KR100581570B1 - A orbiting vane compressor having a linear slider - Google Patents

Abstract

The present invention relates to a swing vane compressor, and more particularly, a swing vane having a linear slider which facilitates the processing of the sealing means and improves the adhesion between the circular vane and the sealing means and at the same time makes the sealing means more stable. A compressor is provided. An annular space is formed inside a cylinder having an inner ring, and a circular vane having an opening is inserted into the annular space, and the annular space is inserted into a state in close contact with the opening to interlock with the circular vane. A swing vane compressor comprising a sealing means for sealing between a pair of compression chambers formed in a space; The sealing means is inserted between the first horizontal contact surface formed on the outer circumferential surface of the inner ring and the second horizontal contact surface formed on the inner circumferential surface of the cylinder in correspondence to the first horizontal contact surface to linearly reciprocate along the horizontal contact surface. By the configuration of the linear slider to be made, it is easy to manufacture the sealing means, the sealing force between the compression chamber is significantly increased and the performance of the compressor is improved.

Vane, Compressor, Slider, Interference, Private

Description

A orbiting vane compressor having a linear slider}

Figure 1 is a longitudinal sectional view showing the overall structure of a conventional swing vane compressor.

Figure 2 is an exploded perspective view showing the main portion of FIG.

3 is a plan sectional view showing an operating state of a conventional swing vane compressor.

Figure 4 is a plan sectional view showing a first embodiment of the present invention.

Figure 5 is a schematic plan view showing the operating state of FIG.

Figure 6 is an enlarged cross-sectional plan view of the main portion showing a second embodiment of the present invention.

Figure 7 is an enlarged cross-sectional plan view of the main portion showing a third embodiment of the present invention.

8 is an enlarged plan sectional view showing main parts of a fourth embodiment of the present invention;

9 is an enlarged cross-sectional top view showing a fifth embodiment of the present invention;

* Explanation of symbols for the main parts of the drawings

4: cylinder

   41: inner ring

      411: first horizontal contact surface

   42: annular space

      421: second horizontal contact surface 422: curved groove

5: turning vane

   51: round vane

      511: horizontal cutting surface 512: first dead bump

   53: opening

   54: sealing means

      541: linear slider 542: second dead bump

The present invention relates to a swing vane compressor, and more particularly, a swing vane having a linear slider which facilitates the processing of the sealing means and improves the adhesion between the circular vane and the sealing means and at the same time makes the sealing means more stable. Relates to a compressor.

In general, the swing vane compressor has a shape in which the driving unit D and the compression unit P are sealed in one shell 1, and the driving unit D and the compression unit P are Both upper and lower ends are interconnected to a vertical crankshaft 8 rotatably supported by the mainframe 6 and the subframe 7 so that the power of the driving unit D is compressed through the crankshaft 8. It is configured to be delivered to the side (P) side.

The driving unit D includes a stator 2 fixed between the main frame 6 and the subframe 7, and a crank shaft vertically passing through the applied power provided in the stator 2. The rotor 3 is configured to rotate 8, and the counterweight 3a is formed symmetrically with each other on the upper and lower portions of the rotor 3 to prevent the rotational imbalance of the crank shaft 8 by the crank pin 81. It is supposed to be.

The compression portion P is the inside of the cylinder 4 by the swing vane 5, the lower side boss portion 55 is coupled to the crank pin 81 to the pivoting motion inside the cylinder 4; It is configured to compress the refrigerant gas introduced into the cylinder 4, the cylinder 4 includes an inner ring 41 protruding to the lower side, the turning vane 5 is a circular vane 51 protrudes vertically on the upper side It is formed so as to make a pivoting movement in the annular space 42 formed between the inner ring 41 and the inner wall of the cylinder (4), by the pivoting movement around the inner circle vanes (51). It is configured to form a compression chamber on the outside, the refrigerant gas compressed in the compression chamber is configured to be discharged to the outside of the cylinder 4 through the inner, outer discharge port 44, 44a of the upper cylinder (4) do.

In addition, an old dam ring 9, which is a rotation preventing mechanism, is provided between the main frame 6 and the turning vane 5, and an oil supply passage 82 is formed to penetrate up and down inside the crank shaft 8. The oil supply to the compression part (P) is made by the operation of the oil pump 83 installed on the lower end of the crankshaft (8).

Here, reference numeral 11 denotes a suction tube, 12 denotes a high pressure chamber, and 13 denotes a discharge tube.

2 is an exploded perspective view illustrating the main part of FIG. 1.

As shown in the drawing, the compression part P includes a turning vane 5 coupled to the crankshaft 8 at an upper end of the main frame 6 rotatably supporting the upper side of the crankshaft 8. The cylinder 4 is coupled to the main frame 6 on the upper side of the swing vane 5, and the cylinder 4 has a suction port 43 formed in a lateral direction, and one side of an upper end surface thereof. Inner and outer ejection openings 44 and 44a are formed.

In addition, the inlet of the cylinder 4 is provided in the circular vane 51 of the turning vane 5, in which the crank pin 81 of the crankshaft 8 is coupled to the boss portion 55 formed on the lower surface of the hard plate 50. Through-hole 52 is formed so that the refrigerant gas sucked through the 43 is also sucked into the inner side of the circular vane 51, the slider 53 is formed in the opening 53 formed on one side of the circular vane 51; 54).

Here, reference numeral 9 is an Oldham ring.

3 is a plan view showing an operating state of the present invention.

As shown in the present invention, when the turning vane 5 of the compression unit P is driven by receiving power from the driving unit D through the crankshaft 8 (see FIG. 1), the cylinder 4 The circular vanes 51 of the turning vanes 5 inserted into the annular space 42 are pivoted in the annular space 42 as shown by the arrow, and the inside of the annular space 42 through the suction port 43. Compressed refrigerant gas is compressed.

That is, the initial operating state (0 °) is the suction of the refrigerant gas into the inside of the inner suction chamber (A1) through the through hole 52 of the suction port 43 and the circular vane 51, the circular vane Compression starts in the state in which the outer compression chamber B2 is blocked from the inlet 43 and the outer discharge port 44a, and the inner compression chamber A2 simultaneously compresses and discharges the refrigerant gas.

In the state rotated by 90 °, compression of the outer compression chamber B2 of the circular vane 51 is continuously in progress, and the inner compression chamber A2 of the circular vane 51 is compressed refrigerant gas through the inner discharge port 44. Discharge is almost completed, and the outer suction chamber B1, which did not exist in the previous step, is generated and suction of the refrigerant gas is carried out through the suction port 43.

In the rotated state by 180 °, the inner suction chamber A1 existing in the previous step disappears, and instead, the inner suction chamber A1 becomes the inner compression chamber A2 to start compression, and the outer compression chamber B2 ) Communicates with the outer discharge port 44a to proceed with the discharge of the compressed refrigerant gas.

In the state of rotating 270 °, the outer compression chamber B2 of the circular vane almost completely discharges the compressed refrigerant gas through the outer discharge port 44a, and the inner compression chamber A2 continues to compress the outer surface. Compression to the suction chamber (B1) is started, and when rotated further 90 degrees in the above state, the outer suction chamber (B1) that existed in the previous step becomes the outer compression chamber (B2) to the outer compression chamber (B2). By returning to the initial state while the compression is performed, the cycle based on one rotation of the crankshaft is continuously repeated.

Here, the sealing means 54 is inserted into the upper end of the circular vane 51 to maintain the sealing between the inner and outer compression chamber (A2, B2) of the circular vane 51 is composed of a slider 54a. do.

The slider 54a is in close contact with the circular vanes 51 while performing linear reciprocating motion along the inner surface of the annular space 42 while making linear contact with both upper ends formed in the arc shape of the circular vanes 51.

By the way, the above-described prior art had the following problems.

It was very difficult to process the reciprocating motion in a curved space in the annular space along the rotational motion of the circular vane in a state in which the slider as the sealing means is in close contact with the opening.

In addition, the slider, which is a sealing means, performs a curved motion while making linear contact with both ends of an arc-shaped opening of a circular vane that swings, so that the leakage length and the close contact length between the opening of the circular vane and the sealing means are short. There was a problem that the sealing force and the adhesion is significantly lowered.

In addition, a decrease in the sealing force and the adhesion between the circular openings of the circular vane and the sealing means has been a factor of deteriorating the performance of the compressor.

Accordingly, the present invention has been made to solve the conventional problems as described above, the object of the present invention is to facilitate the processing of the sealing means and to improve the adhesion between the circular vane and the sealing means at the same time the operation of the sealing means more It is to make it stable.

In addition, another object of the present invention is to prevent interference between the circular vane and the inner peripheral surface of the cylinder.

In addition, another object of the present invention is to prevent the occurrence of dead volume between the circular vane and the sealing means.

In order to achieve the object of the present invention, the present invention is an annular space is formed in the interior of the cylinder having an inner ring, a circular vane having an opening in the annular space is inserted, is inserted in close contact with the opening In the swing vane compressor is provided with a sealing means for interlocking with the circular vanes and sealing the pair of compression chambers formed in the annular space; The sealing means is inserted between the first horizontal contact surface formed on the outer circumferential surface of the inner ring and the second horizontal contact surface formed on the inner circumferential surface of the cylinder in correspondence to the first horizontal contact surface to linearly reciprocate along the horizontal contact surface. Characterized in that consisting of a linear slider to.

In addition, horizontal cutting surfaces are formed at both ends of the upper portion of the circular vanes so as to prevent interference between the circular vanes and the second horizontal contact surface.

In addition, a curved groove is formed on the inner circumferential surface of the cylinder on both sides of the second horizontal contact surface along the turning trajectories of both ends of the circular vane to prevent interference between the circular vane and the second horizontal contact surface.

In addition, a first dead volume stopper is formed at both ends of the lower end of the circular vane so as to prevent generation of a dead volume between the circular vane and the first horizontal contact surface.

In addition, a second dead volume stopper is formed on both sides of the lower side of the linear slider to prevent generation of dead volume between the circular vane and the first horizontal contact surface.

Hereinafter, a swing vane compressor having a linear slider according to the present invention will be described in detail with reference to the accompanying drawings.

4 is a plan sectional view showing a first embodiment of the present invention.

As shown in FIG. 4, the swing vane compressor of the present invention has a linear reciprocating motion in the annular space 42 of the cylinder 4 while being in close contact with the opening 53 of the circular vane 51. A sealing means 54 for sealing between the pair of compression chambers formed in 42 is provided.

The sealing means 54 is inserted between the first horizontal contact surface 411 formed on the inner ring 41 of the cylinder 4 and the second horizontal contact surface 421 formed on the inner circumferential surface of the cylinder 4. The linear slider 541 linearly reciprocates along the horizontal contact surfaces 411 and 421.

The linear slider 541 linearly reciprocates along the horizontal contact surfaces 411 and 421, so that the openings 53 of the circular vanes 51 closely adhere in a horizontal manner during the pivoting movement of the circular vanes 51. Thus, the horizontal adhesion of the opening 53 to the linear slider 541 is significantly enhanced.

As such, the horizontal contact force with the opening portion 53 is enhanced by the linear reciprocating motion of the linear slider 541, so that a pair of compression chambers are formed on the inside and the outside of the circular vane 51 on one side of the linear slider 541. Confidentiality is maintained smoothly.

In addition, since both ends of the opening 53 of the circular vane 51 are in surface contact with both sides of the linear slider 541, the leakage length and the close contact length between the two compression chambers become remarkably long, thereby both compression chambers. The sealing force and the adhesion between them are significantly enhanced.

5 is a schematic plan sectional view showing the operating state of FIG.

As shown in FIG. 5, the circular vanes 51 rotate in the annular space 42 formed between the inner circumferential surface of the cylinder 4 and the outer circumferential surface of the inner ring 41, and the inner compression chamber ( A2) and an outer compression chamber B2 are formed.

At this time, the linear slider 541 inserted in the surface contact state at both ends of the opening 53 of the circular vane 51 is interlocked with the pivoting motion of the circular vane 51 and the first horizontal contact surface 411 and the second. A linear reciprocating motion is performed horizontally along the horizontal contact surface 421.

As such, the linear slider 541 linearly reciprocates horizontally during the pivoting motion of the circular vane 51, so that both sides of the opening 53 of the circular vane 51 are continuous on both sides of the linear slider 541. Tightly and horizontally.

As described above, both ends of the opening 53 of the circular vane 51 are in close and horizontal close contact with both side surfaces of the linear slider 541 to be formed on the inside and the outside of the circular vane 51. The leakage length and the adhesion length between the inner compression chamber A2 and the outer compression chamber B2 are remarkably long, so that the airtightness between the inner compression chamber A2 and the outer compression chamber B2 is more stably maintained.

6 is an enlarged plan sectional view showing main parts of a second embodiment of the present invention.

As shown in FIG. 6, the circular vanes 51 are horizontally cut surfaces 511 at both ends of upper portions of both sides of the opening 53 so as to naturally contact the second horizontal contact surface 421 formed on the inner circumferential surface of the cylinder 4 without interference. Is formed.

The horizontal cutting surface 511 is to prevent friction and interference due to unnatural contact between the upper end of the circular vane 51 and the second horizontal contact surface 421, the circular vane 51 is the horizontal cutting surface ( The upper ends of the upper and lower surfaces of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the rotating surface.

As such, the horizontal cutting surface 511 serves to prevent friction and interference generated between the circular vane 51 and the second horizontal contact surface 421 of the cylinder 4, so that the circular vane 51 has an annular space. In the inside of the 42 is a more stable behavior, thereby making the rotational movement of the circular vane 51 more stable.

7 is an enlarged plan sectional view showing main parts of a third embodiment of the present invention.

As shown in FIG. 7, the cylinder 4 has the second horizontal contact surface along the turning trajectories of the upper ends of the circular vanes 51 to prevent interference between the circular vanes 51 and the second horizontal contact surface 421. Curved grooves 422 are formed at both sides of the 421.

The curved groove 422 is formed on the inner circumferential surface of the cylinder 4 to prevent friction and interference due to unnatural contact between the upper ends of the circular vanes 51 and the second horizontal contact surface 421. 51, the upper surface of the upper surface of the curved groove 422 during the rotational movement is a natural rotational movement without friction and interference with the second horizontal contact surface 421.

As such, the curved groove 422 serves to prevent friction and interference generated between the circular vane 51 and the second horizontal contact surface 421 of the cylinder 4, so that the circular vane 51 has an annular space. In the inside of the 42 is a more stable behavior, thereby making the rotational movement of the circular vane 51 more stable.

8 is an enlarged plan sectional view showing main parts of a fourth embodiment of the present invention.

As illustrated in FIG. 8, the circular vanes 51 have horizontal cutting surfaces 511 at both ends of the upper ends of both sides of the opening 53 so as to naturally contact the second horizontal contact surface 421 formed on the inner circumferential surface of the cylinder 4 without interference. The first dead volume stopper 512 is formed at both ends of the lower portion of both sides of the opening 53 to prevent generation of dead volume between the first horizontal contact surface 411 of the inner ring 41.

The first dead volume preventing jaw 512 is to remove the dead volume generated between the inner circumferential surface of both ends of the circular vane 51 and the first horizontal contact surface 411 during the swinging motion of the circular vane 51, Inner circumferential surfaces of both ends of the circular vane 51 are formed to be in close contact with the first horizontal contact surface 411.

In this way, the first dead volume preventing jaw 512 prevents the dead volume generated between the circular vane 51 and the first horizontal contact surface 411 of the inner ring 41, thereby compressing the compressed or intake refrigerant gas contained in the dead volume. Abnormal compression or suction caused by this can be prevented smoothly.

9 is an enlarged plan sectional view showing main parts of a fifth embodiment of the present invention.

As shown in FIG. 9, the linear slider 541 has a second carcass at both ends of the lower body so as to prevent the occurrence of a dead body between the inner peripheral surface of both ends of the circular vane 51 and the first horizontal contact surface 411 of the inner ring 41. A red bump 542 is formed.

The second dead volume stopper 542 has a dead volume generated between the inner circumferential surfaces of both ends of the circular vanes 51 and the first horizontal contact surface 411 of the inner ring 41 during the movement of the circular vanes 51. It is formed at both ends of the lower end of the linear slider 541 in its corresponding body shape so as to be removed.

In this way, the second dead volume stopper 542 prevents dead volume generated between the circular vane 51 and the first horizontal contact surface 411 of the inner ring 41, thereby compressing the compressed or inhaled refrigerant gas contained in the dead volume. Abnormal compression or suction caused by this can be prevented smoothly.

As described above, the present invention facilitates the processing of the sealing means and improves the adhesion between the circular vane and the sealing means, and at the same time makes the operation of the sealing means more stable, making the sealing means easy and the sealing force between the compression chambers. This is significantly enhanced and has the effect of improving the performance of the compressor.

In addition, the present invention has the effect that the behavior of the circular vane is more stable by preventing the interference between the circular vane and the inner peripheral surface of the cylinder.

In addition, the present invention is to prevent the occurrence of the dead volume between the circular vane and the sealing means has an effect that the abnormal compression of the compressor due to the refrigerant gas introduced into the dead volume is prevented in advance.

Claims (5)

A pair of annular spaces are formed inside the cylinder having an inner ring, and a circular vane having an opening is inserted into the annular space, and a pair formed in the annular space is inserted in close contact with the opening and interlocked with the circular vanes. In the swing vane compressor is provided with a sealing means for sealing between the compression chamber of the; The sealing means is inserted between the first horizontal contact surface formed on the outer circumferential surface of the inner ring and the second horizontal contact surface formed on the inner circumferential surface of the cylinder in correspondence to the first horizontal contact surface to linearly reciprocate along the horizontal contact surface. Swivel vane compressor having a linear slider, characterized in that consisting of a linear slider. The method of claim 1; Swivel vane compressor having a linear slider, characterized in that the horizontal cutting surface is formed on both ends of the circular vane on both sides of the opening to prevent interference between the circular vane and the second horizontal contact surface. The method of claim 1; The linear slider having a linear slider is formed on the inner circumferential surface of the cylinder to both sides of the second horizontal contact surface along the turning trajectory of the upper ends of the circular vane so as to prevent interference between the circular vane and the second horizontal contact surface. Slewing vane compressor. The method according to any one of claims 1 to 3; Swivel vane compressor having a linear slider characterized in that the first dead volume bumps are formed at both ends of the lower side of the circular vanes so as to prevent the occurrence of the dead volume between the circular vanes and the first horizontal contact surface. The method according to any one of claims 1 to 3; And a second dead volume stopper is formed on both sides of the lower portion of the linear slider to prevent generation of dead volume between the circular vane and the first horizontal contact surface.

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