KR100451842B1 - a compressor - Google Patents

Abstract

PURPOSE: A compression pump is provided to minimize the size of the compression pump by combining a vane assembling groove of a rotor with a hinge projection of a vane, and to prevent discharge of fluid between the rotor and the vane in compressing by installing a rotor sealing unit in the outer periphery of the rotor. CONSTITUTION: A compression pump comprises a cylinder(10), a rotor(20) rotated and inserted to a crank pin installed in a main shaft of the cylinder, a vane(30) turning the rotor in the cylinder and forming a compression chamber and a suction chamber in the rotor, a suction port(40) sucking refrigerant into the suction chamber in turning the rotor, and a discharge port(50) having a check valve(51) discharging refrigerant compressed from the suction port. A vane assembling groove(26) is formed longitudinally in the outer periphery of the rotor, and the width of an opening part(26a) is formed to be smaller than the center diameter of the vane assembling groove. A vane groove(11) is formed in the cylinder, and the vane is turned around a hinge shaft(31) to compress. A hinge projection(32) is formed in the end of the vane, and combined with the vane assembling groove of the rotor.

Description

Compression pump {a compressor}

The present invention relates to a compression pump capable of forcibly compressing and supplying a fluid such as a gas or a liquid, and more particularly, by performing a compression process and a suction process in a state in which a vane and a rotor constituting the compression pump are coupled to each other. The present invention relates to a compression pump that maximizes the compression efficiency and enables its use in low pressure as well as high pressure pumps.

As is well known, a compression pump such as a compressor functions to compress and supply a fluid at a high temperature and high pressure in a cycle in which compression, condensation, expansion, and a process are continuously performed through a fluid such as a refrigerant.

The compression pump as described above is inserted into the crank pin 110 formed on the main shaft, as shown in the first diagram and the rotor 120 to rotate together, the rotor 120 is rotated in the cylinder 130, while operating the compression chamber The vane 170 inserted into the cylinder slot 160 so as to constitute the 140 and the suction chamber 150 and elastically supported by the spring, and the refrigerant flows to the suction chamber 150 according to the rotation of the rotor 120. The suction port 180 to be sucked and also the discharge port 190 to discharge the refrigerant compressed and sucked into the suction port 180 are configured.

When the main shaft is rotated by the motor to operate the compression pump in the state configured as described above, the crank pin 110 rotates to rotate the rotor 120.

At this time, since the suction force is generated in the suction chamber 150 formed by the vane 170 when the rotor 120 rotates, the refrigerant is sucked into the suction chamber 150 through the suction port 180.

The refrigerant sucked into the suction chamber 150 is compressed in the compression chamber 140 according to the rotation of the rotor 120 and is discharged to the discharge port 190.

In the conventional compression pump as described above, the tip of the vane 170 receives the force F by the pressure ΔP = P1-P2 between the suction chamber 150 and the compression chamber 140 as the second degree during compression. Both ends of the 170 are in contact with the cylinder slot 160 locally to receive a concentrated load, thereby causing a problem in that both ends of the cylinder slot 160 and the vane 170 are badly worn.

In addition, in the related art, the fluid compressed at high pressure in the compression chamber 140 presses one side of the vane 170 as shown by the arrow of FIG. 1, and thus slides in and out of the cylinder slot 160 of the cylinder 130. As the frictional force with the vane 170 is greatly increased, not only the mechanical damage caused by the wear of the vane 170 is further promoted, but also the thickness of the cylinder 130 is thickened by the length of the cylinder slot 160, resulting in a compression pump. There were many problems such as the increase in size.

Therefore, in recent years, a compression pump (Japanese Laid-Open Patent Publication No. 6-50273) as shown in FIG. 3 has been developed, and the compression pump forms the vane groove 231 in the inner place of the cylinder 230, and then The vane 220 is installed so that the vane 220 is rotated by a predetermined angle about the hinge 221 at the vane groove 231 to allow the vane 220 to correspond to the rotor 240, but the rotor 240 of the In the outer circumferential position, the coupling protrusion 241 or the coupling protrusion groove was protruded and coupled to the tip of the vane 230, and the conventional compression pump configured as described above has a somewhat larger size of the cylinder of FIG. Although it can be reduced, since the coupling protrusion 241 protrudes on the outer circumference of the rotor 240 which rotates at a high speed, a phenomenon in which stress concentrates on the coupling protrusion 241 occurs, thereby damaging the coupling protrusion 241. The problem has been raised.

Therefore, the present invention has been researched and developed in view of the above problems, the length of the vane coupling groove formed in the rotor, and then to minimize the size of the compression pump by combining the hinge protrusion of the vane to the vane coupling groove. It is an object of the present invention to provide a compression pump which minimizes damage to the rotor and vanes due to high speed rotation.

1 and 2 is a schematic cross-sectional view of a compression pump according to the prior art,

3 is a cross-sectional view showing another embodiment of a compression pump according to the prior art,

4 is an exploded perspective view of a compression pump according to the present invention;

Figure 5 (a), (b), (c) is a cross-sectional view showing sequentially the operating state of the compression pump according to the present invention,

Figure 6 is an exploded perspective view showing the main portion extracting the rotor seal means of the compression pump according to the present invention,

Fig. 7 is a side view of the main portion taken from Fig. 6;

<Description of the symbols for the main parts of the drawings>

10: Cylinder 11: Vane Home

20: rotor 21: compression chamber

22: suction room 24: seal groove

25: support groove 26: vane coupling groove

26a: Opening 30: Vane

31: hinge axis 32: hinge protrusion

33: compression surface 40: suction port

50: discharge port 70: rotor seal means

71: seal member 72: seal

72a: Insertion groove 73: Support part

73a: rotary shaft 73b: weight shaft

73c: rotation support shaft 74: elastic means

The present invention for achieving the above object is a cylinder, a rotor which is inserted into the crank pin installed on the main shaft in the cylinder and eccentrically rotated together, while the rotor rotates in the cylinder and the compression chamber and the suction chamber is configured A compression pump including a vane, a suction port through which the refrigerant is sucked into the suction chamber as the rotor rotates, and a discharge port through which the refrigerant sucked into the suction port is discharged. The vane coupling groove is formed to be long, but the opening width of the opening is smaller than the center diameter of the vane coupling groove, and the vane groove is formed in the inner place of the cylinder, and then the vane groove is fixed around the one side hinge. Each vane is rotatably installed, and a hinge protrusion is formed at the tip of the vane to hinge the vane coupling groove of the rotor. Characterized in that the protrusion can be bound.

In addition, the present invention is characterized in that the vane is formed with a compression surface concentric with the hinge axis to ensure that the high pressure fluid pressure is uniformly distributed, while at the same time the compression force transmitted to the compression surface is transmitted to the hinge shaft portion. .

In addition, the present invention is characterized in that the seal groove is formed on the outer circumferential side of the rotor in the longitudinal direction, the rotor seal means is provided in the seal groove so that the end of the seal member is projected slightly in the outer circumferential direction of the rotor.

The present invention also has a seal groove formed on the outer circumferential side of the rotor in the longitudinal direction, the support groove is formed at a substantially right angle to one side of the seal groove to install a needle-shaped seal member on the seal groove and the support groove. Next, the elastic means is mounted on the seal member located in the support groove.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Figure 4 is an exploded perspective view of a compression pump according to the present invention, Figure 5 (a), (b), (c) is a cross-sectional view showing the operating state of the compression pump according to the invention sequentially.

The cylinder 10, the rotor 20 is inserted into the crank pin installed in the main shaft (S) in the cylinder 10 and rotates together, and while the rotor 20 rotates in the cylinder 10, while operating A vane 30 for forming the compression chamber 21 and the suction chamber 22 in the rotor 20, a suction port 40 through which the refrigerant is sucked into the suction chamber 22 according to the rotation of the rotor 20; In addition, in the compression pump configured to include a discharge port 50 and the like provided with a check valve 51 to discharge the refrigerant compressed by the suction port 40,

First, it is important to form the vane coupling groove 26 longer in the outer circumferential position of the rotor 20, but to make the opening width of the opening 26a smaller than the center diameter of the vane coupling groove 26, Both ends of the opening 26a may be smoothly rounded.

Then, the vane groove 11 is formed in the inner place of the cylinder 10, and then the vane 30 is installed to the vane groove 11 to be rotated by a predetermined angle about the hinge shaft 31 on one side. The hinge protrusion 32 is formed at the tip of the vane 30 to allow the hinge protrusion 32 to be bound at the side of the vane coupling groove 26 of the rotor 20. At this time, when the hinge protrusion 32 of the vane 30 is bound to the vane coupling groove 26 of the rotor 20 as shown in FIG. 5, the vane 30 should be rotatably installed from the rotor 20 at a predetermined angle. do.

In addition, the vane 30 is provided with a compression surface 33 concentric with the hinge shaft 31 to uniformly distribute the high pressure fluid pressure as shown by the arrow of FIG. It is preferable to allow the compressive force transmitted to 33 to be transmitted to the hinge shaft 31 portion.

In addition, a seal insertion groove having a predetermined shape is formed along the outer surface of the vane 30, and then the seal member 34 is installed when the vane 30 operates by installing the seal member 34 in the seal insertion groove. By operating together in close contact with the inner wall of the vane groove 11, the airtightness between the compression side and the suction side is effectively maintained.

Although not shown, the vane 30 is provided with an oil supply passage (not shown) through which lubricant is supplied from the outside to maintain the airtightness of the compression chamber 21 and the suction chamber 22, and the rotor 20 and the vane 30. ) To minimize friction.

Meanwhile, as shown in FIGS. 6 and 7, the rotor seal means 70 is installed on the outer circumferential side of the rotor 20. First, the seal groove 24 is formed in the longitudinal direction on the outer circumferential side of the rotor 20. It is formed, but forms a support groove 25 which is substantially perpendicular to one side of the seal groove 24.

Then, a seal member 71 having a needle-shaped shape is installed in the seal groove 24 and the support groove 25. The seal member 71 includes a seal 72 corresponding to the seal groove 24 and the support. The rotary shaft portion 73a of one end of the support portion 73 is fitted into the insertion groove 72a which is divided into the groove portion 25 and the support portion 73 corresponding to the groove portion 25, and is opened to one side of the lower end of the seal portion 72. The other end of the support portion 73 is formed with a weight shaft portion (73b) heavier than the rotation shaft portion (73a), the rotation shaft portion (73a) on the support portion 73 between the rotation shaft portion (73a) and the weight shaft portion (73b) Rotation support shaft (73c) closer to the () is formed so that the upper end of the seal portion 72 connected to the support portion 73 can maintain the state protruding out of the seal groove 24 of the rotor (20).

In addition, the elastic means 74 such as a spring is installed between the weight shaft portion 73b and the support groove portion 25 of the support portion 73 so that the upper end portion of the seal portion 72 is outside the seal groove 24 of the rotor 20. It is desirable to protrude with a constant force.

The above embodiments are intended to illustrate the present invention, but the present invention is not limited to this embodiment. Various modifications and variations of the present invention will be apparent to those skilled in the art without departing from the scope and spirit of the invention, which modifications and variations fall within the spirit and scope of the invention as defined by the appended claims.

Referring to the effect of the compression pump configured as described above in detail.

First, looking at the assembly process of the rotor 20 and the vane 30 of the compression pump, the hinge protrusion 32 of the vane 30 is rotatably installed on the side of the vane coupling groove 26 of the rotor 20. Next, the hinge shaft 31 of the vane 30 is installed at one side of the vane groove 11 of the cylinder 10 to allow the vane 30 to enter and exit the vane groove 11 of the cylinder 10.

Referring to the driving sequence of the compression pump in a state in which the rotor 20 and the vane 30 are coupled to each other as described above, as shown in FIG. 5 (a), the check valve 51 is closed in the main shaft S. This rotation causes the rotor 20 to eccentrically rotate so that fluid compression in the compression chamber 21 starts.

At this time, the vanes 30 are released from the vane groove 11 inside the cylinder 10 about the hinge shaft 31 on one side thereof, the vane 30 in the vane coupling groove 26 of the rotor 20. Since the hinge protrusions 32 are coupled to each other, the vanes 30 are engaged with each other along the eccentric rotation of the rotor 20.

As shown in (b) of FIG. 5, the rotor 20 rotates clockwise from the state of FIG. 5 (a) to correspond to an initial stage of suction and compression, and the check valve 51 is kept closed. Therefore, the fluid in the compression chamber 21 starts to compress more and more. When the mechanical friction is ignored, the torque received by the rotor 20 is a counterclockwise torque due to the clockwise torque applied by the drive motor and the pressure difference between the suction chamber 22 and the compression chamber 21, And the torque of the counterclockwise direction by the action of the tension spring (not shown) which is a mechanism which reduces the pulsation of the rotor 20 rotation becomes all. Thus, the tension spring exerts a force in a direction that impedes rotation of the rotor 20 in the initial stage of compression.

On the other hand, when the rotor 20 is rotated in the clockwise direction in the cylinder 10, the vane 30 is coupled to the vane coupling groove 26 of the rotor 20 to the maximum in the vane groove (11). In this case, the vane 30 has a compression surface 33 formed concentrically with the hinge shaft 31 so that the high pressure fluid pressure is uniformly distributed as shown by the arrow of FIG. The compressive force transmitted to 33 may be transmitted to the hinge shaft 31 to greatly extend the service life of the vane 30.

As shown in FIG. 5C, the rotor 20 is rotated by 180 degrees or more from the state of FIG. 5A, and the check valve 51 has a pressure exceeding the target pressure in the compression chamber 21. When it is opened.

After the state of FIG. 5C, the fluid pump returns to the state of FIG. 5A and the above-described process is repeated.

At this time, the vane 30 enters the vane groove 11 inside the cylinder 10, and at this time, the seal member 34 installed along the outside of the vane 30 is formed on the inner wall of the vane groove 11. Since it keeps in close contact, the fluid pressure to the vane 30 can be prevented from escaping.

6 and 7, the seal unit 72 is installed on the outer circumferential side of the rotor 20 so that the seal portion 72 slightly protruded to the outer circumference of the rotor 20 has a cylinder 10. By being in close contact with each other, high pressure fluid pressure can be prevented from leaking. In this case, the seal member 71 includes a seal portion 72 corresponding to the seal groove 24 and a support portion corresponding to the support groove 25. 73, the rotary shaft portion 73a of one end of the support portion 73 is rotatably coupled to the insertion groove 72a of the seal portion 72, and then the rotary support shaft 73c is inserted into the support groove portion 25. The upper end portion of the seal portion 72 connected to the support portion 73 is formed outside the seal groove 24 of the rotor 20 in contact with the upper end portion of the seal portion 72 connected to the support portion 73. It is possible to maintain the protruding state.

In addition, an elastic means 74 such as a spring is installed between the weight shaft portion 73b of the support portion 73 and the support groove portion 25 so that the upper end portion of the seal portion 72 is outside the seal groove 24 of the rotor 20. By protruding with a constant force, it is possible to prevent the fluid pressure from escaping between the rotor 20 and the vanes 30.

Accordingly, the present invention minimizes the size of the compression pump by forming a long vane coupling groove 26 in the rotor 20 and then engaging the hinge protrusion 32 of the vane 30 with the vane coupling groove 26. Of course, there is a very useful effect of minimizing damage to the rotor 20 and vanes 30 due to the high speed rotation.

In addition, the present invention has a very useful effect to prevent the fluid pressure escape between the rotor 20 and the vanes 30 during compression stroke by installing the rotor seal means 70 on the outer peripheral side of the rotor 20 .

Claims (4)

A rotor inserted into a cylinder, a crank pin installed on a main shaft in the cylinder and eccentrically rotating; vanes for forming a compression chamber and a suction chamber while the rotor rotates in the cylinder, and the rotor rotates according to the rotation of the rotor. A compression pump comprising a suction port through which a refrigerant is sucked into a suction chamber, and a discharge port through which a refrigerant compressed by being sucked into the suction port is discharged, The vane coupling groove is formed longer in the outer circumferential position of the rotor, the opening width of the opening is smaller than the center diameter of the vane coupling groove, and the vane groove is formed in the inner place of the cylinder, and then the vane groove is formed. Compression pump, characterized in that for installing a vane that is rotated at a predetermined angle around the hinge on one side, by forming a hinge protrusion on the tip of the vane to bind the hinge protrusion toward the vane coupling groove of the rotor. The method of claim 1, The vane is provided with a compression surface concentric with the hinge shaft to uniformly distribute the high pressure fluid pressure, and at the same time the compression force transmitted to the compression surface is transmitted to the hinge shaft portion. The method of claim 1, Compression pump, characterized in that the rotor groove formed on the outer circumferential side of the rotor in the longitudinal direction, the seal member is installed in the seal groove so that the end of the rotor is projected slightly in the outer circumferential direction of the rotor. The method of claim 3, wherein A seal groove is formed in the longitudinal direction on the outer circumferential side of the rotor, and a support groove part substantially perpendicular to the seal groove is formed at one side of the seal groove to install a needle-shaped seal member on the seal groove and the support groove, and then the support groove part. Compression pump characterized in that the elastic means is mounted on the seal member located.