KR20020069920A - Vane for compressor - Google Patents

Abstract

PURPOSE: A structure of a vane of a compressor is provided to improve compression efficiency by minimizing the leakage of gas from a high pressure part to a low pressure part. CONSTITUTION: Vanes(60,61) contacting the corrugated surface formed along an inner curve and an outer curve of a parting plate have a specific thickness. A parting plate contacting curve has a specific curvature. A gap formed between a contact point of a curve and the parting plate and a front end point is removed by the face-to-face contacting of an axially contacting curve(R4) of the vane and the outer surface of a rotating shaft. Therefore, the leakage of gas to a low pressure part through the gap is minimized.

Description

Vane structure of the compressor {VANE FOR COMPRESSOR}

The present invention relates to the vane structure of the compressor, and in particular, the pressure between the vane and the partition plate to compress the gas while moving up and down in accordance with the rotation of the partition plate to contact the radially located in the rotating partition plate receiving the driving force of the electric mechanism. It relates to the vane structure of a compressor to minimize leakage.

Generally, a compressor is a machine that compresses a fluid. Such a compressor is composed of an airtight container having a predetermined internal space, an electric mechanism part mounted in the airtight container and generating a driving force, and a compression mechanism part for compressing gas by receiving the driving force of the electric mechanism part. According to different types.

One type of the compressor has been filed by the applicant of the present application (Korean Patent No. 99-42381) with a compressor having a compression method different from that of conventional compressors. 1, 2, and 3 illustrate a compressor mechanism for compressing refrigerant gas by receiving a driving force of an electric mechanism part from a compressor previously filed by the applicant of the present application. As shown in FIG. And the rotation shaft 20 so as to penetrate through the center of the inner space V of the cylinder assembly 10 having the suction passage 11 and the discharge passage 12 in communication with the internal space V, respectively. ) Is inserted and the rotary shaft 20 is coupled to the electric motor unit (M) for generating a driving force. In addition, the partition plate 30 for dividing the internal space V of the cylinder assembly 10 into the first and second spaces 13 and 14 is integral to the rotation shaft 20 so as to be located in the internal space V of the cylinder assembly. The first and second spaces 13 and 14 are respectively formed in the suction area 13a and 14a as the partition plate 30 is rotated so as to be in elastic contact with both sides of the partition plate 30 at all times. ) And moving vanes 40 and 41 moving through the compression zones 13b and 14b, respectively, are inserted into and coupled to the cylinder assembly 10. And opening and closing means 50 for discharging the compressed gas in the compression zone (13b, 14b) of the first and second spaces (13) and (14) while opening and closing the discharge passage 12 of the cylinder assembly 10, respectively Coupled to the cylinder assembly 10.

Reference numeral 1 is an airtight container, and 2 is an elastic support means.

In the operation of the compressor compression mechanism, when the rotary shaft 20 is rotated by receiving the driving force of the electric mechanism unit M, the partition plate 30 of the rotary shaft 20 is in the internal space V of the cylinder assembly 10. Will rotate. As the partition plate 30 rotates in the internal space V of the cylinder assembly 10, the first space 13 and the second space 14 are respectively formed in the suction area (V) due to the volume change of the internal space V. The refrigerant gas is sucked into each of the suction passages 11 of the first space 13 and the second space 14 while being switched to the 13a, 14a and the compression zones 13b, 14b, and compressed into a volume change. Is discharged through the discharge passage 12. At this time, the vanes 40 and 41 are linearly reciprocated in the axial direction by the partition plate 30 as the partition plate 30 rotates in an elastically supported state.

On the other hand, the partition plate 30 of the rotary shaft is formed in a circular shape having a predetermined thickness around the rotary shaft 20, the upper convex curved portion (r1) having a convex surface when viewed from the side and the lower side having a concave surface. It consists of the concave curved part r2, the convex curved part r1, and the connection curved part r3 which connects the concave curved part r2. That is, the partition plate 30 is a sinusoidal wave-shaped curved surface, the convex curved portion r1 and the concave curved portion r2 are formed to be located at a phase of 180 degrees, and the arbitrary axis around the rotating shaft 20 is arbitrary. When cut radially at the position, the cutting line of the rotary shaft 20 and the partition plate 30 is always formed at right angles. In addition, the distal end portions forming the inflection points of the convex curved portion r1 and the concave curved portion r2 of the partition plate are positioned in the inner space V while being in contact with the upper and lower surfaces of the inner space, respectively.

The first and second vanes 40 and 41 are inserted through vane slots 15 radially penetrating through the cylinder assembly 10 and positioned in the first and second spaces 13 and 14, respectively. Done. As shown in FIG. 4, the vanes 40 and 41 have a rectangular shape having a predetermined thickness, and the partition plate contact surface R1 contacting the curved surface of the partition plate 30 has a predetermined curvature. A rounding surface, that is, a curved surface having a constant curvature, is formed so that the partition plate contact surface R1 having a curved shape is in contact with the corrugated curved surface of the partition plate 30, and the sides thereof, that is, the inner wall of the inner space V of the cylinder assembly. The outer side surface R2 of the outer side surface R1 and the inner side surface F1 which is in contact with the outer circumferential surface of the rotating shaft 20 is formed as a convex curved surface to be in linear contact with the inner wall of the inner space (V) and the inner side surface F1 is formed in a plane so as to be in linear contact with the outer circumferential surface of the rotating shaft 20, and the outer surface R2 and the inner surface F1 are in contact with the inner wall of the inner space V and the outer circumferential surface of the rotating shaft 20, respectively.

In this state, as the partition plate 30 rotates, the vanes 40 and 41 linearly reciprocate vertically (in the figure) at a vertical radial position along the curved surface of the partition plate 30.

However, the conventional structure as described above, as shown in Figs. 5 and 6, the curvature of the inner curve (a) of the partition plate 30, that is, the curve where the rotating shaft 20 and the partition plate 30 meet and In contact with the corrugated surface formed along the inner curve (a) and the outer curve (b) in a state where the curvature of the inner curve (L1) and the outer curve (b) of the partition plate (30) and the outer diameter (L2) are present. Since the vanes 40 and 41 are formed to have a predetermined thickness and the partition plate contact surface R1 is formed to have a predetermined curvature, the inner surface F1 of the vanes 40 and 41 and the partition plate contact surface ( The curve where R1) meets and the contact point P1 where the partition plate 30 meets do not coincide with the longitudinal centerline tip of the vanes 40, 41 in the longitudinal direction F1, so that a gap between the contact and the tip By generating (A), the gap A between the contact point P1 and the tip point P2 leaks the gas of the high pressure portion to the low pressure portion, thereby reducing the compression performance. There is a problem.

The object of the present invention devised in view of the problems described above is a vane and a compartment for compressing the gas while moving up and down in accordance with the rotation of the partition plate is contacted to be radially located in the rotating partition plate receiving the driving force of the electric machine part It is to provide a vane structure of a compressor to minimize the gas leakage between the plates.

1,2 is a front sectional view and a plan view showing a compression mechanism of the conventional compressor;

3 is a perspective view showing a partial cross section of the compressor compression mechanism;

4 is a perspective view illustrating a vane structure and a vane slot of the compressor;

5 and 6 are a front view and a plan view showing a coupling state of the compressor vanes;

7, 8 is a front sectional view and a partial cross-sectional perspective view showing a compression mechanism of the compressor with a compressor vane of the present invention,

9 is a perspective view showing a compressor vane structure of the present invention;

10 is a perspective view showing another modification of the compressor vane structure of the present invention,

11 and 12 are a plan view showing the operating state of the compressor mechanism of the compressor equipped with vanes of the present invention, respectively;

12 and 13 are a front view and a plan view showing a coupled state of the compressor vane of the present invention.

(Explanation of symbols for the main parts of the drawing)

10; Cylinder assembly 20; Axis of rotation

30; Partition plate 60,61; Bain

F3; Plane portion R4; Shaft contact surface

R5; Cylinder contact curved portion V; Cylinder Assembly Inner Space

In order to achieve the object of the present invention as described above, a cylinder assembly having an inner space, a rotating shaft inserted into the cylinder assembly so as to pass through the inner space, and the inner space of the cylinder assembly integrally provided with the rotating shaft A compressor configured to include a partition plate rotatably inserted into a vane, and a vane for compressing gas while reciprocating in an axial direction according to the rotation of the partition plate, the compressor including a vane contacting the outer peripheral surface of the rotary shaft and its outer peripheral surface. To provide a vane structure of the compressor, characterized in that the shaft contact curved portion formed with a curved surface corresponding to the outer circumferential surface of the rotary shaft to be in surface contact with.

Hereinafter, the compressor vane structure of the present invention will be described according to the embodiment shown in the accompanying drawings.

7 and 8 illustrate a compression mechanism of a compressor provided with an example of the compressor vane structure of the present invention. Referring to this, the compression mechanism has a predetermined internal space (V) and its internal space (V). A cylinder assembly 10 having a suction passage 11 and a discharge passage (not shown) communicating with the cylinder assembly 10 and penetratingly inserted into the cylinder assembly 10 to penetrate the internal space V of the cylinder assembly 10. It is provided integrally with the rotary shaft 20 so as to be rotatable in the rotary shaft 20 and the internal space (V) of the cylinder assembly to partition the internal space (V) into first and second spaces (13) (14). Located in the partition plate 30 and the first and second spaces 13 and 14, respectively, and inserted into the cylinder assembly 10 to radially contact the partition plate 30, the partition plate 30. The first space 13 and the second space 14, respectively, while linearly reciprocating in the axial direction according to the rotation of And vanes 60 and 61 for switching to suction zones 13a and 14a and compression zones 13b and 14b. And the rotating shaft 20 is coupled to the electric drive unit. Reference numeral 1 is an airtight container, and 2 is an elastic support means.

The partition plate 30 of the rotation shaft 20 is formed in a circular shape having a predetermined thickness around the rotation shaft 20, and has an upper convex curved portion r1 having a convex surface and a concave surface when viewed from the side. It consists of the connection surface part r3 which connects the lower concave curved part r2, its convex curved part r1, and the concave curved part r2. That is, the partition plate 30 is a sinusoidal wave-shaped curved surface, the convex curved portion r1 and the concave curved portion r2 are formed to be located at a phase of 180 degrees, and the arbitrary axis around the rotating shaft 20 is arbitrary. When cut radially at the position, the cutting line of the rotary shaft 20 and the partition plate 30 is always formed at right angles. In addition, the distal ends of the convex curved portion r1 and the concave curved portion r2 of the partition plate 30 are positioned in the inner space in contact with the upper and lower surfaces of the inner space, respectively.

As shown in FIG. 9, the vanes 60 and 61 are formed in a predetermined shape, such that the contact surface contacting the outer circumferential surface of the rotating shaft 20 is in surface contact with the outer circumferential surface of the rotating shaft 20. Axial contact curved portion (R4) corresponding to the outer peripheral surface of the is provided.

When describing the vanes 60 and 61 in more detail, the vanes 60 and 61 have a vane body part B formed to have a predetermined thickness and an area of a square shape, and one of the vane body parts B. A partition plate contact curved portion R3 formed to have the same curvature on a side surface, that is, a surface in contact with the partition plate 30, and the vane body portion positioned in a direction perpendicular to the partition plate contact curved portion R3 ( An axial contact curved portion R4 formed in a concave curvature corresponding to an outer circumferential surface of the rotary shaft 20 such that one side surface of B), that is, a contact surface in contact with the rotary shaft 20, is in surface contact with the outer circumferential surface of the rotary shaft 20; A cylindrical contact curved surface formed on one side of the vane body portion (B) facing the axial contact curved portion (R4) to have a curvature corresponding to the inner wall of the inner space (V) of the cylinder assembly (10) A vane positioned to face the portion R5 and the partition plate contact curved portion R3 One side of the body portion (B) is provided with a mounting portion (F2) for mounting the elastic support means (2). The axial contact curved portion R4 is formed over the entire contact surface of the vane body portion B. And the cylinder contact curved portion (R5) is formed over the entire contact surface of the vane body portion (B).

As a modification of the contact surface of the vanes 60 and 61 in contact with the rotation shaft 20, as shown in FIG. 10, the contact surfaces of the vanes 60 and 61 in contact with the outer circumferential surface of the rotation shaft are centered therein. Is formed on both sides of the axial contact curved portion (R4) and the axial contact curved portion (R4) formed to correspond to the outer circumferential surface of the rotary shaft 20 to have a predetermined width and the surface contact with the outer circumferential surface of the rotary shaft 20 It consists of the flat part F4.

The vanes 60 and 61 are respectively inserted into vane slots 15 formed in the cylinder assembly 10 such that the partition plate contact curved portion R3 contacts the partition plate 30 and the axial contact curved surface. The portion R4 is in surface contact with the outer circumferential surface of the rotation shaft 20, and the cylinder contact curved portion R5 is in contact with the inner circumferential surface of the cylinder assembly internal space V. At this time, the vanes 60 and 61 are positioned radially to face the center of the partition plate 30 and are perpendicular to the rotation axis 20.

Meanwhile, vane slots 15 into which the vanes are inserted are formed at upper and lower surfaces of the cylinder assembly, and the vane slots 15 have a width and a predetermined interval so as to correspond to the thicknesses of the vanes 60 and 61. The inner surface is formed in the form of a through hole having a length corresponding to the length of the (60) 61, the inner surface located on the rotating shaft 20 is formed in a straight shape and located on the edge side of the cylinder assembly 10 Is formed into a curved surface corresponding to the shape of the cylinder contact surface portion R5 of the vanes 60 and 61.

Hereinafter, the operational effects of the compressor vane structure of the present invention will be described.

Compressor mechanism of the compressor when the rotary shaft 20 is rotated by receiving the driving force of the electric mechanism (M) rotates the rotary shaft 20 and the partition plate 30 of the rotary shaft 20 while the vane The inner space V of the cylinder assembly 10, that is, the first and second spaces 13 and 14, together with the 60 and 61, respectively, is continuously drawn into the suction zones 13a and 14a and the compression zone 13b. While switching to 14b, the gas sucked through the suction channel 11 is compressed and discharged through the discharge channel 12.

Referring to the above process in more detail, as shown in FIG. 11, first, the position of the first vane 60 in which the tip of the convex curved portion r1 of the partition plate 30 is located on the first space 13 side. When the tip of the concave curved portion r2 of the partition plate 30 is positioned at (a1) and is positioned at the position a1 'of the second vane 61 located in the second space 14, The first space 13 and the second space 14 are in a state where the discharge of the compressed gas is completed and the gas suction is completed. In this case, each of the first and second vanes 60 and 61 has the partition plate contact curved surface R3 at the tip end of the convex curved portion r1 and the concave curved surface r2 of the partition plate 30, respectively. As it coincides with, it is maximized out of the internal space.

Then, as shown in FIG. 12, the tip of the convex curved portion r1 of the partition plate 30 passes through the suction passage 11 of the first space 13 by the rotation of the rotation shaft 20. The vane 61 is positioned at the position a2 and at the same time the tip of the concave curved portion r2 passes through the suction passage 11 of the second space 14 to the position a2 'of the first vane 60. When positioned, the compression of the gas sucked in the first space 13 and the second space 14 proceeds with the gas being sucked. In this process, the first vane 60 and the second vane 61 each have a partition plate contacting curved portion R3 and a partial surface of the partition plate convex curved portion r1 and a connecting curved portion r3 and concave. In contact with a portion of the surface portion r2 is moved into the cylinder assembly internal space (V), respectively, by its sinusoidal curved shape. At this time, the vanes 60 and 61 are in surface contact with the axial contact curved portion R4 on the outer circumferential surface of the rotation shaft 20 and the cylinder contact curved portion R5 is in surface contact with the inner wall of the inner space V. It will move in a straight line.

Subsequently, as shown in FIG. 11, as the partition plate 30 is rotated by the rotation of the rotation shaft 20, the tip of the convex surface portion r1 is positioned on the first vane 60 and the concave curved surface at the same time. When the tip of the portion r2 is positioned in the second vane 61, the gases compressed in the first space 13 and the second space 14 are discharged, respectively, and the first space 13 and the second space are respectively discharged. The gas suction is completed in the space 14. In this process, the first vane 60 and the second vane 61 each have a partition plate contacting curved portion R3 and a partial surface of the partition plate convex curved portion r1 and a connecting curved portion r3 and concave. While being in contact with a portion of the surface portion r2, the sinusoidal wave shape is linearly moved along the outer circumferential surface of the rotating shaft 20 in the outward direction of the inner space. At this time, the vanes 60 and 61 are in surface contact with the axial contact curved portion R4 on the outer circumferential surface of the rotation shaft 20 and the cylinder contact curved portion R5 is in surface contact with the inner wall of the inner space V. It will move in a straight line.

As this process is repeated, the gas is sucked, compressed and discharged.

Meanwhile, in the process, the shaft contact curved portion R4 of the first and second vanes 60 and 61 inserted into the vane slot 15 of the cylinder assembly 10 is in surface contact with the outer circumferential surface of the rotation shaft 20. The vane 60 and 61 are partitioned into the suction space 13a and the compression zone 13b by moving up and down in the first space 13 and the second space 14 of the inner space V of the cylinder assembly. The contact between the partition plate contact curved portion R3 and the axial contact curved portion R4 of the partition plate and the partition plate does not coincide with the longitudinal center line tip of the vane axial contact curved portion R4. The gap between the tip ends minimizes the leakage of gas from the high pressure section to the low pressure section.

More specifically, as shown in FIGS. 13 and 14, the inner curve a of the partition plate 30, that is, the curvature of the curve where the rotating shaft 20 and the partition plate 30 meet and the inner diameter thereof ( Vane in contact with the corrugated curved surface formed along the inner curve (a) and the outer curve (b) in the state where the curvature of the outer curve (b) of the partition plate (30) and the partition plate (30) and the outer diameter (L2) exist. Since not only 60 and 61 are formed to have a predetermined thickness, but also the partition plate contact curved portion R3 is formed to have a predetermined curvature, the axial contact curved portion R4 and the partition plate contact curved portion R3 of the vane. The contact point P1 where the curved line c and the partition plate 30 meet each other does not coincide with the longitudinal center line tip point P2 of the axial contact curved portion R4 of the vane. A gap A occurs between the disadvantages P2, and the gap A is such that the axial contact curved portion R4 of the vane is formed with the outer circumferential surface of the rotation shaft 20. Since the contact, thereby minimizing the leakage of high pressure gas which is a low-pressure portion through the gap (A).

The cylinder contact curved portion R5 of the vane also prevents leakage of gas on the same principle.

As described above, the vane structure of the compressor according to the present invention is in contact with the partition plate of the rotating shaft rotating in the inner space of the cylinder assembly and the partition plate while receiving the driving force of the electric mechanism, and compresses the inner space with the suction region. As the gap is structurally formed by the vane for compressing the gas and the shape of the rotating shaft and the inner space of the cylinder assembly while switching to the region, the pressure of the high pressure part is minimized to the low pressure part, thereby improving the compression performance.

Claims (4)

A cylinder assembly having an inner space, a rotating shaft penetrating and inserted into the cylinder assembly to penetrate the inner space, a partition plate integrally provided with the rotating shaft and inserted into the inner space of the cylinder assembly so as to be rotatable; A compressor comprising a vane for compressing a gas while reciprocating in an axial direction as the plate rotates, the compressor comprising a vane contacting the outer circumferential surface of the rotating shaft so as to be in surface contact with the outer circumferential surface of the rotating shaft. The vane structure of the compressor, characterized in that the shaft contact curved portion formed with a curved surface. The vane structure of the compressor as claimed in claim 1, wherein the vane contact surface of the vane is formed over one side of the vane in contact with the outer circumferential surface of the rotary shaft. According to claim 1, The contact surface of the vanes in contact with the outer circumferential surface of the rotary shaft is a shaft contact curved portion and the axial contact curved surface formed to correspond to the outer circumferential curved surface of the rotary shaft so as to have a predetermined width and the surface contact with the outer circumferential surface of the rotary shaft The vane structure of the compressor, characterized in that the planar portion formed on each side of the portion. A cylinder assembly having an inner space, a rotating shaft penetrating and inserted into the cylinder assembly to penetrate the inner space, a partition plate integrally provided with the rotating shaft and inserted into the inner space of the cylinder assembly so as to be rotatable; A compressor comprising a vane for compressing a gas while reciprocating in an axial direction as the plate rotates, the compressor comprising a vane contacting the outer circumferential surface of the rotating shaft so as to be in surface contact with the outer circumferential surface of the rotating shaft. A cylindrical contact curved portion formed with a curved axial contact surface portion and the contact surface of the vane contacting the inner space inner wall of the cylinder assembly is formed with a curved surface corresponding to the curvature of the inner space inner wall. The vane structure of the compressor, characterized in that.