KR20030032352A - Dual capacity compressor - Google Patents

Abstract

PURPOSE: A dual capacity compressor is provided to stably work keeping fixed eccentric degree while rotating action for changing capacity. CONSTITUTION: A compressor comprises a power generating part including a motor capable of reverse rotation, and a crankshaft(23) inserted to the motor; a compression part including a cylinder, a piston placed in the cylinder, and a connecting rod(33) connected with the piston; a crank pin(110) formed on an upper end of the crankshaft eccentrically with a center of the crankshaft; an eccentric sleeve(120) having an inner circumferential surface joined to a periphery of the crank pin to rotate and a periphery to which an end of the connecting rod is joined to rotate, and re-arranged according to rotating direction of the motor to change effective eccentric degree between the crank pin and the connecting rod; and a fixing member(130) completely fixing the eccentric sleeve to the crank pin.

Description

Dual Capacity Compressor {DUAL CAPACITY COMPRESSOR}

The present invention relates to a compressor for compressing a working fluid such as a refrigerant to a predetermined pressure, and more particularly, to a compressor for changing a compression capacity as necessary.

The dual displacement compressor is a kind of reciprocating compressor whose piston stroke and compression capacity are varied by an eccentric sleeve rotatably connected to the crank pin of the crankshaft according to the rotational direction of the motor and the crankshaft. Since the dual capacity compressor can adjust the compression capacity according to the size of the load required, it is widely applied to increase the operating efficiency in various devices that require the compression of the working fluid, in particular, home appliances such as refrigerators. have.

U.S. Patent No. 4,236,874 discloses a general double capacity compressor, which will be described in brief with reference to the patent.

1 is a cross-sectional view showing the structure of a double displacement compressor according to US Patent No. 4,236,874, and FIG. 2 is a schematic view showing the operation of the double displacement compressor.

Referring to FIG. 1, the main part of a double displacement compressor includes a piston 7, a crankshaft 1, and a crank pin eccentrically formed with the center 3a of the crankshaft in the cylinder 7. 3), it consists of an eccentric ring (4) coupled to the crank pin (3), the connecting rod (6) connected to the eccentric ring (4) and the piston (7), respectively. The eccentric ring 4 and the connecting rod 6 are rotatable with respect to an adjacent component and have the center of rotation of the crank pin center 3a. On each contact surface of the crank pin 3 and the eccentric ring 4, a release region 9 of a predetermined length is formed, and in the release region 9, the crank pin 3 and the eccentric ring 4 are connected to each other. A key 5 for engagement is provided. The operation according to the compression capacity of the double displacement compressor is as follows. As shown in FIG. 2, in the double displacement compressor, the stroke distance of the piston 7 is adjusted by the amount of eccentricity that varies according to the arrangement state of the eccentric ring 4, and when a large load is required, the crankshaft ( 1) clockwise (forward direction), when the load is required to be small, the crankshaft 1 is rotated counterclockwise (reverse direction). More specifically, FIG. 2A shows a state where the piston 7 is located at the top dead center and B is the bottom dead center during the clockwise rotation, and in this case, the eccentricity is the maximum, so the stroke distance Lmax. Is also the maximum. In addition, FIG. 2C shows a state where the piston 7 is located at the bottom dead center, and D is the top dead center of the piston, and the stroke distance Lmin is minimized due to the minimized amount of eccentricity.

However, due to the rotation about the crankshaft center 1a during this operation, a separate centrifugal force acts on the crank pin 3 and the eccentric ring 4, and this centrifugal force is generated between the axis center 1a and the pin center 3a. And an extension line between the shaft center 1a and the ring center of gravity 4a, respectively. Therefore, unlike A and B of FIG. 2, since C and D do not coincide with each other, the eccentric ring 4 has the product of the vertical distance d with respect to the pin 3 and its centrifugal force. The local moment of rotation which occurs appears and the direction of action of this moment of rotation is the same as the direction of rotation of the crankshaft 1 (counterclockwise). Since the crank pin 3 and the eccentric ring 4 are members rotatably separated from each other, the rotation moment causes relative rotation in the direction of rotation of the crank shaft 1 so that the key 5 is moved to the crank pin 3 and Release from the eccentric ring (4). The eccentric ring 4 and the key 5 are thus moved in the rotational direction as indicated by the dashed line in FIG. 3. Further, as shown in Fig. 3, for example, the pressure P in the cylinder (re-expansion pressure of the working fluid) after the compression process during operation in the clockwise direction causes the eccentric ring 4 to rotate in the crankshaft 1 direction. Acting as a pushing force, this pressure rotates the eccentric ring 4 relative to the crank pin 3 in the direction of the compressor rotation. As a result, the relative rotation makes the operation of the compressor unstable, and the desired compression performance is not obtained.

Substantially the relative rotation occurs because the key 5 does not completely secure the crank pin 3 and the eccentric ring 4. In addition, the key 5 makes a rolling motion in the release area 9 whenever the compressor rotation direction changes, thereby shortening the life due to severe wear at each contact.

Meanwhile, in addition to the U.S. Patent No. 4,236,874, many patent publications disclose the technologies related to the double displacement compressor and briefly describe them.

First, US Pat. No. 4,479,419 similarly discloses a dual displacement compressor using a crank pin, an eccentric cam and a key. Here, the key is fixed to the eccentric cam and moves along the track formed on the crank pin when the compressor rotation direction is changed. However, even in the U.S. Patent No. 4,479,419, since the key does not completely restrain the crank pin and the eccentric cam, unstable operation of the compressor due to relative rotation occurs.

Further, in the compressor according to US Pat. No. 5,951,261, a bore having a predetermined inner diameter is formed across the eccentric portion and a bore having the same inner diameter as the eccentric portion bore is formed on one side of the eccentric cam. A pin is provided in the bore of the eccentric, and a compression spring is provided in the bore of the eccentric sleeve. Thus, when the respective bores are aligned during rotation, the pin is moved to the bore of the cam by centrifugal force to constrain the eccentric portion and the eccentric cam. However, in the U.S. Patent No. 5,951,261, since the eccentric cam has only one bore, the eccentric portion and the eccentric cam can be constrained only when the compressor is rotated in only one direction. In addition, since it is difficult for the pin to move accurately from the eccentric to the cam practically through the respective bores, operational reliability is not guaranteed.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a dual capacity compressor that operates stably while maintaining a constant amount of eccentricity even when rotating in any direction for changing the compression capacity.

1 is a cross-sectional view showing the configuration of a double displacement compressor according to the prior art.

2 is a schematic diagram illustrating the operation of the dual displacement compressor of FIG.

3 is a schematic diagram showing the relative rotation between a crank pin and an eccentric sleeve that occur during operation of a conventional double displacement compressor.

4 is a cross-sectional view showing the overall configuration of a double displacement compressor according to the present invention.

Figure 5a is a side view showing a first embodiment of a double displacement compressor according to the present invention with a partial cross section.

5B is a plan view showing a first embodiment of the double displacement compressor according to the present invention, including a partial cross section.

6A and 6B are plan views showing the operation of the first embodiment of the present invention in the forward rotation.

7A and 7B are plan views showing the operation of the first embodiment of the present invention in reverse rotation.

8A is a side view showing a second embodiment of a double displacement compressor according to the present invention, including a partial cross section.

8B is a plan view showing a second embodiment of the double displacement compressor according to the present invention with a partial cross section.

9A is a perspective view illustrating a crank pin according to a second embodiment of the present invention.

9B is a perspective view showing a modification of the crank pin of FIG. 9A;

FIG. 10 is a plan view showing a modification of the fixing member shown in FIG. 8 mounted in the crank pin. FIG.

11A and 11B are plan views showing the operation of the second embodiment of the present invention in forward rotation; And

12A and 12B are plan views showing the operation of the second embodiment of the present invention in the reverse rotation.

Description of the main parts of the drawing

20: power generating section 30: compression section

40: administrative variable 110,210: crank pin

111, 211a, 211b: fixing member mounting portion 120, 220: eccentric sleeve

121,221: thick side groove 122,222: thin side groove

130,230: fixing member 231: first protrusion

232: second protrusion 233: stopper

140,240: elastic member

In order to achieve the above object, the present invention provides a power generation unit including a crank shaft inserted into the motor and a motor capable of reverse rotation with respect to a predetermined rotation direction; A compression unit including a cylinder of a predetermined size, a piston located in the cylinder, and a connecting rod connected to the piston; A crank pin formed eccentrically at an upper end of the crankshaft; An inner circumferential surface rotatably coupled to an outer circumferential surface of the crank pin and an outer circumferential surface rotatably coupled to an end of the connecting rod, and being rearranged according to the rotational direction of the motor to change an effective amount of eccentricity between the crank pin and the connecting rod. Eccentric sleeves; And a fixing member located in the crank pin and completely restraining the eccentric sleeve to the crank pin in both clockwise and counterclockwise rotation of the motor. The present invention provides a dual displacement compressor having different compression capacities, wherein the relative movement of the crank pin and the eccentric sleeve is substantially prevented by the fixing member regardless of the rotational direction of the motor.

The crank pin of the dual displacement compressor configuration includes a mount for movably receiving the fixing member.

And when the crank pin has a solid shaft shape, the fixing member mounting portion is a through hole formed along the radial direction of the solid shaft crank pin, when the crank pin has a hollow shaft shape, the fixing member mounting portion is the crank pin It becomes a pair of through-holes formed in the wall so as to face each other. In addition, the fixing member mounting portion of the hollow shaft crank pin preferably includes a groove extending from a predetermined position of the crank pin wall to the upper end.

The eccentric sleeve comprises two grooves each extending radially from the inner circumferential surface toward the outer circumferential surface and preferably these two grooves are disposed opposite each other on an extension line passing through the center of the crank pin and the center of the eccentric sleeve.

The holding member is positioned within the crank pin as a whole when at rest and at least a portion protrudes out of the crank pin to engage the eccentric sleeve during operation. The length of the fixing member is preferably smaller than the crank pin diameter, and the cross section of the fixing member may be any one of polygons such as a circle, a square, a hexagon, and the like.

Here, the fixing member may be a straight straight pin protruding out of the crank pin along the centrifugal force action direction in the solid crank pin.

In addition, the fixing member may include a first protrusion projecting outside the crank pin in the centrifugal force direction during operation; A second protrusion formed in a direction opposite to the first protrusion and positioned in the mounting portion during operation; And a stopper defining a length of the second protrusion so as not to protrude out of the crank pin.

Here, it is preferable that the crank pin contact surface of the stopper has a shape coincident with the inner surface of the crank pin.

On the other hand, the dual capacity compressor of the present invention preferably further comprises an elastic member for restoring the protruding fixed member to the inside of the crank pin during operation stop.

The elastic member is inserted into the grooves of the eccentric sleeve, respectively, when a simple pin-shaped fixing member is used, or is inserted into the first protrusion of the fixing member.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention in which the above objects can be specifically realized are described with reference to the accompanying drawings. In describing the present embodiment, the same name and the same reference numerals are used for the same configuration and additional description thereof will be omitted below. First, the overall structure of a double displacement compressor according to the present invention will be described with reference to FIG. 1.

As shown, the dual displacement compressor of the present invention is located in the upper portion of the power generating unit 20 and the power generating unit 20 to generate and transmit the required power, which is located in the lower part of the compressor, as shown in the figure. Compression unit 30 for compressing the working fluid by using. In addition to this general configuration, the dual displacement compressor includes a stroke variable unit 40 which connects the power generating unit 20 and the compression unit 30 and changes the compression capacity of the compression unit 30 during operation. . Meanwhile, the container 11 encloses the power generating unit 20 and the compression unit 30 in a sealed manner in order to prevent leakage of the refrigerant, and the frame 12 is attached to the container inside the container 11. It is elastically supported by a plurality of support members (ie springs) 14. In addition, the refrigerant suction pipe 13 and the discharge pipe 15 are respectively installed at a predetermined position of the container 11 and communicate with the inside thereof.

The power generator 20 is installed under the frame 12 and includes a motor and a crankshaft 23 including a stator 21 and a rotor 22 to generate rotational force by an external power source. Here, the motor is rotatable in a counterclockwise direction, that is, clockwise and counterclockwise. The lower part of the crankshaft 23 is inserted into the rotor 22 so as to transmit power, and has a structure for supplying lubricating oil accommodated in the lower part of the compressor, such as an oil hole or an oil groove, to each drive unit of the compressor. Have

The compression unit 30 is installed on the frame 12 to be positioned above the power generating unit 20 and has a driving mechanism mechanically moving to compress the refrigerant and an intake and discharge valve structure to assist the driving mechanism. Is done. The drive mechanism, together with the cylinder 32 forming a substantial compression space, provides power to the piston 31 and the piston 31 for reciprocating motion inside the cylinder 32 for refrigerant suction / compression. It has a connecting rod 33 for transmitting. In addition, the valve structure supplies the refrigerant to the cylinder 32 and discharges the compressed refrigerant by a combination of related parts such as the cylinder head 34 and the head cover 35.

In the dual capacity compressor configuration of the present invention, the power generation unit and the compression unit, etc. are the same as the general compressor, and thus an additional description thereof will be omitted and the stroke variable unit 40 will be described as follows.

The stroke variable portion 40 is fixed to mutually fix the crank pin and the crank pin and the eccentric sleeve rotatably mounted between the crank pin is formed eccentrically on the upper end of the crankshaft, the outer peripheral surface of the crank pin and the connecting rod Member. More specifically, in the present invention, the fixing member is basically movably mounted in the crank pin, so that at least a portion of the fixing member protrudes out of the crank pin to be inserted with a part of the eccentric sleeve by centrifugal force during operation.

By this configuration, the rearrangement of the eccentric sleeve is basically performed according to the rotation direction (forward or reverse direction) of the motor, and the compression capacity is changed by the effective eccentric amount and the piston displacement change. Also in any rotational direction of the motor, the fixing member completely engages the eccentric sleeve with the crank pin to prevent relative rotation by mutually generated rotation moments.

The dual displacement compressor of the present invention outlined above is described in more detail in conjunction with the associated drawings in the following first and second embodiments.

First embodiment

5A and 5B are side and top views illustrating a first embodiment of a dual displacement compressor according to the present invention, wherein each of the components is shown assembled together, including some cross sections, for ease and clarity of description. . Referring to the drawings, a first embodiment of the present invention will be described.

The dual displacement compressor according to the first embodiment is a crank pin 110 having a fixing member mounting portion 111, an eccentric sleeve 120 rotatably mounted to the crank pin 110 and having a pair of grooves 121 and 122. And, and the fixing member 130 is located in the mounting portion 111, the other parts are the same as the compressor of FIG.

As shown in FIG. 5A, the crank pin 110 of the first embodiment has a solid shaft shape and an oil passage 112 and an oil supply hole formed in a lower portion together with the fixing member mounting portions 111. (113).

Here, the mounting portion 111 extends in the radial direction beyond the center 110a of the solid shaft crank pin 110 and is formed as a through hole for substantially receiving the fixing member 130. And the diameter of the mounting portion 111 that is the through hole is formed slightly larger than the cross-sectional size of the fixing member 130 for the smooth movement of the fixing member 130.

The oil passage 112 communicates with an oil groove formed outside the crankshaft 23 and communicates with the oil supply hole 113. During operation, the lubricating oil contained in the bottom of the compressor is scattered to be supplied to the contact surface between the parts, primarily through the oil groove and the oil passage 112, to prevent abrasion and smooth operation of the parts. It may be directly supplied between the crank pin 110 and the eccentric sleeve 120 through the). Preferably, the crank pin 110 is formed higher than the eccentric sleeve 120, so that the lubricating oil may be scattered at a high position and evenly supplied to each driving unit.

The eccentric sleeve 120 according to the first embodiment basically has an inner circumferential surface and an outer circumferential surface rotatably coupled to the outer circumferential surface of the crank pin 110 and the end of the connecting rod 33, and the fixing member 130 during operation. ) Includes a pair of grooves 121 and 122 inserted therein.

The grooves 121 and 122 extend radially in a predetermined depth from the inner circumferential surface of the eccentric sleeve 120 toward the outer circumferential surface. More specifically, the grooves 121 and 122 are disposed to face each other on an extension line passing through the center of gravity of the eccentric sleeve 120 itself and the crank pin center 110a (that is, the center of the eccentric sleeve inner diameter). That is, the grooves 121 and 122 are disposed in the maximum and minimum thickness portions of the eccentric sleeve 120, respectively, as shown, and are fixed to the crank pin 110 through the grooves 121 and 122 during operation. Thereby maintaining the correct maximum and minimum eccentricity.

It is important that the grooves 121 and 122 also be aligned with the mounting portion 111 for accurate insertion of the fixing member 130.

The fixing member 130 according to the first embodiment has a shape as a straight simple pin located in the through hole mounting portion 111 as shown. In this case, the eccentric sleeve 120 rotates around the crank pin 110 to change the amount of eccentricity when the rotation direction of the compressor is changed. The length of the fixing member 130 is formed smaller than the diameter of the crank pin 110 so as not to interfere with the rotational movement of the eccentric sleeve 120, any end protrudes to the outer circumferential surface of the crank pin 110 during operation stop It doesn't work. In addition, the cross section of the fixing member 130 is described and illustrated with respect to the circle in the present invention, it may be any shape that can be inserted into the grooves (121, 122), such as square and hexagon.

Due to this structure, the fixing member 130 is located in the crank pin 110 at rest and at least partly engages with the eccentric sleeve 120 and more specifically any one of the grooves 121 and 122 during operation. It protrudes out of the crank pin. And this protruding length is limited by the closed ends of the grooves (121, 122).

Meanwhile, the first embodiment of the present invention further includes an elastic member 140 installed in the grooves 121 and 122, and the elastic members 140 crank the fixing member 130 that protrudes when the operation is stopped. It is restored to 110.

The operation of the present invention according to the first embodiment described above is described next with reference to the associated drawings. 6A and 6B show the operation of the first embodiment in the forward rotation and FIGS. 7A and 7B show the operation of the second embodiment in the reverse rotation.

First, FIG. 6A shows the relative position between the fixing member 130 and the eccentric sleeve 120 when the crankshaft 23 begins to rotate in the forward (clockwise) direction. When the crankshaft 23 begins to rotate, the eccentric sleeve 120 interposed between the crank pin 110 and the connecting rod 33 also rotates and is aligned as shown. At this time, the rotational angular velocity reaches a certain level, and the fixing member 130 is freed from the restraint by the inner circumferential surface of the eccentric sleeve 120, and as shown in FIG. Move along the extension line between 23a and 110a. Accordingly, the fixing member 130 is inserted into the thick thickness side groove 121 so that the crank pin 110 and the eccentric sleeve 120 are completely engaged with each other. Therefore, in the forward rotation, the relative rotation between the crank pin 110 and the eccentric sleeve 120 even if the external force P and any other force are transmitted through the connecting rod 33 by re-expansion of the working fluid after the compression process. This is avoided. And even if a local rotation moment occurs in the eccentric sleeve 120, the relative rotation with respect to the crank pin 110 can also be prevented. In addition, as shown in FIG. 6B, the solid line portion of the figure shows a top dead center state, and the dotted line portion represents a bottom dead center state, and in the case of forward rotation, the eccentric sleeve 120 is arranged to have the maximum amount of eccentricity. Thus the piston reciprocates at the maximum stroke length Lmax and the compressor according to the invention has a maximum compression capacity.

On the other hand, when the crankshaft 23 temporarily stops to rotate in the reverse direction, since the elastic force is greater than the centrifugal force, the elastic member 140 elastically recovers the fixing member 130 into the mounting portion 111 of the crank pin. Return Thereafter, when the crankshaft 23 and the crank pin 110 integrated therein start to rotate in the opposite direction, that is, counterclockwise, the eccentric sleeve 120 is disposed between the crank pin 110 and the connecting rod 33. It is arranged as shown in Fig. 7a with relative rotation in the opposite direction, ie forward direction. As in the forward rotation, when the rotational angular velocity reaches a predetermined level, as shown in FIG. 7B, the fixing member 130 protrudes by the centrifugal force F to engage the thin thickness side groove 122, and the eccentric sleeve A fixing state is made through the fixing member 130 between the 110 and the crank pin 110. Therefore, in the reverse rotation, even if the external force P and any other force due to the pressure applied by the working fluid to the piston during the compression process, the relative rotation between the crank pin 110 and the eccentric sleeve 120 can be prevented. . On the other hand, as shown in Figure 7b, it is understood that the compressor has a minimum compression capacity since the eccentric sleeve 120 is arranged to have a minimum amount of eccentricity in the reverse rotation.

Second embodiment

The second embodiment of the present invention has a different fixing member shape and its mounting structure as compared with the first embodiment described above as a whole.

For this second embodiment, FIGS. 8A and 8B are side and top views showing a second embodiment of a dual displacement compressor according to the invention, and FIGS. 9-10 show the main components separately. Herein, the respective components are shown assembled together with each other, including some cross sections, for ease of explanation and clarity as in the first embodiment. Referring to the drawings, a second embodiment of the present invention will be described in detail.

The dual capacity compressor according to the second embodiment is a crank pin 210 having a fixing member mounting portion 211, an eccentric sleeve 220 rotatably mounted to the crank pin 210 and having a pair of grooves 221 and 222. And a fixing member 230 positioned in the mounting portion 211. In this second embodiment, the respective components are generally the same as in the first embodiment and are described next on the basis of the distinguishing features.

First, as shown in FIG. 8A, the crank pin 210 partially has a hollow shaft shape, and thus includes a pair of mounting portions 211a and 211b which are formed to face each other on the wall of the crank pin 210. do. In addition, the crank pin 210 includes an oil passage 212 and an oil supply hole 213 having the same shape and function as in the first embodiment.

The mounting portions 211a and 211b are located on an extension line between the centers 23a and 210a as shown in FIG. 8B and are arranged in the same horizontal plane as shown in FIG. 8A. Accordingly, the fixing member 230 in which each end is inserted into the mounting portion 211 is affected by the centrifugal force acting on the extension line between the centers 23a and 210a along its longitudinal direction, You will be guided and moveable. In practice, in the second embodiment, the mounting portions 211a and 211b are formed as through holes as shown in FIG. 9A, and preferably, at least one of the mounting portions 211a and 211b is shown in FIG. 9B. Likewise, the groove may extend from the upper end of the wall of the crank pin 210 to a predetermined position. By including the mounting portion 211a of the groove shape, the fixing member 230 may be easily mounted to the hollow tube crank pin 210. In addition, it is also preferable that the seat portion 211c is formed at the end of the groove-shaped mounting portion 211a in order to mount the fixing member 130 more stably.

The eccentric sleeve 220 includes a pair of grooves 221 and 222 into which the fixing member 230 is inserted. Since the eccentric sleeve 220 is substantially the same as the eccentric sleeve 120 of the first embodiment, a detailed description thereof will be omitted.

8A and 8B, the fixing member 230 continuously extends in the opposite direction to the first protrusion 231 and the first protrusion 231 protruding out of the crank pin 210 during operation. And a second protrusion 232 which is always located inside the crank pin 210. The fixing member 230 also includes a stopper 233 that defines the protruding length of the second protrusion 232. In practice, the first protrusion 231 is disposed in the crank pin 210 away from the crankshaft center 22a in order to be greatly influenced by the centrifugal force, and the second protrusion 232 is relatively disposed at the center ( Adjacent to 22a).

More specifically, the first protrusion 231 protrudes from the mounting portion 211b by a centrifugal force generated during rotation and is inserted into one of the grooves 221 and 222. In this case, the elastic member 240 is inserted into the first protrusion 231 to return the protruding fixing member, that is, the first protrusion 231 when the operation stops, and the stopper 233 and the crank pin 210 are actually used. It is located between the inner walls. In addition, the first protrusion 231 should have a length at which the end does not protrude to the outer circumferential surface of the crank pin 210 so as not to interfere with the rotation of the eccentric sleeve 220 for the change of the eccentric amount.

The second protrusion 232 is always located in the mounting portion 211a so that the fixing member 230 is not separated from the crank pin 210 regardless of the compressor operating state (stop or operation). To this end, the stopper 233 itself defines the protruding length of the second protrusion 232 to the outside of the crank pin 210, the elastic member 240 also the stopper together with the inner wall of the crank pin 210 Resilient support of 233 restricts crank pin 210 central movement of the second protrusion 232.

Meanwhile, as shown in FIG. 10, the stopper 233 includes a contact surface 233a having a shape coinciding with the inner circumferential surface of the crank pin 210, and preferably, a receiving portion of the elastic member 240. 233b may be further included. The contact surface 133a and the receiving portion 233b substantially assist the stable operation of the fixing member 230 according to the second embodiment. In addition, the stopper 233 may be formed integrally with the fixing member 130 or may be formed as a separate member.

The operation of the present invention according to the second embodiment described above is described next with reference to the associated drawings. 11A and 11B show the operation of the first embodiment in the forward rotation and FIGS. 12A and 12B show the operation of the second embodiment in the reverse rotation. Here, a detailed description of the initial arrangement process of the eccentric sleeve 210 in each rotation direction is the same as in the first embodiment, and thus will be omitted.

First, the centrifugal force (F) acts on the fixing member 230 during the forward rotation of the crankshaft (23), when the predetermined angular velocity or more, the centrifugal force (F) overcomes the elastic force of the elastic member (240). At this time, when the eccentric sleeve 210 is arranged as shown in FIG. 11A, the first protrusion 231 of the fixing member 230 is separated from the restraint by the inner circumferential surface of the eccentric sleeve 220, and thus, FIG. 11B. It is inserted into the thick thickness side groove 221 as shown. 12A and 12B, the first protrusion 231 is inserted into the thin side groove 222 through the same process as in the previous forward rotation, as shown in FIGS. 12A and 12B. On the other hand, since the elastic force is greater than the centrifugal force during the switching of the rotation direction (forward rotation or forward rotation in reverse rotation), the elastic member 240 pushes the stopper 233 to the crank pin 210 inner wall to The first protrusion 231 is returned into the mounting portion 211b of the crank pin.

Thus, the crank pin 210 and the eccentric sleeve 220 are completely fixed to each other and the external force (P) and any other force is applied in all directions of rotation or a local rotation moment is generated in the eccentric sleeve (220) Even in this case, the relative rotation between the crank pin 210 and the eccentric sleeve 220 is prevented as in the first embodiment. As a result, the compressor according to the invention ensures the stability of operation while maintaining the respective maximum and minimum compression capacity in any operating state, ie forward or reverse rotation.

Although several embodiments have been described above, it will be apparent to those skilled in the art that the present invention may be embodied in many other forms without departing from the spirit and scope thereof. Accordingly, the described embodiments are to be considered as illustrative and not restrictive, and all embodiments within the scope of the appended claims and their equivalents are included within the scope of the present invention.

In the present invention, the crank pin on which the fixing member is located is also completely constrained with the eccentric sleeve by inserting the fixing member into the eccentric sleeve during operation. Therefore, even if any external or internal factors occur, the relative motion is prevented between the eccentric sleeve and the crank pin, so that the compressor operates stably without changing the output. More specifically, the constant amount of eccentricity is maintained so that the designed amount of compression is constant. In addition, friction loss between the crank pin and the eccentric sleeve due to relative rotation is prevented. As a result, this stable operation results in an increase in the double capacity compressor efficiency. In addition, noise generated during relative rotation is prevented, and the life of each component can also be increased. On the other hand, since the structure of the present invention is substantially simple and its assembly is easy, productivity can be improved.

Claims (16)

A power generator including a motor capable of reverse rotation with respect to a predetermined rotation direction and a crank shaft inserted into the motor; A compression unit including a cylinder of a predetermined size, a piston located in the cylinder, and a connecting rod connected to the piston; A crank pin formed eccentrically at an upper end of the crankshaft; An inner circumferential surface rotatably coupled to an outer circumferential surface of the crank pin and an outer circumferential surface rotatably coupled to an end of the connecting rod, and being rearranged according to the rotational direction of the motor to change an effective amount of eccentricity between the crank pin and the connecting rod. Eccentric sleeves; And Located in the crank pin and consisting of a fixing member that completely constrains the eccentric sleeve to the crank pin in both clockwise and counterclockwise rotation of the motor, thereby varying the piston displacement by the respective varied effective eccentricity. And a compression capacity different from each other, and the relative motion of the crank pin and the eccentric sleeve is substantially prevented by the fixing member regardless of the rotational direction of the motor. The method of claim 1, And a mounting portion of the crank pin to movably receive the fixing member. The method of claim 2, And said crank pin has a solid shaft shape, and said fixing member mounting portion is a through hole formed along the radial direction of said solid shaft crank pin. The method of claim 2, And the crank pin has a hollow shaft shape, and the fixing member mounting portion is a pair of through holes formed to face the crank pin wall. The method of claim 4, wherein And the fixing member mounting portion includes a groove extending from a predetermined position of the crank pin wall to an upper end thereof. The method of claim 1, And the eccentric sleeve includes two grooves each extending radially from the inner circumferential surface toward the outer circumferential surface. The method of claim 6, And the two grooves are disposed opposite each other on an extension line passing through the center of the crank pin and the center of the eccentric sleeve. The method of claim 1, Wherein said holding member is positioned within said crank pin as a whole when at rest and at least a portion protrudes out of the crank pin to engage said eccentric sleeve during operation. The method of claim 8, And a length of the fixing member is smaller than the crank pin diameter. The method of claim 8, Dual-capacity compressor, characterized in that the cross section of the fixing member is any one of a polygon, such as a circle, a square, a hexagon. The method of claim 8, And the fixing member is a straight simple pin that protrudes out of the crank pin along the centrifugal force action direction in the solid crank pin. The method of claim 8, The fixing member is: A first protrusion projecting out of the crank pin in the centrifugal force direction during operation; A second protrusion formed in a direction opposite to the first protrusion and positioned in the mounting portion during operation; And And a stopper defining the length of the second protrusion so as not to protrude out of the crank pin. The method of claim 12, And a crank pin contact surface of the stopper has a shape coincident with the inner circumferential surface of the crank pin. The method of claim 1, And a resilient member for restoring the protruding fixed member into the crank pin during operation stop. The method of claim 14, And the elastic member is inserted into the grooves of the eccentric sleeve, respectively, when the fixing member in the form of a simple pin is used. The method of claim 14, And the elastic member is inserted into the first protrusion of the fixing member.