KR102367895B1 - Rotary compressor - Google Patents

Abstract

This application relates to a compressor configured to accurately orient vanes. The present application relates to a cylinder: a chamber formed in the cylinder and configured to receive a predetermined working fluid; a rotor rotatably received within the chamber and disposed eccentrically in the chamber; first and second bearings respectively disposed above and below the cylinder to close the chamber and configured to support a drive shaft of the rotor; a plurality of vanes movably installed in the rotor in a radial direction thereof and configured to protrude from the rotor to divide the chamber into a plurality of compression spaces; and first and second bearings formed on the chamber-facing surfaces of the first and second bearings to receive a portion of the vanes, for guiding the vanes to continuously protrude to the inner circumferential surface of the cylinder while the rotor rotates. A rotary compressor including a second guide groove is provided.

Description

Rotary Compressor

The present application relates to a rotary compressor, and more particularly, to a rotary compressor including a rotating vane.

In general, a compressor is a machine that increases the pressure of the working fluid by receiving power from a power generating device such as an electric motor or a turbine and applying compression work to a working fluid such as air or a refrigerant. Such compressors are widely used in air conditioners and refrigerators, that is, from small devices such as household appliances to large devices such as oil refineries and chemical plants.

Such a compressor may be classified into a positive displacement compressor and a turbo compressor (dynamic compressor or turbo compressor) according to a compression method. Among them, a positive displacement compressor is widely used in industry, and has a compression method that increases the pressure by reducing the volume. The positive displacement compressor may be further classified into a reciprocating compressor and a rotary compressor according to a compression mechanism.

The reciprocating compressor compresses a working fluid by means of a piston reciprocating linearly inside a cylinder, and has the advantage of producing high compression efficiency with relatively simple mechanical elements. However, the reciprocating compressor has a limitation in rotational speed due to the inertia of the piston, and has a disadvantage in that significant vibration occurs due to the inertial force. On the other hand, the rotary compressor compresses the working fluid by the rotor rotating inside the cylinder, and can produce high compression efficiency at a low speed compared to the reciprocating compressor. Accordingly, the rotary compressor has the advantage of generating less vibration and noise, and has recently been used more widely than the reciprocating type, particularly in home appliances. Such a rotary compressor is disposed in a cylinder and is divided into a fixed vane type compressor and a rotating vane type compressor according to the operation method of a vane that divides the inner space of the cylinder into variable subspaces (ie, compression space). can The fixed vane type compressor includes a rotor rotating eccentrically along an inner circumferential surface of a cylinder, and vanes disposed in a stationary state between the cylinder and the rotor. In addition, the rotating vane type compressor includes a rotor rotating in a cylinder and a vane rotating together with the rotor between the inner circumferential surface of the cylinder and the rotor.

In such a rotating vane type compressor, the vane is configured to form a variable compression space in the cylinder. Therefore, if the vane does not have the correct orientation at the correct position, leakage of the working fluid may occur between the cylinder and the vane, precisely between the cylinder inner circumferential surface and the end of the vane facing the same. especially. As the vanes rotate with the rotor at high speeds, the correct placement and orientation of the vanes can be even more important to the reliability and stability of the compressor. In addition, although the vane is under a harsh operating environment such as continuous high-speed rotation, it does not have a structure and shape having high strength and rigidity. Therefore, in order to secure the reliability and stability of the compressor, it is necessary to consider the structural stability and reliability of the vane.

In this regard, Japanese Patent Registration JP5660919 discloses a rotary compressor configured to position the vanes relatively accurately with respect to the rotor and the cylinder. However, since the rotary compressor of Japanese Patent Registration JP5660919 uses many members such as a vane guide and a vane bush for guiding the vanes, it causes an increase in production cost and a decrease in productivity. In addition, Japanese Patent Registration JP5660919 does not specifically consider the structural stability of the vane itself.

The present application has been devised to solve the above-described problem, and an object of the present application is to provide a rotary compressor configured to accurately orient the vanes while having a simple structure.

Another object of the present invention is to provide a rotary compressor having a structurally stable and reliable vane.

The present application provides a guide structure of a vane having a simple structure in order to solve the above-mentioned problems. Since the guide mechanism is implemented through simple mechanical structures such as slots and grooves, it can be formed by simple mechanical processing, and the number of parts is not increased. In addition, this guiding mechanism can accurately orient the vanes without failure or breakage due to its simple structure. Further, the guide mechanism may be configured to space the end of the vane out of contact with the inner circumferential surface of the cylinder. Accordingly, loss of power of the vane, vibration/noise, and wear and damage can also be prevented.

In addition, the present application provides an optimally designed shape of the vane. Due to this shape, a large load is not applied to the vane during rotation, and thus wear and damage can be prevented.

The present application as described above, in more detail, a cylinder: a chamber formed in the cylinder and configured to receive a predetermined working fluid; a rotor rotatably received within the chamber and disposed eccentrically in the chamber; first and second bearings respectively disposed above and below the cylinder to close the chamber and configured to support a drive shaft of the rotor; a plurality of vanes movably installed in the rotor in a radial direction thereof and configured to protrude from the rotor to divide the chamber into a plurality of compression spaces; and first and second bearings formed on the chamber-facing surfaces of the first and second bearings to receive a portion of the vanes, for guiding the vanes to continuously protrude to the inner circumferential surface of the cylinder while the rotor rotates. It is possible to provide a rotary compressor including a second guide groove.

The vanes may be configured to be oriented toward a center of the rotor, and a longitudinal centerline of the vanes may be configured to pass through the center of the rotor.

The rotor may include a slot extending a predetermined length radially inward from an outer periphery thereof and configured to movably receive the vane therein. The longitudinal centerline of the slot may be configured to pass through the center of the rotor. In addition, both sides of the slot may be configured to be in close contact with both sides of the vane.

The end portion of the vane may be configured not to contact the inner peripheral surface of the cylinder as a whole, and a gap of a predetermined size may be formed between the end of the vane and the inner peripheral portion of the cylinder. The gap may be set to 10 μm to 20 μm.

The first and second guide grooves may be formed concentrically with the chamber, and a distance from an inner circumference of each of the first and second guide grooves to an inner circumference of the cylinder may be greater than a length of the vane. .

The vane may include: a body extending radially long of the rotor and including a first end disposed in the rotor and a second end adjacent to an inner circumferential surface of the cylinder; and pins extending from the first end of the body and inserted into the first and second guide grooves. The pin may be formed integrally with the body or may be detachably installed on the body. In addition, the pin may have a diameter corresponding to the distance between the inner and outer circumferences of each of the first and second guide grooves.

The end of the vane may be configured to have a predetermined curvature. The vane may include a first side portion positioned on the rotational direction side of the rotor and a second side portion opposite to the first side portion, and the first side portion may be shorter than the second side portion.

The compressor according to the present application includes only a slot of a rotor and a guide groove of a bearing as a guide mechanism of a vane. Such a guide mechanism can be formed by simple mechanical machining, and does not increase the number of parts. Accordingly, this guide mechanism has a simple structure and can be easily provided to the compressor by a simple process. In addition, the guiding mechanism can accurately orient and move the vanes towards the center of the rotor and cylinder during operation of the compressor. For this reason, the guiding mechanism can increase the productivity of the compressor while also bringing reliability and stability of operation. In addition, since the guide mechanism separates the end of the vane from contact with the inner circumferential surface of the cylinder while preventing leakage, loss of power, vibration/noise, and wear and damage of the vane can also be prevented. Accordingly, reliability and stability as well as efficiency of the compressor can be improved.

Furthermore, the ends and sides of the vane are designed to have an optimal shape, and thus the load applied to the pin of the vane can be greatly reduced. Accordingly, wear and breakage of the vanes can also be significantly reduced. Such an optimal design design can greatly increase the structural stability and reliability of the vane, and accordingly, the stability and reliability of the compressor itself.

1 is a partial cross-sectional view showing a rotary compressor according to the present application.
2 is an exploded perspective view showing the compression unit of the rotary compressor according to the present application.
3 is a plan view showing the compression unit from which the upper bearing is removed.
4 is a perspective view illustrating an assembly of a lower bearing and a vane.
5 is a perspective view showing the vane in detail.
6 is a schematic diagram showing in detail the geometrical relationship between the chamber, the guide groove and the vane.
7 is a partial plan view showing the shape of the vane in detail.
8 is a plan view showing the operation of the rotary compressor according to the present application in stages.

Examples of the rotary compressor according to the present application are described in detail below with reference to the accompanying drawings.

In the description of these examples, the same or similar components are assigned the same reference numerals regardless of reference numerals, and overlapping descriptions thereof will be omitted. The suffixes "module" and "part" for components used in the following description are given or mixed in consideration of only the ease of writing the specification, and do not have distinct meanings or roles by themselves. In addition, in describing the embodiments disclosed in the present specification, if it is determined that detailed descriptions of related known technologies may obscure the gist of the embodiments disclosed in this specification, the detailed description thereof will be omitted. In addition, the accompanying drawings are only for easy understanding of the examples disclosed in this specification, and the technical idea disclosed herein is not limited by the accompanying drawings, and all changes included in the spirit and scope of the present application, It should be understood to include equivalents and substitutes.

Terms including an ordinal number, such as first, second, etc., may be used to describe various elements, but the elements are not limited by the terms. The above terms are used only for the purpose of distinguishing one component from another.

When a component is referred to as being “connected” or “connected” to another component, it may be directly connected or connected to the other component, but it is understood that other components may exist in between. it should be On the other hand, when it is said that a certain element is "directly connected" or "directly connected" to another element, it should be understood that the other element does not exist in the middle.

The singular expression includes the plural expression unless the context clearly dictates otherwise.

In this application, terms such as "comprise", "comprises" or "have" are intended to designate that a feature, number, step, operation, component, part, or combination thereof described in the specification exists. , it should be understood that it does not preclude the possibility of addition or existence of one or more other features or numbers, steps, operations, components, parts, or combinations thereof. In addition, for the same reason, the present application also provides some features from combinations of related features, numbers, steps, operations, components, and parts described using the above-mentioned terms without departing from the intended technical purpose and effect of the disclosed invention. It should also be understood that combinations in which numbers, steps, actions, components, parts, etc. are omitted are also encompassed.

Examples described in this application relate to a rotary compressor comprising a vane that rotates with a rotor. However, the principles and configuration of the examples described may be applied without substantial modification to any type of apparatus having a vane moving without substantial modification.

First, the overall configuration of an example of a rotary compressor according to the present application will be described below with reference to the related drawings. In this regard, FIG. 1 is a partial cross-sectional view showing a rotary compressor according to the present application.

Referring to FIG. 1 , the rotary compressor 1 according to the present application may include a case 2 , a power unit 10 and a compression unit 100 positioned inside the case 1 . In FIG. 1 , the power unit 10 is located above the compressor 1 , and the compression unit 100 is located below the compressor 1 , but their positions may be interchanged as needed. An upper cap 3 and a lower cap 5 are installed at the upper and lower portions of the case 2, respectively, to form a sealed inner space. The suction pipe 7 is installed on the side of the case 1 and can suck a working fluid such as a refrigerant or air from the outside of the compressor 1 . Also, an accumulator 8 may be connected to the suction pipe 7 to separate lubricants and other foreign substances from the working fluid. A discharge pipe 9 through which the compressed working fluid is discharged may be installed at the center of the upper cap 3 . Also, the lower cap 5 may be filled with a certain amount of lubricating oil 0 for lubrication and cooling of the moving member.

The power unit 10 may be formed of any power device capable of supplying power required for the rotary compressor 1 . Among these power devices, as an example, the power unit 10 may be formed of an electric motor that generates power with high efficiency while being compact. More specifically, the power unit 10 includes a stator 11 fixed to the case 2 , a rotor 12 rotatably supported inside the stator 11 , and a drive shaft coupled to the rotor 12 . (13) may be included. The rotor 12 is rotated by the stator 11 and electromagnetic force generated by the rotor 12 , and the driving shaft 13 transmits the rotational force of the rotor 12 to the compression unit 100 . In order to supply external power to the stator 11 , a terminal 4 may be installed in the upper cap 3 .

The compression unit 100 compresses the working fluid to have a predetermined pressure, and may be configured to discharge the compressed working fluid. For such compression of the working fluid, the compression unit 100 may be connected to the suction pipe 7 to receive the working fluid to be compressed, as shown in FIG. 1 . Also, the compression unit 100 may communicate with the discharge pipe 9 to discharge the compressed working fluid. That is, as shown, the compressed working fluid is discharged from the extrusion unit 100 to the inner space of the sealed case 2 , and then may be discharged to the outside of the case 2 through the discharge pipe 9 . On the other hand, like the suction pipe 7 , the discharge pipe 9 may be directly connected to the compression unit 100 . In addition, the compression unit 100 may be connected to the power unit 10 by the drive shaft 13 to receive the rotational force required for compression. Since the compression unit 100 includes parts moving at high speed by the power of the power unit 10 , it can be firmly fixed in the case 2 . Such a compression unit 100 will be described in more detail below with reference to the related drawings.

2 is an exploded perspective view showing the compression unit of the rotary compressor according to the present application. 3 is a plan view showing the compression unit from which the upper bearing is removed, and FIG. 4 is a perspective view showing the assembly of the lower bearing and the vane. 5 is a perspective view showing the vane in detail. 6 is a schematic diagram showing in detail the geometric relationship between the chamber, the guide groove and the vane, and FIG. 7 is a partial plan view showing the shape of the vane in detail. Finally, Figure 8 is a plan view showing the operation of the rotary compressor according to the present application in stages.

The top view of Fig. 3 shows the assembly of the cylinder, rotor, lower bearing, and vane with the upper bearing removed to better show the inside of the cylinder, and Figs. 7 and 8 include plan views of the same assembly for the same purpose. Also, Fig. 3 shows the chamber eccentric in the y-axis in plan view whereas Fig. 6 shows the chamber eccentric in the x-axis to better show the geometrical relationship of the parts, in these figures the relative arrangement of the parts is substantially the same Do.

First, the compression unit 100 may include a cylinder 110 disposed in the case (2). The cylinder 110 may generally have a ring-shaped body 111 having a predetermined thickness, and, if necessary, may have a body of another shape. The cylinder 110 may include a chamber 112 of a predetermined size formed in the body 111 . The chamber 112 may form a working space for accommodating a working fluid for compression. The cylinder 110 is formed in the body 111 and may include an inlet 113 and an outlet 114 communicating with the chamber 112 . The suction port 113 is connected to the suction pipe 7 to supply the working fluid into the chamber 112 , and the discharge port 114 may communicate with the discharge pipe 9 for discharging the compressed working fluid. Such inlet 113 and outlet 114 may be disposed in the body 111 spaced apart from each other at a predetermined angle and spacing for the smooth suction and discharge of the working fluid that does not interfere with each other. In addition, as shown in FIG. 3 , the cylinder 110 has a recess formed around the inlet 113 and the outlet 114 on its inner circumferential surface (to be precise, the inner circumferential surface of the body 111 ) forming the chamber 112 . (recess) or dimples (dimple) (113a, 114a) may be included. These recesses (113a, 114a) prevent the vortex of the working fluid due to the rapid suction and discharge of the working fluid, and thus the working fluid can be smoothly sucked and discharged. In addition, the size of the chamber 112 is substantially expanded by the recesses 113a and 114a, so that a larger amount of the working fluid can be smoothly sucked and discharged. In such a cylinder 110 , the chamber 112 may be arranged radially eccentrically to the cylinder 110 , as best shown in FIG. 3 . That is, the center C of the chamber 112 may be radially spaced apart from the center O of the cylinder 110 at a predetermined interval. This arrangement is for the cylinder 110 to form a variable compression space together with other members of the compression unit 100, which will be described in more detail later.

The compression unit 100 may also include a rotor 120 rotatably accommodated in the chamber 112 of the cylinder 110 . The rotor 120 may have a body 121 having a circular cross-section, ie in the form of a disk, as best shown in FIGS. 2 and 3 . In addition, the rotor 120 has a through hole 121a disposed in the central portion of the body 121 thereof, and the drive shaft 13 of the power unit 10 may be press-fitted into the through hole 121a. Accordingly, the rotor 120 may rotate about its central axis, that is, the driving shaft 13 by the power provided from the power unit 10 in the chamber 112 of the cylinder 110 . In addition, as shown in FIG. 3 , the rotor 120 may be eccentrically disposed in the chamber 112 . Accordingly, the rotor 120 may be disposed concentrically with the cylinder 112 eccentric to the chamber 112 . That is, the rotor 120 may share the same center O with the cylinder 110 or may have a different center O from the cylinder 110 , and this center O is the center C of the chamber 112 . may be spaced apart from each other in a radial direction at predetermined intervals. In addition, the center O of the rotor 120 is disposed on the central axis of the drive shaft 13 , and thus can rotate in the chamber 112 without eccentricity by the drive shaft 13 . With such an arrangement, the rotor 120 is disposed at the radial end of the chamber 112 , as well shown in FIG. 3 , so that the outer periphery of the rotor 120 is the outer periphery of the chamber 112 , that is, It may be disposed adjacent to the inner peripheral surface or the inner peripheral portion of the cylinder body (111). Therefore, a space having a cross-section or volume varying along the circumferential direction of the cylinder 112 or chamber 112 is formed between the outer periphery of the rotor 120 and the chamber 112 opposite to the outer periphery of the adjacent to each other, and Therefore, this space can be used as a compression space to receive and compress the working fluid.

Further, the compression unit 100 may include a bearing 130 disposed in the cylinder 110 and configured to close the chamber 112 of the interior 110 thereof. The bearing 130 is disposed on the lower and upper (ie, bottom and top surfaces) of the cylinder 110 precisely of its body 111 , respectively, first and second configured to cover the chamber 112 . It may include bearings 130a and 130b. In order to prevent leakage of the working fluid compressed to a high pressure in the chamber 112, the bearings 130: 130a, 130b are the body 111 of the cylinder 110. ) can be firmly coupled using a fastening member In addition, the bearings 130: 130a, 130b may be configured to support the drive shaft 13 coupled to the rotor 120. More specifically, the bearing (130: 130a, 130b) may include sleeves 132 surrounding the driving shaft 13, as shown in Fig. 2. The sleeve 132 of the first bearing 130a is the rotor 130. A portion of the lower drive shaft 13 is supported, and the sleeve 132 of the second bearing 130b may support a portion of the upper drive shaft 13 of the rotor 130. Therefore, With such sleeves 132 , the rotor 120 can rotate stably at high speed in the cylinder 110 .

Also, the compression unit 100 may include a plurality of vanes 140 provided to the rotor 120 . As an example, as shown in FIGS. 3 and 4 , the compression unit 100 may include 1-3 vanes 140a, 140b, and 140c, and if necessary, fewer or more vanes. may include 140 . The vanes 140:140a-140c may extend radially from the rotor 120 and be spaced apart from each other at equal intervals and angles, for example at intervals of 120° as shown, and may have the same radial lengths. . As shown in FIG. 3 , the vanes 140 are eccentric to the remaining space of the chamber 112 (ie, the chamber 112 ) except for the space occupied by the rotor 120 in the chamber 112 . It is disposed in the space between the outer periphery of the rotor 120 and the outer periphery of the chamber 112 (hereinafter, the effective space of the chamber 112), and the effective space is used for compression of the working fluid in a plurality of compression spaces. That is, the vanes 140 may divide the effective space while extending across the effective space of the chamber 112 from the outer periphery of the rotor 120. Also, as discussed above, , the effective space may have a volume and a cross-section that change along the circumferential direction of the cylinder 110. Therefore, as shown, between the vanes 140 dividing the effective space in the radial direction, compression of different volumes Spaces can be formed In addition, each compression space between these vanes 140 is moved in the circumferential direction of the cylinder 110 while the vanes 140 rotate together with the rotor 120 . That is, the vanes 140 divide the chamber 112 in the cylinder 110, that is, the effective space, so that the rotor 120 or the vanes 140 are variable during rotation. That is, it is possible to form a plurality of compression spaces that are continuously changed during such rotation, and each of these variable compression spaces independently sucks the working fluid using its changed volume during rotation of the rotor 120, Compression and discharge, and this series of operations will be described later in more detail with reference to the related drawings.

On the other hand, these compression spaces need to be properly sealed in order to compress the working fluid at a high pressure. Accordingly, for proper sealing, the vanes 140 need to reach the outer periphery of the chamber 112 from the rotor 120 , that is, the inner periphery (or inner circumferential surface) of the body 111 of the cylinder 110 . As mentioned above, since the rotor 120 is relatively eccentric to the chamber 112, as well shown in FIG. 3, one point of the rotor 120 and the inner periphery of the cylinder 110 (that is, the chamber ( The distance between the outer periphery of 112) may be continuously changed while the rotor 120 rotates. Accordingly, the vane 140 disposed at one point of the rotor 120 changes to reach the inner periphery of the cylinder 110, and the distance between the one point of the rotor 120 and the inner periphery of the cylinder 110 changes. Correspondingly, it may be configured to protrude from the rotor 120 at different distances.

In order to enable such movement of the vanes 140 during rotation of the rotor 120, the rotor 120 may first include slots 122 corresponding to the vanes 140: 140a-140c as a guide mechanism. can As shown in FIGS. 2 and 3, the slot 122 may extend a predetermined length radially inward from the outer periphery of the body 121 of the rotor 120, and the vane 130 may be accommodated therein. can Accordingly, the length of the slot 122 may determine the minimum protrusion length of the vane 140 . As described above, due to the relative eccentricity of the rotor 120 with respect to the chamber 112 , the outer periphery of the rotor 120 is partially on the outer periphery of the chamber 112 , that is, the inner periphery of the body 111 of the cylinder 110 . Since it is adjacent, when the vane 140 protrudes greatly, it may interfere with the cylinder 110 . Accordingly, the length of the slot 122 , actually the radial length, may be set so that such interference does not occur, for example, may be set to be substantially equal to the length of the vane 140 .

In addition, if the vane 140 is disposed at the correct position as designed and is not oriented correctly, leakage of the working fluid may occur between the inner periphery of the cylinder 110 and the end of the vane 140 facing it. . More specifically, if the vane 140 is not accurately oriented along the radial direction of the rotor 140, that is, the cylinder 110 and is tilted at a predetermined angle with respect to the radial direction, such a vane 140 ) can be tilted with respect to the inner periphery of the cylinder 110 as well, and a large gap is formed between the end of the tilted vane 140 and the inner periphery of the cylinder 110 to cause leakage. For this reason, the slot 122 may be configured to be oriented toward the center O of the cylinder 110 or rotor 120 . That is, the slot 122 extends along the radial direction of the cylinder 110 , and the longitudinal centerline of the slot 122 may pass through the center O of the cylinder 110 or the rotor 120 . In addition, as shown in FIG. 3 , both side portions 122a and 122b of the slot 122 may be configured to be in close contact with the side surfaces of the vane 140 so that a gap is not generated. In addition, both side portions 122a and 122b of the slot 122 may extend parallel to the centerline of the vane 140 or its own centerline so as to be advantageously in close contact with the side surfaces of the vane 140 having a certain thickness or width. there is. Precisely, since the side portions 122a and 122b of the slot 122 are relatively formed by the rotor 120, it will also be described that the rotor 120 itself is formed in close contact with and parallel to the side surfaces of the vane 120. Therefore, by such a slot 122, the vane 140 can be accurately oriented toward the center O of the cylinder 140 along the radial direction of the cylinder 140, and That is, the longitudinal centerline of the vane 140 may also pass through the center O of the cylinder 110 or rotor 120 by the slot 122. For this reason, the slot 122 is 140 can move in the radial direction of the cylinder 110 to accurately guide it to protrude from the rotor 120 to the inner periphery of the cylinder 110. By the configuration of the slot 122 as described above, the vane 140 By being accurately oriented to face the center O of the rotor 120, it is possible to form a compression space without leakage without creating a large gap with respect to the inner circumferential surface of the cylinder 110, and compression of the working fluid is performed stably and reliably can be

In addition, during the rotation of the rotor 120 , in order for the vanes 140 to reach the inner periphery of the cylinder 110 , an appropriate driving force applies the vanes 140 to the change in the distance between the rotor 120 and the cylinder 110 . It needs to be applied to the vane 140 to move it significantly. In order to apply such a driving force, the compression unit 100 may include a guide groove 150 as an additional guide mechanism. The guide groove 150 may be configured to receive a portion of each vane 140 to basically guide the movement of the vane 140 as shown in FIGS. 2 - 4 and 6 . The guide groove 150 accommodates a part of the vane 140 while not interfering with the compression in the chamber 112 and other components of the compression unit 100, and the bearing ( 130) may be formed on the surface. In order to guide the movement of the vane 140 stably, the guide groove 150 includes first and second guide grooves 150a and 150b respectively formed in the first and second bearings 130a and 130b. It can be, and accordingly, it is possible to accommodate the portions disposed on the upper and lower portions of the vane 140, respectively. The guide groove 150 may be continuously extended over the entire circumferential direction while having a ring shape, that is, having a certain radius, and thus actually guide the entire rotational movement of the vane 140 according to the rotation of the rotor 120 . can

In addition, as shown in FIGS. 3 and 6 , the guide groove 150 is eccentric with the rotor 120 but concentric with the chamber 121 , that is, to be disposed to share the same center C with the chamber 121 . can That is, the guide groove 150 can maintain a constant distance D in the radial direction with respect to the outer periphery of the chamber 112 , that is, the inner periphery of the cylinder 110 , and this distance D is generally the vane 140 . It can be set equal to the radial length (L) of . More precisely, as shown in FIG. 6 , since the vane 140 may occupy the entire radial length of the guide groove 150 , the inner circumferential surface of the cylinder 110 from the inner peripheral portion 151 of the guide groove 150 . The distance (D) to the can be set equal to the radial length (L) of the vane (140). By this configuration, as shown in FIG. 3 , the vane 140 is constrained by the guide groove 150 while the rotor 120 rotates and the cylinder 110 along the guide groove 150 . ), it can rotate continuously while reaching the inner periphery. That is, the guide groove 150 may apply a force to the vane 140 to move relative to the rotor 120 eccentric to the chamber 112 by restraining the vane 140 . Accordingly, the vane 140 is guided by the slot 122 from the eccentric rotor 120, and reciprocates in the radial direction, and continuously maintains the state reached to the inner periphery of the cylinder 110 by this relative reciprocating motion. can be maintained as For this reason, the guide groove 150 may be configured to continuously guide the vanes 140 to protrude from the rotor 120 to the inner periphery of the cylinder 110 while the rotor 120 rotates, and accordingly, the chamber A plurality of closed compression spaces can be formed in the 112 .

On the other hand, when the length L of the vane 140 is set equal to the distance D, the end of the vane 140 may contact the inner circumferential surface of the cylinder 110 . The compression space formed by this contact can be completely sealed, but various unfavorable effects can also arise therefrom. For example, power loss may occur due to friction between the vane 140 and the cylinder 110 , and noise may be generated while the vane 140 vibrates. In addition, since the vane 140 rotates at a high speed, wear and damage due to friction may also occur. That is, the vane 140 configured to contact the inner circumferential surface of the cylinder 110 may bring about mechanical loss and reduced stability/reliability. In this regard, as described above, the guide groove 150 is formed concentrically with the chamber 112 to maintain a fixed distance between the outer periphery of the guide groove 150 and the outer periphery of the chamber 112 . Therefore, the distance between the end of the vane 140 constrained to the guide groove 150 and the inner periphery of the cylinder 110 can be adjusted similarly by adjusting the fixed distance. Therefore, by adjusting the distance between the guide groove 150 and the outer periphery of the chamber 112, the end of the vane 140 can be configured to reach the inner periphery of the cylinder 110, but not directly contact. More specifically, the distance D from the inner peripheral portion 151 of the guide groove 150 to the inner peripheral surface of the cylinder 110 may be formed to be longer than the radial length L of the vane 140 . Precisely, the vane 140 may have a length L that is shorter than the distance D, and thus the end of the vane 140 may be configured not to contact the inner circumferential surface of the cylinder 110 as a whole. Accordingly, a clearance having a predetermined size may be formed between the end of the vane 140 and the inner circumferential surface of the cylinder 110 . When such a gap is formed large, since leakage of the working fluid is generated, the gap can be formed finely. For example, the gap may be set to 10 μm - 20 μm. The end of the vane 140 forms only a very fine gap up to the inner circumferential surface of the cylinder 110 , and this gap may be sufficiently filled by an oil film applied to the inner circumferential surface of the cylinder 110 . Thus, the vane 140, precisely its end, does not cause a substantial leakage of the working fluid, and can eliminate ancillary effects that may be caused by contact with the inner periphery of the cylinder 110 as described above. . For this reason, the vane 140 can increase the efficiency of the compressor 1 by removing the mechanical loss, and also improve the stability and reliability of the compressor 1 .

More specifically, with reference to FIGS. 5, 6 and 7 , the vane 140 is also advantageously and effectively compressed to be guided by the guiding mechanism as described above, that is, the slot 122 and the guiding groove 150 . You can have a configuration that can perform

First, to be advantageously guided by the slots 122 of the rotor 120 , each vane 140 may include a body 141 elongated radially of the rotor 120 . . As shown, the body 141 may have a rectangular prism shape with a thin thickness, and may have any other shape if necessary. Such a body 141 includes a first end portion 141a disposed in the rotor 120 so as not to be separated from the rotor 120 and a second end portion protruding from the rotor 120 and adjacent to the inner periphery of the cylinder 110 . It may include two end portions (141b). As described above, the second end portion 141b may be configured to form a predetermined fine gap with respect to the inner circumferential surface of the cylinder 110 without contacting the entire inner circumferential surface.

Also, the vane 140 may include a pin 142 extending vertically from the first end 141 of the body 141 toward the adjacent guide groove 150 . The pin 142 may be inserted into the guide groove 150 to guide the rotation of the vane 140 . That is, the pin 142 may include first and second pins 142a and 142b respectively inserted into the first and second guide grooves 150a and 150b. The first pin 142a extends downward from the bottom surface of the body 141 by a predetermined length so as to be inserted into the first and second guide grooves 150a and 150b, respectively, and the second pin 142b includes the body ( 141) may extend upward by a predetermined length from the upper surface. In addition, as shown in Fig. 7 as well as Fig. 3, the slot 122 is also formed at the inner end of the rotor 120, that is, the closed end, and is configured to stably receive the pins 142: 142a, 142b. It may include a seat 122c. Since the pin 142 moves along the guide groove 150 during rotation of the rotor 120 , the vane 140 can rotate stably without being separated from the guide groove 150 .

More specifically, the pins 142:142a, 142b may be integrally formed with the body 141, and high structural strength may be secured. On the other hand, the pins 142: 142a, 142b may be detachably coupled to the body 141, and may be replaced with other pins when wear and tear are derived. Also, referring to FIG. 6 , the diameter r of the pin 142 may be set to correspond to the distance between the inner periphery 151 and the outer periphery 152 of the guide groove 150 . Accordingly, the pin 142 can be stably supported by both the inner peripheral portion 151 and the outer peripheral portion 152 during rotation. For this reason, the vane 140 may also rotate more stably, and the gap between the vane 140 , precisely the second end portion 141b and the inner circumferential surface of the cylinder 110 , may also be stably maintained.

In addition, as shown in FIGS. 6 and 7 , an end adjacent to the inner circumferential surface of the cylinder 110 of the vane 140 , that is, the second end 141b may be configured to have a predetermined curvature. That is, the second end 141b may have a curved surface. The curved second end 141b may form a variable gap with respect to the inner circumferential surface of the cylinder 110 . Accordingly, the second end 141b maintains a predetermined gap with respect to the inner circumferential surface of the cylinder 110, that is, it is more advantageous in avoiding contact and friction with the inner circumferential surface. More specifically, as shown in Fig. 7, the vane 140 is opposite to the first side portion 141c and the first side portion 141c located on the rotational direction side of the rotor 120 indicated by the arrow, That is, it may include a second side portion 141d that is relatively disposed opposite to the rotational direction of the rotor 120 . That is, the first side portion 141c may be disposed on the traveling direction side of the rotor 120 or the vane 140 , while the second side portion 141d may be disposed opposite to the first side portion 141c. . By adjusting the curvature or curved surface of the second end 141b described above, the first side portion 141c may be formed shorter than the second side portion 141d. A curved surface may be formed as the second end 141b between the first and second side portions 141c and 141d. In addition, the first side portion 141c, that is, the end thereof may form a first gap G1 with respect to the inner circumferential surface of the cylinder 110, and the second side portion 141d, that is, the end thereof, is the inner circumferential surface of the cylinder 110 A second gap G1 may be formed with respect to . Due to the difference in length of the first and second side portions 141c and 141d, the first and second gaps G1 and G2 are set differently from each other, and precisely, the first gap G1 is the second gap G2. can be made larger.

Since the first side portion 141c is disposed in the traveling direction of the vane 140, it can receive substantial pressure when the working fluid is substantially compressed. However, due to the configuration described above, the first side portion 141c forms a curved surface between the first and second side portions 141c and 141d, that is, a considerably extended pressing area together with the second end portion 141b. The force applied to the vane 140 by the pressure of the fluid may be relatively reduced. Accordingly, the torsion of the vane 140 and the pin 142 that may be generated by such a force can be reduced, and the vane 140, particularly the pin 142, is worn or damaged in the guide groove 150. can be prevented. In addition, since the first gap G1 is formed to be relatively large, this may result in relatively expanding the compression space and increasing the compression efficiency. In contrast, the second side portion 141d may be formed to be relatively long and may extend adjacent to the inner circumferential surface of the cylinder 110 while forming a relatively narrow second gap G2 . Accordingly, the second side portion 141d can effectively support back pressure generated from another compression space formed adjacent to the vane 140 opposite to the traveling direction thereof. For this reason, leakage of the working fluid and vibration/noise of the vane 140 can be prevented.

The curvature or curved surface of the second end 141b may be formed in various ways to determine the side portions 141c and 141d and the gaps G1 and G2. For example, the curvature of the second end 141b may be a curvature in which a center F thereof is disposed on an extension line A2 passing through the center C of the chamber 112 . The center F may be disposed to be moved in a direction B opposite to the rotation direction of the rotor 120 from the center line A1 of the vane 140 passing through the center O of the rotor 120 . The curvature along the center of curvature F may form the side portions 141c and 141d and the gaps G1 and G2 having the configuration as described above.

Such a compression unit 100 can effectively and efficiently perform compression of the working fluid in a stable and reliable manner by the cooperation of its parts, and this compression operation will be described in detail step by step below with reference to FIG. 8 . do.

First, referring to FIG. 8( a ), the first and third vanes 140a , 140b and 140c may divide the chamber 112 , precisely its effective space, into a plurality of compression spaces. That is, a first compression space 112a is formed between the first and second vanes 140a and 140b, and a second compression space 112b is formed between the second and third vanes 140b and 140c. , a third compression space 112c may be formed between the third and first vanes 140c and 140a. The compression spaces 112a, 112b, and 112c may have different sizes due to the rotor 120 being relatively eccentric to the chamber 112 . More specifically, among the vanes 140 , the first vane 140a is disposed at the point S closest to the inner periphery of the cylinder 110 , and the first compression space 112a is the current suction port 113 . It communicates with and sucks the working fluid. In the following, for clear and concise description, the compression operation of the compression unit 100 will be described in relation to the first vane 140a and the first compression space 112a.

In the state of FIG. 8( a ), when the first vane 140a starts to rotate clockwise, the first compression space 112a gradually expands and continuously sucks more working fluid through the suction port 113 . can do. As shown in FIG. 8(b), when the first vane 140a rotates at 90° from the starting point S, the first compression space 112a is greatly expanded to suck a sufficient working fluid, and the first vane A 140a may pass through the suction port 113 to isolate the suction port 113 from the first compression space 112a. When the first vane 140a continues to rotate clockwise through 180° to 270° in the state of FIG. 8(b), the first compression space 112a is shown in FIGS. 8(c) and 8(d). As described above, as it is gradually reduced again, it is possible to compress the working fluid therein. In the state of FIG. 8(d), the first compression space 112a communicates with the outlet 114 to start discharging the compressed working fluid to the outside. When the first vane 140a is further rotated clockwise in the state of FIG. 8( d ), the first compression space 112a is gradually reduced further, and more compressed working fluid is continuously supplied through the outlet 114 . As shown in FIG. 8( a ), when the first vane 140a rotates up to 360°, one cycle consisting of suction-compression-discharge ends. After the end of this cycle, the same cycle may be repeatedly performed by the continuous rotation of the rotor 120 . Also, the same cycles may be simultaneously performed in the second and third compression spaces 112b and 112c, and may be repeated as well.

As described above, since the guide mechanism of the vane 140 consists only of the slot 122 and the guide groove 150, it can be formed by simple mechanical processing and does not increase the number of parts. Accordingly, this guide mechanism has a simple structure and can be easily provided to the compressor 1 by a simple process. Further, the guiding mechanism can accurately orient and move the vane 100 in the radial direction of the cylinder 110 during operation of the compression unit 100 . For this reason, the guiding mechanism can increase the productivity of the compressor 1 while also bringing reliability and stability of operation. In addition, the guide mechanism separates the end of the vane 140 from the inner circumferential surface of the cylinder 110 while preventing leakage, so that the loss of power, vibration / noise, and wear and damage of the vane 140 can also be prevented. . Accordingly, not only the efficiency of the compressor 1 but also the reliability and stability can be improved. Furthermore, the vane 140, precisely its end 141b and sides 141c, 141d, is optimally formed to reduce the load applied to the pin 142 of the vane 140, so that the Wear and breakage due to friction can also be significantly reduced. Structural stability and reliability of the vane 140 may also be increased in size.

The above detailed description should not be construed as restrictive in all respects and should be considered as exemplary. The scope of the present application should be determined by a reasonable interpretation of the appended claims, and all modifications within the equivalent scope of the present application are included in the scope of the present application.

1: Compressor 10: Power unit
100: compression unit 110: cylinder
120: rotor 130: bearing
140: vane 150: information home

Claims (15)

cylinder;
a chamber formed in the cylinder and configured to receive a predetermined working fluid;
a rotor rotatably received within the chamber and disposed eccentrically in the chamber;
first and second bearings respectively disposed above and below the cylinder to close the chamber and configured to support a drive shaft of the rotor;
a plurality of vanes movably installed in the rotor in a radial direction thereof and configured to protrude from the rotor to divide the chamber into a plurality of compression spaces; and
first and second bearings formed on the chamber-facing surfaces of the first and second bearings to receive a portion of the vanes, and for guiding the vanes to continuously protrude to the inner circumferential surface of the cylinder while the rotor rotates 2 including a guide groove;
The first and second guide grooves are formed concentrically with the center of the chamber, and the distance from the inner circumference of each of the first and second guide grooves to the inner circumference of the cylinder is greater than the radial length of the vane. formed,
The end of the vane is configured to have a predetermined curvature,
The vane includes a first end disposed in the rotor so as not to be separated from the rotor and a second end protruding from the rotor and adjacent to the inner periphery of the cylinder,
The second end of the curvature has a curvature whose center is disposed on an extension line passing through the center of the chamber. The method of claim 1,
The vanes are configured to be oriented toward the center of the rotor. The method of claim 1,
The longitudinal centerline of the vanes is configured to pass through the center of the rotor. The method of claim 1,
and wherein the rotor extends a predetermined length radially inward from an outer periphery thereof and includes a slot configured to movably receive the vane therein. 5. The method of claim 4,
The longitudinal centerline of the slot is configured to pass through the center of the rotor. 5. The method of claim 4,
The both sides of the slot are configured to be in close contact with both sides of the vane. The method of claim 1,
The end of the vane is configured not to contact the inner circumferential surface of the cylinder as a whole. The method of claim 1,
A rotary compressor in which a gap of a predetermined size is formed between the end of the vane and the inner periphery of the cylinder. 9. The method of claim 8,
The gap is set to 10㎛-20㎛ rotary compressor. delete The method of claim 1,
The vanes are:
a body extending in a radial direction of the rotor and including a first end disposed in the rotor and a second end adjacent to an inner circumferential surface of the cylinder; and
and pins extending from the first end of the body and inserted into the first and second guide grooves. 12. The method of claim 11,
The pin is formed integrally with the body or a rotary compressor that is detachably installed on the body. 12. The method of claim 11,
The pin has a diameter corresponding to the distance between the inner periphery and the outer periphery of each of the first and second guide grooves. delete The method of claim 1,
The vane includes a first side portion positioned on the rotational direction side of the rotor and a second side portion opposite the first side portion,
The rotary compressor wherein the first side is formed shorter than the second side.

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