologies|Scroll compressor with offset scroll members|

US7789640B2|2004-12-21|2010-09-07|Daikin Industries, Ltd.|Scroll fluid machine with a pin shaft and groove for restricting rotation|

JP2006242133A|2005-03-04|2006-09-14|Denso Corp|Fluid machine|

JP2006257941A|2005-03-16|2006-09-28|Sanden Corp|Scroll compressor|

US7753663B2|2005-05-17|2010-07-13|Daikin Industries, Ltd.|Mounting structure of discharge valve in rotary compressor|

JP2007154761A|2005-12-05|2007-06-21|Daikin Ind Ltd|Scroll compressor|

JP2007162475A|2005-12-09|2007-06-28|Mitsubishi Electric Corp|Scroll compressor|

JP4969878B2|2006-03-13|2012-07-04|アネスト岩田株式会社|Scroll fluid machinery|

JP5065234B2|2008-11-28|2012-10-31|サンデン株式会社|Scroll type fluid machinery|

JP4941480B2|2009-02-03|2012-05-30|パナソニック株式会社|Scroll compressor|JP2620399B2|1990-08-20|1997-06-11|鐘淵化学工業株式会社|3'-alkyl or arylsilyloxybenzoxazinolifamycin derivatives|

KR101811291B1|2011-04-28|2017-12-26|엘지전자 주식회사|Scroll compressor|

KR101282227B1|2011-09-21|2013-07-09|엘지전자 주식회사|Scroll compressor|

KR20130031734A|2011-09-21|2013-03-29|엘지전자 주식회사|Scroll compressor|

KR101282228B1|2011-09-21|2013-07-09|엘지전자 주식회사|Scroll compressor|

KR20130034538A|2011-09-28|2013-04-05|엘지전자 주식회사|Scroll compressor|

US20130078129A1|2011-09-28|2013-03-28|Cheolhwan Kim|Scroll compressor|

KR101285619B1|2011-09-28|2013-07-12|엘지전자 주식회사|Scroll compressor|

KR101285618B1|2011-09-28|2013-07-12|엘지전자 주식회사|Scroll compressor|

KR101216466B1|2011-10-05|2012-12-31|엘지전자 주식회사|Scroll compressor with oldham ring|

KR101277213B1|2011-10-11|2013-06-24|엘지전자 주식회사|Scroll compressor with bypass hole|

KR101275190B1|2011-10-12|2013-06-18|엘지전자 주식회사|Scroll compressor|

KR101849138B1|2012-01-04|2018-04-16|엘지전자 주식회사|Scroll compressor with shaft inserting portion and manufacturing method thereof|

KR101441928B1|2012-03-07|2014-09-22|엘지전자 주식회사|Horizontal type scroll compressor|

KR101386485B1|2012-09-24|2014-04-18|엘지전자 주식회사|Scroll compressor with a bearing|

KR101308753B1|2012-09-24|2013-09-12|엘지전자 주식회사|Synthetic resine bearing and scroll compressor with the same|

CN103028904B|2012-11-23|2015-06-03|湖州德卡斯电子有限公司|Preparation method of brake boosting system device and product thereof|

JP5540192B2|2012-12-03|2014-07-02|株式会社リッチストーン|Scroll liquid pump|

JP6267441B2|2013-05-28|2018-01-24|株式会社ヴァレオジャパン|Scroll compressor|

JP6213855B2|2013-06-24|2017-10-18|エルジー・ケム・リミテッド|Heat recovery equipment|

JP6235964B2|2014-05-13|2017-11-22|株式会社Ｓｏｋｅｎ|Scroll compressor|

KR102234708B1|2014-08-06|2021-04-01|엘지전자 주식회사|compressor|

KR102226457B1|2014-08-08|2021-03-11|엘지전자 주식회사|compressor|

KR102241201B1|2014-08-13|2021-04-16|엘지전자 주식회사|Scroll compressor|

CN104196723A|2014-09-18|2014-12-10|乔建设|Multiplying power line body scroll compressor|

EP3306096A4|2015-06-03|2018-10-31|Hitachi Industrial Equipment Systems Co., Ltd.|Scroll-type fluid machine|

JP6718223B2|2015-11-20|2020-07-08|三菱重工サーマルシステムズ株式会社|Scroll fluid machinery|

KR20170122020A|2016-04-26|2017-11-03|엘지전자 주식회사|Scroll compressor|

CN109996962B|2016-11-24|2021-02-26|松下知识产权经营株式会社|Asymmetric scroll compressor|

KR102318123B1|2017-04-20|2021-10-27|엘지전자 주식회사|Scroll compressor|

US10711782B2|2017-04-20|2020-07-14|Lg Electronics Inc.|Scroll compressor with wrap contour modification|

KR102318124B1|2017-04-24|2021-10-27|엘지전자 주식회사|Scroll compressor|

KR20180136282A|2017-06-14|2018-12-24|엘지전자 주식회사|Compressor having centrifugation and differential pressure structure for oil supplying|

KR101974272B1|2017-06-21|2019-04-30|엘지전자 주식회사|Compressor having merged flow path structure|

KR20190000171A|2017-06-22|2019-01-02|엘지전자 주식회사|Compressor having lubrication structure for thrust surface|

KR20190000688A|2017-06-23|2019-01-03|엘지전자 주식회사|Compressor having enhanced discharge structure|

KR20190006400A|2017-07-10|2019-01-18|엘지전자 주식회사|Compressor having enhanced discharge structure|

KR20190011115A|2017-07-24|2019-02-01|엘지전자 주식회사|Compressor having centrifugation structure for supplying oil|

CN112041561A|2018-04-27|2020-12-04|三菱电机株式会社|Scroll compressor and refrigeration cycle device|

KR20190135375A|2018-05-28|2019-12-06|엘지전자 주식회사|Scroll compressor having enhanced discharge structure|

JP6956131B2|2019-03-28|2021-10-27|株式会社豊田自動織機|Scroll compressor|

RU2763334C1|2021-05-18|2021-12-28|Леонид Михайлович Курин|Scroll compressor range of scroll compressor|

法律状态:
2013-11-05| B03A| Publication of a patent application or of a certificate of addition of invention [chapter 3.1 patent gazette]|

2018-12-18| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

2019-12-10| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

2021-01-12| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

2021-03-23| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 07/03/2012, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

申请号 | 申请日 | 专利标题

KR20110021108|2011-03-09|

KR10-2011-0021108|2011-03-09|

KR10-2011-0046492|2011-05-17|

KR1020110046492A|KR101059880B1|2011-03-09|2011-05-17|Scroll compressor|

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