Scroll compressor

Abstract

The purpose of the present invention is to maximize compression space and prevent unstable behavior of an orbiting scroll during low-speed operation of a scroll compressor. To this end, the present invention includes a rotary shaft having eccentric portions offset from the center of the shaft, wherein a plurality of the eccentric portions are formed along the axial direction of the rotary shaft and coupled to the orbiting scroll.

Description

Scroll compressor

[0001] The present invention relates to a scroll compressor installed such that a rotating shaft penetrates between the laps of a swivel scroll.

[0002] Generally, a compressor is a device or apparatus used for generating high pressure or transporting high-pressure fluids. Among these compressors, those applied to refrigeration cycles, such as those in refrigerators or air conditioners, perform the function of compressing refrigerant gas and transferring it to the condenser.

[0003] Among the compressors mentioned above, the scroll compressor is a type of compressor in which the rotating scroll among two scrolls installed facing each other rotates around the non-rotating scroll, and the compression chamber created between the laps of each scroll gradually narrows to compress the refrigerant.

[0004] Meanwhile, conventional general scroll compressors are configured such that an eccentric part is inserted into a boss formed on the rotating scroll to rotate the scroll. However, this structure has a problem in that the rotating scroll is subjected to an overturning moment, causing it to behave unstably, because the connection point of the eccentric part has a height difference from the point receiving the gas force of the rotating wrap.

[0005] In addition, in the case of conventional back-pressure scroll compressors, back pressure is generated only when the spinning scroll rotates at a high speed above a certain level, causing the non-spinning scroll to be pressed against the spinning scroll, thereby reducing unstable behavior.

[0006] However, heating and cooling systems using scroll compressors require various operating conditions, and these conditions include the low-speed rotation of the slewing scroll. For example, in the case of an air conditioner where multiple indoor units are connected to a single outdoor unit and the system is controlled to operate only one indoor unit at a low speed, the slewing scroll is operated to rotate slowly.

[0007] When the slewing scroll is operated to rotate slowly in this manner, back pressure is not generated, leading to a problem where the scroll rotates at an unstable angle. In other words, the compression efficiency was reduced due to this unstable behavior, making it impossible to achieve the desired compression performance.

[0008] Accordingly, a structure is provided in which the eccentric portion of the rotation axis is formed to extend to a height between the pivoting laps at the center of the pivoting scroll, as described in the prior art Japanese Patent Publication No. JP 08-326671, Registered Patent No. 10-252594, and Registered Patent No. 10-2056371. In other words, the operational stability of the pivoting scroll is ensured by a structure in which the eccentric portion is extended to overlap radially with the pivoting lap.

[0009] However, the aforementioned conventional scroll compressor had a disadvantage in that it was inevitably difficult to design the slewing wrap of the slewing scroll because the eccentric portion of the rotation shaft was formed to extend into the inner side of the slewing scroll. In other words, when forming the profile of the slewing wrap, a design had to be made that took into account the penetration portion of the eccentric portion.

[0010] In particular, as described above, since the eccentric portion is provided at the central part of the rotating scroll, there was a problem in that the compression space was reduced and the compression efficiency decreased.

[0011] The present invention was devised to solve various problems according to the aforementioned prior art.

[0012] The objective of the present invention is to prevent unstable behavior of the slewing scroll during low-speed operation of the scroll compressor, while maximizing the compression chamber.

[0013] The objective of the present invention is to prevent unstable behavior from increasing when the rotating scroll is operated at a low speed.

[0014] The objective of the present invention is to prevent the behavior of a rotating scroll from increasing even when the back pressure acting on the non-rotating scroll is small.

[0015] The objective of the present invention is to allow for more freedom in designing the turning wrap of a turning scroll while reducing the unstable behavior of the turning scroll.

[0016] According to the scroll compressor of the present invention for achieving the above-mentioned purpose, at least a portion of a rotating shaft installed in a slewing scroll to eccentrically rotate the slewing scroll is provided between the slewing wraps by penetrating the end plate portion of the slewing scroll.

[0017] According to the scroll compressor of the present invention, at least two or more eccentric parts of a rotating shaft installed on a rotating scroll to eccentrically rotate the rotating scroll are provided.

[0018] According to the scroll compressor of the present invention, a plurality of eccentric parts are formed sequentially along the axial direction of the rotation axis.

[0019] According to the scroll compressor of the present invention, the eccentric portion of the rotating shaft is provided in plurality, and each eccentric portion supports the rotation of the rotating scroll differently depending on the rotational speed or back pressure of the rotating scroll.

[0020] According to the scroll compressor of the present invention, the eccentric portion of the rotating shaft may include a first eccentric portion for supporting the load of the rotating scroll when it rotates above the reference speed of the rotating scroll. As a result, when the rotating scroll operates at the reference speed, accurate rotational operation can be performed by the first eccentric portion.

[0021] According to the scroll compressor of the present invention, the eccentric portion of the rotating shaft may include a second eccentric portion to reduce the unstable behavior of the rotating scroll when the rotating scroll rotates at a speed lower than the reference speed. This enables the rotating scroll to be supported even if back pressure sufficient to cause the rotating wrap of the rotating scroll to contact the end plate portion of the non-rotating scroll is not provided.

[0022] According to the scroll compressor of the present invention, the eccentric portion of the rotating shaft may include a first eccentric portion installed on the rotating end plate portion of the rotating scroll.

[0023] According to the scroll compressor of the present invention, the eccentric portion of the rotating shaft may include a second eccentric portion positioned between the rotating laps by penetrating the rotating plate portion.

[0024] According to the scroll compressor of the present invention, a shaft insertion part into which a second eccentric part is inserted may be provided between the swivel wraps of the swivel scroll. Due to the shaft insertion part, the second eccentric part does not affect the compression space where the refrigerant is compressed.

[0025] According to the scroll compressor of the present invention, a boss protrudes from the pivot plate portion, and a first eccentric portion of the rotation shaft is inserted into the boss.

[0026] According to the scroll compressor of the present invention, the first eccentric portion can be installed so as to be recessed from the boss of the rotating scroll to a portion of the thickness of the rotating plate portion.

[0027] According to the scroll compressor of the present invention, the second eccentric portion may be formed to protrude to a height such that the rotating scroll does not tilt.

[0028] According to the scroll compressor of the present invention, the second eccentric portion can be formed to protrude to a height of at least 1 / 2 of the height of the slewing wrap. This prevents the problem of the slewing scroll behaving unstably while operating at a low speed.

[0029] According to the scroll compressor of the present invention, the second eccentric part may be formed with an outer diameter smaller than that of the first eccentric part. This minimizes the problem of the design of the swivel wrap being limited by the second eccentric part. In other words, the reduction of the compression space caused by the second eccentric part can be minimized.

[0030] According to the scroll compressor of the present invention, the second eccentric portion can be formed lower than the first eccentric portion. This minimizes the reduction of the compression space caused by the second eccentric portion.

[0031] According to the scroll compressor of the present invention, a bearing may be provided around the circumference of the eccentric portion. By means of such a bearing, the slewing scroll can be rotated stably.

[0032] According to the scroll compressor of the present invention, the gap between the first bearing and the first eccentric part can be formed to be smaller than the gap between the second bearing and the second eccentric part. Thus, when the slewing scroll rotates above a reference speed, the first bearing can support the load of the slewing scroll.

[0033] According to the scroll compressor of the present invention, the gap between the second bearing and the second eccentric part can be formed to be larger than the gap between the first bearing and the first eccentric part. This allows the second bearing to reduce the unstable behavior of the slewing scroll when the slewing scroll rotates slower than the reference speed.

[0034] According to the scroll compressor of the present invention, the turning radius of the first bearing can be formed to be larger than the turning radius of the second bearing. This allows the first bearing to support the load of the turning scroll when the turning scroll rotates above a reference speed.

[0035] According to the scroll compressor of the present invention, the turning radius of the second bearing can be formed to be smaller than the turning radius of the first bearing. This allows the second bearing to reduce the unstable behavior of the turning scroll when the turning scroll rotates at a speed below a reference speed.

[0036] According to the scroll compressor of the present invention, the turning radius of the first eccentric part can be formed to be larger than the turning radius of the second eccentric part. Thus, when the turning scroll rotates above a reference speed, the first eccentric part can support the load of the turning scroll.

[0037] According to the scroll compressor of the present invention, the turning radius of the second eccentric part can be formed to be smaller than the turning radius of the first eccentric part. This allows the second eccentric part to reduce the unstable behavior of the turning scroll when the turning scroll rotates at a speed below a reference speed.

[0038] According to the scroll compressor of the present invention, a slide bush may be further provided in the first eccentric portion of the rotating shaft. Thereby, the first eccentric portion to which the slide bush is applied supports the rotation of the rotating scroll during constant speed or high speed operation of the rotating scroll.

[0039] According to the scroll compressor of the present invention, the eccentric portion of the rotating shaft may include a first eccentric portion for supporting the load of the rotating scroll when rotating above the reference speed of the rotating scroll, and a second eccentric portion for reducing the unstable behavior of the rotating scroll when the rotating scroll rotates at a speed lower than the reference speed.

[0040] The scroll compressor of the present invention as described above provides the following effects.

[0041] The scroll compressor of the present invention can prevent unstable behavior of the rotating scroll during low-speed operation by providing an additional second eccentric part, while maximizing the compression chamber.

[0042] In addition, the scroll compressor of the present invention supports the load of the slewing scroll during constant speed or high speed operation by the first eccentric part, and prevents unstable behavior of the slewing scroll during low speed operation by the second eccentric part.

[0043] In addition, the scroll compressor of the present invention has a small back pressure acting on the non-swivel scroll, so even if the swivel scroll receives a turning moment, the second eccentric part prevents the unstable behavior of the swivel scroll from increasing.

[0044] In addition, the scroll compressor of the present invention has a second eccentric part having a minimum diameter that prevents unstable behavior of the slewing scroll without causing damage, so the design of the slewing wrap can be made more freely.

[0045] FIG. 1 is a cross-sectional view schematically showing the internal structure of a compressor according to an embodiment of the present invention.

[0046] FIG. 2 is an enlarged view of a key part illustrating the relationship between the compression section and the rotating shaft of a compressor according to an embodiment of the present invention.

[0047] Figure 3 is an enlarged view of section “A” in Figure 2.

[0048] FIG. 4 is a cross-sectional view showing a swivel scroll of a compressor according to an embodiment of the present invention.

[0049] FIG. 5 is a perspective view showing the rotating shaft of a compressor according to an embodiment of the present invention.

[0050] FIG. 6 is a plan view showing the rotation axis of a compressor according to an embodiment of the present invention.

[0051] FIG. 7 is a front view showing the rotating shaft of a compressor according to an embodiment of the present invention.

[0052] FIG. 8 is a side view showing the rotating shaft of a compressor according to an embodiment of the present invention.

[0053] FIG. 9 is a cross-sectional view showing the rotating shaft of a compressor according to an embodiment of the present invention.

[0054] FIG. 10 is an enlarged view of a key part showing a portion of the rotating scroll of a compressor according to an example of another form of the present invention.

[0055] FIG. 11 is a perspective view of the rotating shaft of a compressor according to another example of another form of the present invention.

[0056] Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. It should be noted that in assigning reference numerals to the components of each drawing, the same components are given the same reference numeral whenever possible, even if they are shown in different drawings. Furthermore, in describing the embodiments of the present invention, if it is determined that a detailed description of related known components or functions would hinder understanding of the embodiments of the present invention, such detailed description is omitted.

[0057] In describing the components of the embodiments of the present invention, terms such as first, second, A, B, (a), (b), etc., may be used. These terms are intended only to distinguish the components from other components, and the essence, order, or sequence of the components is not limited by the terms. Where it is stated that a component is "connected," "combined," or "connected" to another component, it should be understood that the component may be directly connected or connected to the other component, but that another component may also be "connected," "combined," or "connected" between each component.

[0058] The scroll compressor of the present invention is designed to maximize the compression space while preventing unstable behavior of the rotating scroll during low-speed operation of the scroll compressor.

[0059] Attached FIGS. 1 to 9, FIGS. 10, and FIGS. 11 illustrate respective embodiments of the scroll compressor of the present invention.

[0060] As illustrated in these drawings, the scroll compressor of the embodiment of the present invention includes a case (100), a motor unit (200), a compression unit (300), and a rotating shaft (500). In particular, the rotating shaft (500) includes a structure that supports the load of the swivel scroll (310) during constant speed operation of the scroll compressor and a structure that prevents unstable behavior of the swivel scroll (310) during low speed operation of the scroll compressor.

[0061] The scroll compressor of the embodiment of the present invention will be described in more detail for each component as follows.

[0062] First, the above case (100) will be described with reference to FIG. 1.

[0063] The above case (100) can be defined as the exterior of a scroll compressor.

[0064] The above case (100) is formed to have a sealed internal space.

[0065] The above case (100) can be formed by combining at least one or more parts.

[0066] A refrigerant suction pipe (140) and a refrigerant discharge pipe (150) can be connected to the above case (100).

[0067] The above refrigerant suction pipe (140) is a conduit that receives refrigerant from an external device and sucks it into the case (100). When the scroll compressor of the embodiment of the present invention is connected to a refrigeration cycle, the external device supplying refrigerant to the scroll compressor may be an evaporative heat exchanger.

[0068] The above refrigerant suction pipe (140) can be installed to penetrate the case (100). That is, refrigerant can be introduced into the suction space inside the case (100) through the refrigerant suction pipe (140).

[0069] The above refrigerant discharge pipe (150) is a conduit that discharges refrigerant gas compressed in the compression section (300) to an external device. When the scroll compressor of the embodiment of the present invention is connected to a refrigeration cycle, the external device to which refrigerant is supplied from the scroll compressor may be a condensation heat exchanger.

[0070] The above refrigerant discharge pipe (150) can be installed to penetrate the case (100). That is, the refrigerant present in the discharge space within the case (100) can be guided to an external device through the refrigerant discharge pipe (150).

[0071] Next, the electric motor (200) will be described with reference to FIG. 1.

[0072] The above-mentioned electric motor (200) may be defined as a part, structure, or device that provides driving force for the operation of the compression unit (300) to be described later.

[0073] The above-mentioned electric motor (200) may be provided in any one of the internal spaces of the case (100). For example, as illustrated, the electric motor (200) may be provided in the lower space within the case (100).

[0074] The above electric motor (200) includes a rotor (210) and a stator (220).

[0075] The rotor (210) is positioned inside the stator (220) and rotates by power supply to the stator (220).

[0076] Next, the compression part (300) will be described with reference to FIGS. 1 to 4.

[0077] The above compression unit (300) can be defined as a structure, part, or device that compresses the refrigerant.

[0078] The above compression unit (300) may be provided in the space within the internal space of the case (100) where the refrigerant is sucked in. For example, as illustrated, the compression unit (300) may be provided in the upper space within the case (100).

[0079] The above compression unit (300) includes a rotating scroll (310) and a non-rotating scroll (320) arranged to face each other vertically. For example, the compression unit (300) can be provided with the rotating scroll (310) positioned on the lower side and the non-rotating scroll (320) positioned on the upper side.

[0080] The above-mentioned rotating scroll (310) has a rotating plate section (311) and a rotating wrap (312).

[0081] The upper surface of the above-mentioned pivot plate section (311) (the surface facing the non-pivoting scroll) is formed as a flat plane. The above-mentioned pivot lap (312) is formed to protrude from the upper surface of the above-mentioned pivot plate section (311).

[0082] The above non-rotating scroll (320) has a non-rotating plate section (321) and a non-rotating wrap (322).

[0083] The bottom surface (the surface facing the rotating scroll) of the above-mentioned non-rotating plate section (321) is formed as a flat plane. The above-mentioned non-rotating wrap (322) is formed to protrude from the bottom surface of the above-mentioned non-rotating plate section (321).

[0084] The end surfaces of the above-mentioned rotating wrap (312) and non-rotating wrap (322) come into contact with the end plate of the opposite scroll, forming at least one compression chamber (compression space). For example, the end surface (upper surface) of the rotating wrap (312) is in close contact with the lower surface of the non-rotating end plate (321) of the non-rotating scroll (320), and the end surface (lower surface) of the non-rotating wrap (322) is in close contact with the upper surface of the rotating end plate (311) of the rotating scroll (310).

[0085] Each of the above wraps (312, 322) is formed in a spiral shape and is installed so that a specific part of the rotating wrap (312) comes into contact with a specific part of the non-rotating wrap (322) according to the rotational movement of the rotating scroll (310).

[0086] At least one of the above non-rotating scroll (320) and rotating scroll (310) can be configured to rotate relative to the other scroll.

[0087] For example, the non-rotating scroll (320) may not rotate, and only the rotating scroll (310) may rotate. The rotating scroll (310) may be installed to rotate with respect to the axis center of the non-rotating scroll (320).

[0088] Preferably, the non-rotating scroll (320) is fixedly installed on the main frame (400) within the case (100). The fixation can be defined as a state in which rotation or pivoting in the circumferential direction is prevented. For example, the non-rotating scroll (320) may be installed to move in an up-and-down direction opposite to the pivoting scroll (310), or the non-rotating scroll (320) may be installed to move radially from the axis center.

[0089] Meanwhile, the above-mentioned pivot scroll (310) is provided with an axle insertion part (313). The axle insertion part (313) may be formed to protrude from the upper surface of the pivot plate part (311).

[0090] The shaft insertion part (313) may be formed to protrude from the center of the upper surface of the pivot plate part (311). At this time, the shaft insertion part (313) is formed to have an inner diameter such that the first eccentric part (510) of the rotation shaft (500), which will be described later, does not pass through, and only the second eccentric part (520) can pass through.

[0091] The bottom surface of the shaft insertion part (313) is formed to penetrate the center of the pivoting plate part (311) and open to the bottom surface of the pivoting plate part (311). As a result, the second eccentric part (520) of the rotation shaft (500), which will be described later, can be inserted through the bottom surface of the pivoting plate part (311).

[0092] The shaft insertion portion (313) is formed to have a height of at least 1 / 2 of the height of the pivoting wrap formed on the upper surface of the pivoting plate portion (311). This enables the second eccentric portion (520) of the pivot shaft (500) to support the overturning moment provided from the circumferential direction of the compression chamber.

[0093] A recessed groove (314) is formed in the above-mentioned pivot scroll (310). The recessed groove (314) may be formed to be recessed from the bottom surface of the above-mentioned pivot plate portion (311).

[0094] A portion of the first eccentric part (510) of the rotation shaft (500), which will be described later, is received in the above-mentioned recess (314). That is, the first eccentric part (510) is able to support the gas force (pressure generated when the refrigerant is compressed) provided in the radial direction of the above-mentioned pivot plate part (311) by the above-mentioned recess (314).

[0095] A boss (315) may be further formed on the bottom surface of the above-mentioned pivot plate portion (311). The boss (315) may be formed to have a height sufficient to accommodate the first eccentric portion (510) of the rotation axis (500) while protruding from the bottom surface of the above-mentioned pivot scroll (310).

[0096] Next, the rotation axis (500) will be described with reference to FIGS. 2 and 3 and FIGS. 5 through 9.

[0097] The above-mentioned rotating shaft (500) can be defined as a structure for transmitting the driving force of the electric motor (200) to the compression unit (300).

[0098] The above-mentioned rotating shaft (500) is installed to penetrate the central portion of the stator (220), with its upper end connected to the compression portion (300) and its lower end located in the lower space within the case (100).

[0099] The rotor (210) is installed around the rotation axis (500). Thus, the rotation axis (500) can be rotated together with the rotor (210) by supplying power to the stator (220).

[0100] The axis center of the rotation axis (500) is installed to be concentric with the center of the non-rotating scroll (320) and eccentric with respect to the center of the rotating scroll (310). As a result, the rotating scroll (310) can rotate relative to the center of the non-rotating scroll (320) to form a compression chamber between each lap (312, 322).

[0101] An eccentric portion (510, 520) is provided at the end of the rotation axis (500) so that the above-mentioned pivot scroll (310) pivots around the center of the above-mentioned non-pivot scroll (320).

[0102] These eccentric parts (510, 520) are formed to have an axial center that is eccentric with respect to the axial center of the rotation axis (500). That is, by additionally forming the eccentric parts (510, 520) on the rotation axis (500) and installing them on the pivot scroll (310), the pivot scroll (310) rotates eccentrically with respect to the axial center of the rotation axis (500) due to the rotation of the rotation axis (500).

[0103] Meanwhile, in an embodiment of the present invention, the eccentric portions (510, 520) are formed in multiple numbers along the axial direction of the rotation axis (500).

[0104] In particular, one of the above eccentric parts (510, 520) may be configured to support the load of the swivel scroll (310) during constant speed or high speed operation of the scroll compressor, and the other may be configured to prevent unstable behavior of the swivel scroll (310) during low speed operation of the scroll compressor.

[0105] To this end, the eccentric portions (510, 520) include a first eccentric portion (510) inserted into the boss (315) of the pivot scroll (310), and a second eccentric portion (520) that extends from the first eccentric portion (510), penetrates the pivot plate portion (311) of the pivot scroll (310), and is inserted into the shaft insertion portion (313).

[0106] The first eccentric part (510) above acts to support the load of the rotating scroll (310) during constant speed or high speed operation of the scroll compressor.

[0107] The above second eccentric part (520) prevents unstable behavior of the rotating scroll (310) during low-speed operation of the scroll compressor.

[0108] The first eccentric portion (510) is formed to have a diameter sufficient to support the load of the rotary scroll (310). That is, the first eccentric portion (510) is formed to have a surface pressure sufficient to support the load of the rotary scroll (310) during the rotary operation of the rotary scroll (310).

[0109] In contrast, the second eccentric part (520) is formed with a smaller outer diameter than the first eccentric part (510). That is, by minimizing the outer diameter of the second eccentric part (520), unstable behavior of the rotating scroll (310) can be prevented, while minimizing the disadvantage of the compression chamber being reduced by the second eccentric part (520).

[0110] The second eccentric portion (520) can be formed with a length up to a height such that the pivoting scroll (310) is not tilted by the gas force provided from the radial direction.

[0111] This length can be approximately 1 / 2 or more of the height of the swivel wrap (312).

[0112] If the height of the second eccentric part (520) is excessively high, the space for designing the compression space is reduced, so excellent compression efficiency cannot be obtained. Considering this, it is most desirable to form the second eccentric part (520) only up to the center of the compression chamber (compression space).

[0113] Depending on the design of the compression chamber, the second eccentric part (520) may be formed with a length (height) less than or equal to half the height of the pivot wrap (312). However, in this case, there is a concern that unstable behavior of the pivot scroll (310) may occur.

[0114] Considering this, if the second eccentric part (520) is formed with a length (height) less than or equal to half the height of the pivot wrap (312), the outer diameter of the second eccentric part (520) can be formed to be less than half the outer diameter of the first eccentric part (510). That is, the height of the second eccentric part (520) is increased to prevent unstable movement, while the diameter of the second eccentric part (520) is reduced to maximize the compression space. In particular, as the outer diameter of the second eccentric part (520) is reduced, the problem of the design of the pivot wrap (312) being limited by the second eccentric part (520) can be resolved.

[0115] Of course, if the outer diameter of the second eccentric part (520) is excessively small, a problem may arise where the rotating scroll (310) cannot be stably supported even when rotated at a low speed. In addition, if rotated at a high speed, there is a risk that the second eccentric part (520) may be damaged by the centrifugal force applied to the second eccentric part (520). Considering this, it is preferable that the diameter of the second eccentric part (520) be formed to be approximately half the diameter of the first eccentric part (510).

[0116] The second eccentric portion (520) can be formed lower than the first eccentric portion (510). This prevents damage to the second eccentric portion (520) even if the diameter of the second eccentric portion (520) is formed smaller. Of course, the disadvantage of the compression space being reduced by the second eccentric portion (520) can also be reduced.

[0117] Meanwhile, the first eccentric portion (510) may be formed to have a diameter such that it does not penetrate the through hole (316) formed in the pivoting plate portion (311). Thus, the first eccentric portion (510) can support the load of the pivoting scroll (310) while acting to support the pivoting plate portion (311) and the lower portion of the pivoting plate portion (311).

[0118] In particular, a portion of the first eccentric part (510) is installed to be received in a recessed groove (314) formed in the pivoting plate part (311). As a result, the first eccentric part (510) can support the gas force provided in the radial direction of the pivoting plate part (311).

[0119] The operation of the scroll compressor according to each situation of the embodiment of the present invention is described below.

[0120] The scroll compressor of the embodiment of the present invention is a compressor provided to the outdoor unit of an air conditioner, and an example is given in which a plurality of indoor units are connected to such a single outdoor unit.

[0121] First, when the indoor units of each room are operated together, as in a typical summer season, the scroll compressor supplied to the outdoor unit operates at a predetermined constant speed or at a high speed. For example, constant speed operation is performed when a preset number of indoor units are in operation, and high speed operation is performed when more than a preset number of indoor units are in operation.

[0122] Thus, when the scroll compressor is operated at a constant speed or high speed and the slewing scroll (310) is rotated at high speed, back pressure is generated, and due to this back pressure, the wraps (312, 322) of each scroll (310, 320) are pressed against the end plate (311, 321) of the opposing scroll. As a result, the compression chamber (compression space) created between each wrap (312, 322) compresses the refrigerant gas while maintaining a sealed state from the external environment.

[0123] As described above, while refrigerant compression is being performed in the compression chamber, the rotating scroll (310) is pressurized by the non-rotating scroll (320), thereby providing an excessive axial load to the rotating scroll (310). However, the axial load provided to the rotating scroll (310) is supported by the first eccentric part (510) inserted into the rotating end plate (311) of the rotating scroll (310). At the same time, the first eccentric part (510) also supports the centrifugal force generated according to the rotational movement of the rotating scroll (310).

[0124] In addition, the second eccentric part (520), which is inserted up to the shaft insertion part (313) of the pivot scroll (310), supports the gas force generated in the radial direction of the compression chamber when the refrigerant gas is compressed. Thus, the first eccentric part (510) and the second eccentric part (520) perform not only the function of pivoting the pivot scroll (310) but also the function of supporting the load provided in the axial and radial directions during the pivoting operation of the pivot scroll (310).

[0125] Meanwhile, the scroll compressor operates at a low speed when fewer than a preset number of indoor units are in operation among multiple indoor units, or when operation requiring only a minimum load is performed.

[0126] In particular, when operation is performed with the aforementioned minimum load, the pressure generated within the compression chamber becomes insufficient compared to the pressure provided as back pressure.

[0127] In this case, if the back pressure is insufficient, the wrap (312, 322) and the end plate (311, 321) of each scroll (310, 320) cannot be in close contact with each other, and as a result, unstable behavior occurs in which the rotating scroll (310) tilts and attempts to rotate.

[0128] However, the second eccentric portion (520) provided on the inner side of the pivot wrap (312) of the pivot scroll (310) prevents the pivot scroll (310) from tilting. This prevents unstable behavior even when the pivot scroll (310) rotates slowly.

[0129] Ultimately, the scroll compressor of the present invention can prevent unstable behavior of the rotating scroll during low-speed operation by providing an additional second eccentric part (520), while maximizing the compression chamber.

[0130] In addition, the scroll compressor of the present invention supports the load of the rotating scroll (310) during constant speed operation or high speed operation by the first eccentric part (510), and prevents unstable behavior of the rotating scroll (310) during low speed operation by the second eccentric part (520).

[0131] In addition, the scroll compressor of the present invention has a small back pressure acting on the non-swivel scroll (320), so even if the swivel scroll (310) receives a turning moment, the second eccentric part (520) prevents the unstable behavior of the swivel scroll (310) from increasing.

[0132] In addition, the scroll compressor of the present invention has a second eccentric part (520) that has a minimum diameter that prevents unstable movement of the swivel scroll (310) without damage, so the design of the swivel wrap can be made more freely.

[0133] Meanwhile, the scroll compressor of the present invention can be implemented in various forms different from the aforementioned embodiments. These are explained for each embodiment as follows.

[0134] As an example according to another form of the scroll compressor of the present invention, bearings (610, 620) may be provided in the shaft insertion part (313) and the boss (315) of the slewing scroll (310), respectively, as shown in FIG. 10.

[0135] That is, a bearing (610, 620) supporting each eccentric part (510, 520) inserted into the shaft insertion part (313) and the boss (315) may be provided. By doing so, each eccentric part (510, 520) can more smoothly perform the function of supporting the load on the slewing scroll (310) and preventing unstable behavior while being supported by the bearing (610, 620).

[0136] The above bearings (610, 620) may include a first bearing (610) inserted and installed within the boss (315) and a second bearing (620) inserted and installed within the shaft insertion part (313). Each of the above bearings (610, 620) may be fixed by being pressed into the boss (315) and the shaft insertion part (313), respectively. Thus, the first bearing (610) supports the rotation of the first eccentric part (510), and the second bearing (620) supports the rotation of the second eccentric part (520).

[0137] In particular, the two bearings (610, 620) may be formed to have different sizes and different gaps. For example, the first bearing (610) may be larger than the second bearing (620), and the gap between the first bearing (610) and the first eccentric part (510) may be formed to be smaller than the gap between the second bearing (620) and the second eccentric part (520).

[0138] By forming the gap of the first bearing (610) small in this way, the first bearing (610) can support a large load (load of the slewing scroll), and by forming the gap of the second bearing (620) large, it is possible to reduce the unstable behavior of the slewing scroll (310) even under low load conditions.

[0139] Additionally, the turning radius of the first bearing (610) may be formed to be larger than the turning radius of the second bearing (620). For example, the turning radius of the first bearing (610) may be designed to be 0.01 to 0.02 mm larger than the turning radius of the second bearing (620). That is, with respect to the turning radius (ε), if the first bearing (610) is designed to be ε ± 0.005 mm, the second bearing (620) may be designed to be (ε - 0.01 to 0.02) ± 0.005 mm.

[0140] Thus, when the slewing scroll (310) is operated at a speed above a reference speed (e.g., 30 Hz or higher), the first bearing (610) can support the load of the slewing scroll (310), and when the slewing scroll (310) is rotated at a speed below a reference speed, the second bearing (620) can reduce the unstable behavior of the slewing scroll (310).

[0141] Of course, instead of forming the rotational radii of each bearing (610, 620) differently, the rotational radii of each eccentric part (510, 520) may be formed differently. For example, the rotational radius of the first eccentric part (510) may be formed larger than the rotational radius of the second eccentric part (520).

[0142] As another example according to a different form of the scroll compressor of the present invention, as shown in FIG. 11, a slide bush (630) may be provided in the first eccentric portion (510) of the rotating shaft (500).

[0143] At least one first planar portion (511) is formed on the outer surface of the first eccentric portion (510), and a second planar portion (631) on which the first planar portion (511) slides is formed on the inner surface of the slide bush (630).

[0144] These slide bushes (630) do not operate during low-speed operation of the scroll compressor, but operate by centrifugal force when operated at a speed above the reference speed. That is, during low-speed and low-load operation, unstable behavior of the slewing scroll (310) is prevented by the action of the second eccentric part (or second bearing) (520) having a fixed radius, and during constant speed or high-speed operation, the slide bushes (630) operate and the load of the slewing scroll (310) is supported by the action of the first eccentric part (or first bearing) (510).

[0145] Thus, the roles of the two eccentric parts (or two bearings) (510, 520) can be clearly distinguished and operated.

[0146] As such, the scroll compressor of the present invention can be implemented in various forms.

[0147] In the foregoing, although all components constituting an embodiment according to the present invention have been described as being combined or operating in combination, the present invention is not necessarily limited to such embodiments. That is, within the scope of the purpose of the present invention, all such components may be selectively combined in one or more ways to operate. Furthermore, terms such as "include," "constitute," or "have" described above, unless specifically stated otherwise, mean that the relevant component may be inherent; thus, they should be interpreted as allowing for the inclusion of additional components rather than excluding other components. All terms, including technical or scientific terms, have the same meaning as generally understood by those skilled in the art to which the present invention pertains, unless otherwise defined. Terms commonly used, such as those defined in advance, should be interpreted in accordance with their meaning in the context of the relevant technology and, unless explicitly defined in the present invention, should not be interpreted in an ideal or overly formal sense.

[0148] The foregoing description is merely an illustrative explanation of the technical concept of the present invention, and those skilled in the art to which the present invention pertains will be able to make various modifications and variations within the scope of the essential characteristics of the present invention. Accordingly, the embodiments disclosed in the present invention are intended to explain, not limit, the technical concept of the present invention, and the scope of the technical concept of the present invention is not limited by these embodiments. The scope of protection of the present invention shall be interpreted by the claims below, and all technical concepts within an equivalent scope shall be interpreted as being included within the scope of rights of the present invention.

Claims

1. A rotating scroll having a rotating plate section and a rotating wrap protruding from one surface of the rotating plate section; A non-rotating scroll having a non-rotating plate section facing the above-mentioned rotating plate section, and a non-rotating wrap protruding from one side of the above-mentioned non-rotating plate section and forming a compression chamber together with the above-mentioned rotating wrap; A rotating shaft comprising a first eccentric portion eccentric with respect to the axis center and a second eccentric portion extending axially from the first eccentric portion and penetrating the pivoting plate portion; One side of the above-mentioned pivot plate is provided with a shaft insertion part into which a second eccentric part penetrating from the other side of the above-mentioned pivot plate is inserted. A scroll compressor having a boss formed on the other side of the above-mentioned rotating plate portion to accommodate the above-mentioned first eccentric portion.

2. In Paragraph 1, A scroll compressor formed such that the shaft insertion portion has a height of at least 1 / 2 of the height of the pivoting wrap formed on one surface of the pivoting plate portion.

3. In Paragraph 1, A scroll compressor in which the second eccentric part is formed with a smaller outer diameter than the first eccentric part.

4. In Paragraph 1, A scroll compressor having a recessed groove formed on the other side of the above-mentioned pivot plate portion, in which the first eccentric portion is partially accommodated.

5. In Paragraph 4, The above-mentioned recess is a scroll compressor in which the first eccentric portion is recessed to a depth such that it does not penetrate the pivoting plate portion.

6. In Paragraph 1, A first bearing inserted into a first eccentric portion is provided within the above boss, and A scroll compressor in which a second bearing inserted into a second eccentric part is provided within the shaft insertion part.

7. In Paragraph 6, A scroll compressor in which the gap between the first bearing and the first eccentric part is formed to be smaller than the gap between the second bearing and the second eccentric part.

8. In Paragraph 6, A scroll compressor in which the turning radius of the first bearing is formed to be larger than the turning radius of the second bearing.

9. A rotating scroll having a rotating plate section and a rotating wrap protruding from one surface of the rotating plate section; A non-rotating scroll comprising a non-rotating plate section positioned facing the above-mentioned rotating plate section, and a non-rotating wrap protruding from one surface of the above-mentioned non-rotating plate section and forming a compression chamber together with the above-mentioned rotating wrap; A rotating shaft having an eccentric portion eccentric from the axis center; comprising, A scroll compressor in which the eccentric portions of the above-mentioned rotating shaft are formed in multiple numbers along the axial direction and coupled to the above-mentioned pivoting scroll.

10. In Paragraph 9, The above eccentric part is, A first eccentric portion located in the pivot plate portion of the above-mentioned pivot scroll, and A scroll compressor including a second eccentric portion positioned between the pivoting laps and penetrating the above-mentioned pivoting plate portion.

11. In Paragraph 10, A scroll compressor having a shaft insertion portion into which the second eccentric portion is inserted between the pivot laps of the above-mentioned pivot scroll.

12. In Paragraph 10, A scroll compressor having a boss formed protrudingly on the opposite side of the above-mentioned rotating plate section, into which the first eccentric part is inserted, on the side opposite to the one side equipped with the rotating wrap.

13. In Paragraph 12, A scroll compressor in which the first eccentric portion is installed to be recessed past the boss to a portion of the thickness of the pivoting plate portion.

14. In Paragraph 10, A scroll compressor formed such that the second eccentric portion protrudes to a height of at least 1 / 2 of the height of the pivot wrap.

15. In Paragraph 10, A scroll compressor in which the second eccentric part is formed with a smaller outer diameter than the first eccentric part.

16. In Paragraph 10, A scroll compressor in which the second eccentric portion is formed to be lower in height than the first eccentric portion.

17. In Paragraph 10, A scroll compressor having a first bearing provided around the circumference of the first eccentric portion and a second bearing provided around the circumference of the second eccentric portion.

18. In Paragraph 17, A scroll compressor in which the gap between the first bearing and the first eccentric part is formed to be smaller than the gap between the second bearing and the second eccentric part.

19. In Paragraph 10, A scroll compressor in which the turning radius of the first eccentric part is formed to be larger than the turning radius of the second eccentric part.

20. In Paragraph 10, At least one first planar portion is formed on the outer surface of the first eccentric portion, and A scroll compressor having a slide bushing having a second planar portion on which the first planar portion slides, provided around the circumference of the first eccentric portion.

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