KR101008627B1 - Dual capacity compressor - Google Patents

Abstract

The present invention provides 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 eccentric sleeve having 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; A key member for completely restraining the eccentric sleeve to the crank pin in all rotational directions of the crankshaft; And a balance weight which moves the center of gravity of the eccentric sleeve to prevent the eccentric sleeve from being released from the key member by rotation, and the effective eccentric amount and the piston by rearranging the eccentric sleeve according to the rotational direction of the motor. Displacement is changed to provide a dual displacement compressor having different compression capacities and substantially preventing relative movement during operation between the crank pin and the eccentric sleeve by the key member regardless of the motor rotational direction.

Dual capacity, compressor

Description

Dual Capacity Compressor {DUAL CAPACITY COMPRESSOR}

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

2 is a schematic diagram illustrating 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 which 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;

5A is a side view of a dual displacement compressor in accordance with the present invention, including a partial cross section;

5B is a plan view of a dual displacement compressor in accordance with the present invention, including a partial cross section;

6A is a perspective view of a crank pin of the present invention;

6B is a perspective view showing a modification of the crank pin of FIG. 6A;

7A is a perspective view of an eccentric sleeve of the present invention;

7B, 7C and 7D are plan, side and perspective views, respectively, showing variants of an eccentric sleeve according to the invention;

8 is a perspective view showing a first embodiment of a key member according to the present invention;                 

9 is a plan view showing a modification of the key member of FIG. 8 mounted in the crank pin;

10A and 10B are perspective views showing a first embodiment of a key member having a detachable first stopper;

11A-11C are plan views illustrating a first embodiment of a key member having a second stopper;

12 is a plan view showing a modification of the elastic member applied to the first embodiment of the key member;

13A and 13B are plan views showing the operation of the double displacement compressor to which the first embodiment of the key member is applied in clockwise rotation;

14A and 14B are plan views showing the operation of the double displacement compressor according to the present invention to which the first embodiment of the key member is applied in the counterclockwise rotation;

15A and 15B are plan views respectively showing the correlation of forces occurring in an eccentric sleeve to which the first embodiment of the key member is applied during clockwise rotation and counterclockwise rotation;

16A-16C show a side view and a plan view, including a partial cross section, of a dual displacement compressor according to the present invention to which a second embodiment of a key member is applied;

17 is a side view showing a second embodiment of a key member according to the present invention;

18 is a plan view showing a modification of the key member according to the second embodiment mounted in the crank pin;

19A-19C are plan views showing a key member according to a second embodiment with a second stopper;                 

20 is a plan view showing a modification of the elastic member applied to the second embodiment of the key member;

21A and 21B are plan views showing the operation of the double displacement compressor to which the second embodiment of the key member is applied in the clockwise rotation;

22A and 22B are plan views showing the operation of a modification of the double displacement compressor to which the second embodiment of the key member is applied in the counterclockwise rotation;

23A and 23B are plan views respectively showing the correlation of forces occurring in the eccentric sleeve to which the second embodiment of the key member is applied during clockwise rotation and counterclockwise rotation;

24 is a perspective view showing a modification of the eccentric sleeve having a balance weight; And

25A and 25B are plan views respectively illustrating the correlation of forces occurring in an eccentric sleeve having a balance weight during clockwise rotation and counterclockwise rotation.

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 in which the compression capacity is changed according to the rotation direction.

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.

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 in 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 eccentric sleeve having 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; A key member for completely restraining the eccentric sleeve to the crank pin in all rotational directions of the crankshaft; And a balance weight which moves the center of gravity of the eccentric sleeve to prevent the eccentric sleeve from being released from the key member by rotation, and the effective eccentric amount and the piston by rearranging the eccentric sleeve according to the rotational direction of the motor. Displacement is changed to provide a dual displacement compressor having different compression capacities and substantially preventing relative movement during operation between the crank pin and the eccentric sleeve by the key member regardless of the motor rotational direction.

By the present invention described above, the relative rotation between the crank pin and the eccentric sleeve is prevented, thereby achieving a stable operation of the compressor and an increase in efficiency.

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 100 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, so the additional description thereof will be omitted and the stroke variable unit 100 will be described in detail as follows.

As illustrated in FIG. 5A, the stroke variable part 100 may be formed between the crank pin 110 and the outer circumferential surface of the crank pin 110 and the connecting rod 33 which are eccentrically formed at the upper end of the crank shaft 23 as a whole. And an eccentric sleeve 120 rotatably mounted to the key member 130 installed in the crank pin 110. Here, the key member 130 serves to fix the crank pin 110 and the eccentric sleeve 120 to each other during the operation of the compressor. In this stroke variable portion 40, the eccentric sleeve 120 is rotated between the connecting rod 33 and the crank pin 110 so that the effective eccentricity thereof changes according to the rotation direction (forward or reverse direction) of the motor. Are arranged. And the key member 130 is caught by the eccentric sleeve 120 so that this changed effective eccentric amount is maintained. Therefore, when the rotational direction of the motor is changed by the stroke variable portion 40, the stroke length and the piston displacement of the connecting rod are basically changed according to the change of the effective eccentricity, and thus the compression capacity is also changed. The stroke variable portion 100 of the present invention outlined above is described in more detail below with reference to the associated drawings.

5A and 5B are side and cross sectional views 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. And Figures 6A-12 show the individual components individually.

First, as shown in FIG. 5A, the crank pin 110 has a partially hollow tubular shape, and the inner space formed by the hollow tube shape allows the key member 130 to be movable. The crank pin 110 also has a pair of key member mounting portions 111 formed to face each other, and includes an oil passage 112 and an oil supply hole 113 formed at the bottom thereof.                     

The mounting portions 111a and 111b are respectively formed in the hollow tube portion so as to be arranged in a vertical plane including the crankshaft center 23a and the crank pin center 110a as shown in FIGS. 5A and 6A. Accordingly, the key member 130 located in the mounting portions 111a and 111b is affected by the centrifugal force F acting on the extension line between the centers 23a and 110a in its longitudinal direction. In addition, the key member 130 is movable by being guided by the mounting parts 111a and 11b by the centrifugal force (F). Such mounting portions 111a and 111b may be formed as through holes, as shown in FIG. 6A. Therefore, the detachment of the key member 130 during operation may be prevented by the mounting portion 111 which is a through hole. Preferably, at least one of the mounting portions 111a and 111b may be a groove extending from an upper end of the wall of the crank pin 110 to a predetermined position, as shown in FIG. 6B. By including the groove-shaped mounting portion, the key member 130 can be easily mounted to the crank pin (110). Further, in order to mount the key member 130 more stably, it is also preferable that the seat 111c is formed at the end of the mounting part of the groove shape.

Referring to FIG. 5A, the oil passage 112 communicates with an oil groove formed outside the crankshaft 23 and communicates with the oil supply hole 113. The oil supply hole 113 is formed along a direction perpendicular to an extension line (that is, an extension line between the centers 23a and 110a) connecting the mounting portions 111a and 111b. During operation, the lubricant contained in the bottom of the compressor is first scattered to be supplied to the contact surface between the parts through the oil groove and the oil passage 112 to prevent wear and smooth operation of the parts. 113 may be directly supplied between the crank pin 110 and the eccentric sleeve 120. Preferably, the crank pin 110 is formed higher than the eccentric sleeve 120 so that the lubricating oil can be scattered at a high position and evenly supplied to each driving unit.

The eccentric sleeve 120 basically has an inner circumferential surface rotatably coupled to the outer circumferential surface of the crank pin 110 and an outer circumferential surface to which the ends of the connecting rod 33 are rotatably coupled. In more detail, as shown in FIG. 7A, the eccentric sleeve 120 has a track portion 121 formed along the extending direction of the body itself and a restricting portion 122 formed relative to the track portion 121. ). In addition, two boundary ends 123a and 123b are formed between the continuous track portion 121 and the restricting portion 122, respectively. At least a portion of the key member 130 protrudes to be caught by the eccentric sleeve 120, as shown in FIG. 5A, so that the raceway 121 is eccentric sleeve 120 with respect to the key member 130. Enable their relative rotational movement. That is, the eccentric sleeve 120 may rotate around the crank pin 110 as much as the range of the track portion 120. In addition, the limiting part 122 limits the rotational movement of the sleeve itself together with the key member 130 during stop and operation, as opposed to the track part 121. Substantially, the key member 130 is caught by the boundary ends 123a and 123b.

In the eccentric sleeve 120, the track portion 121 may be a cutout extending in the circumferential direction to a predetermined depth from the upper end of the eccentric sleeve 120. The boundary ends 123a and 123b are formed to be parallel to an extension line between the crankshaft center 23a and the crank pin center 110a as shown in FIGS. 5B and 7B. That is, the boundary ends 123a and 123b are formed to be substantially parallel to the extension line between the maximum thickness and the minimum thickness of the eccentric sleeve 110 and have different widths. Coincide with the extension line between (23a, 110a). In other words, the boundary ends 123a and 123b are located together on any extension line parallel to the extension line of the centers 23a and 110a. Thus, the key members 130 arranged on the same extension line may be caught by both of the boundary ends 123a and 123b, and the boundary ends 123a and 123b are substantially common to the key members 130. Form a contact surface. The boundary ends 123a and 123b are preferably spaced apart from the extension line between the centers 23a and 110a by half the thickness t of the key member 130. Accordingly, the key member 130 is more stably and accurately engaged with the boundary ends 123a and 123b. On the other hand, the boundary ends 123a and 123b may be formed to be inclined at the same predetermined angle with respect to the extension line between the centers 23a and 110a, respectively. More specifically, the boundary ends 123c and 123d are formed along a radial extension line of the crank pin center 110a inclined at a predetermined angle θ with respect to the extension line between the centers 23a and 110a. Can be. In addition, the boundary ends 123e and 123f may be formed to be further inclined at a predetermined angle toward the limiting part 122 at the intersection with the inner circumferential surface of the crank pin 110. In each of these cases, the boundary ends 123c, 123d, 123e, and 123f may be engaged with each other by having at least common contact points with the key member 130. In addition, the track portion 121 may be a through hole extending along a circumferential direction at a predetermined depth from the upper end as shown in FIG. 7D as well as the cutout of FIG. 7A. The track portion 121, which is a through hole, restrains the key member 130 so as not to be separated in the vertical direction.

In addition, the eccentric sleeve 120 may further include an oil supply hole 124 formed to face each other at a predetermined height as shown in FIG. 7C. The oil supply hole 124 is formed as a through hole symmetrically positioned with respect to the extension line between the centers 23a and 110a, and the oil supply of the crank pin when the key member 130 is caught in the eccentric sleeve 110 In communication with the ball 113. Accordingly, any one of the two oil supply holes 124 communicates with the oil supply hole 113 regardless of the rotational direction during the operation of the compressor, and lubricating oil is also supplied between the eccentric sleeve 120 and the connecting rod 33. Can be. In addition, an oil groove 124a having a predetermined depth is formed around the oil supply hole 124. The oil groove 124a forms a preliminary space for diffusing the supplied lubricating oil around the oil supply hole 124 so that lubricating oil can be easily supplied between the eccentric sleeve 120 and the connecting rod 33. 7A, the eccentric sleeve 120 may further include seat portions 125 formed at the boundary ends 123a and 123b, respectively. The seat 125 receives the key member 130 when the key member 130 is caught in the eccentric sleeve 110. In addition, the seat portion 125 may be a groove formed substantially over the boundary ends 123a and 123b, so as to coincide with a cross section of a portion contacting the boundary end 123 of the key member 130. It is preferably formed. Therefore, the key member 130 may be stably hung on the eccentric sleeve 120 by the seat 125. In addition, the key member 130 is in surface contact with the eccentric sleeve 120 instead of point contact due to the seat 125. Therefore, even when the key member 130 and the eccentric sleeve 120 are continuously and repeatedly contacted during the operation of the compressor, the key member 130 and the eccentric sleeve 120 are not damaged by stress concentration and the resulting fatigue. . In addition, as illustrated in FIGS. 5A and 7C, a ring member 126 may be installed between the eccentric sleeve 120 and the crankshaft 23. Since the ring member 126 and the eccentric sleeve 120 are in line contact with each other, the friction force between them is significantly reduced, so that the eccentric sleeve 120 can rotate more smoothly.

5A, 5B and 8 show a first embodiment of a key member according to the invention. As illustrated, the key member 130 according to the first embodiment basically includes a first protrusion 131 protruding to the outside of the crank pin 110 by a predetermined length even when the operation stops, and the crank pin during operation. 110) a second protrusion 132 protruding to a predetermined length to the outside. The key member 130 also includes a first stopper 133 that defines the protruding length of the first protrusion 131. In addition, the elastic member 140 is installed in the key member 130 to adjust the position of the key member 130 during the compressor stop and operation. In the present invention, the key member 130 restrains the eccentric sleeve 120 while moving by centrifugal force. In particular, as mentioned above, the second protrusion 132 protrudes during operation to serve to restrain the eccentric sleeve 120. The second protrusion 132 must face the same direction as the centrifugal force acting direction in order to protrude by the centrifugal force generated during operation. Thus, the second protrusion 132 is located relatively radially outward of the crankshaft 23 and crank pin 110 as shown, while the first protrusion 131 is located radially inward. . In other words, the second protrusion 132 is actually disposed in the crank pin 110 away from the crankshaft center 23a so as to be greatly influenced by the centrifugal force, and the first protrusion 131 is relatively It is disposed adjacent to the center 23a. In addition, it is preferable that the key member 130 has a length greater than the outer diameter of the crank pin 110 in order for the first and second protrusions 131 and 132 to be caught simultaneously with the eccentric sleeve 120 during operation of the compressor. .

In more detail, as shown in FIG. 5A, the first protrusion 131 protrudes out of the crank pin 110 regardless of the compressor operating state (stop or operation) by the elastic force of the elastic member 140. It meshes with either one of the boundary ends 123a and 123b. This engagement state is continuously maintained even during operation of the compressor. To this end, the elastic member 140 is mounted on the second protrusion 132 to elastically support the first stopper 133 together with the inner wall of the crank pin 110. The protruding length of the first protrusion is limited by the first stopper 133 positioned on the key member 130 being caught by the inner wall of the crank pin 110. In this case, the protruding length of the first protrusion 131 may have a size of at least half of the minimum width of the boundary ends 123a and 123b for more stable operation. In addition, as mentioned above, since the first protrusion 131 is located relatively radially inward of the crankshaft 23 and the crank pin 110, the first protrusion 131 is radially inward, that is, the It continuously projects toward the center 23a of the crankshaft. Thus, the key member 130 is always caught by at least a portion of the eccentric sleeve 120 located relatively radially inward of the crankshaft 23.

The second protrusion 132 protrudes in the opposite direction of the first protrusion 130 and engages with the other boundary of the operation. Accordingly, the first and second protrusions 131 and 132 of the key member 130 are caught simultaneously with the eccentric sleeve 120 during operation. The centrifugal force generated along the key member 130 during operation increases gradually as the number of revolutions of the crankshaft 23 increases, and becomes greater than the elastic force of the elastic member 140. Accordingly, the second protrusion 130 is moved and protrudes in the centrifugal force direction (that is, the extension line direction between the centers 23a and 110a). Here, when the rotation direction of the compressor is converted, the eccentric sleeve 120 rotates around the crank pin 110 to change the amount of eccentricity. Therefore, the second protrusion 132 should have a length that does not protrude to the outer circumferential surface of the crank pin when the operation stops so as not to interfere with the rotational movement of the eccentric sleeve 120.

The first and second protrusions 131 and 132 are alternately engaged with the boundary ends 123a and 123b according to the rotational direction of the crankshaft. The key member 130 is arranged on an extension line between the centers 23a and 110a or at least parallel to the extension line so that if the thicknesses t1 and t2 of the first and second protrusions 131 and 132 are different from each other, The contact position with the boundary ends 123a and 123b is not constant. Therefore, the thicknesses t1 and t2 of the first and second protrusions 131 and 132 must have the same thickness in order to accurately engage the boundary ends 123a and 123b. In addition, the cross section of the key member 130 is described and illustrated with respect to the circle in the present invention, it may be any shape that can be engaged with the boundary end (123a, 123b), such as square and hexagon.

As shown in FIG. 9, the contact surface 133a of the first stopper 133 may have a shape that matches the inner circumferential surface of the crank pin 100. Accordingly, the key member 130 can be accurately engaged with the crank pin 110, and the smoother operation due to the increased self weight (i.e., the easy protrusion of the second protrusion 132 due to the increase in centrifugal force). This is done. Preferably, the first stopper 133 may further include a recess 133b for stably accommodating the elastic member 140. These contact surfaces 133a and recesses 133b substantially assist the stable operation of the key member 130. Meanwhile, the first stopper 133 may be integrally formed with the key member 130 or may be formed as a separate member to be mounted on the key member 130. Examples of such a detachable first stopper 133 are shown in FIGS. 10A and 10B.

First, the first stopper 133 may include a protrusion 133a extending radially inward as shown in FIG. 10A. Accordingly, the first stopper 133 is coupled to the key member 130 by being inserted into the circumferential groove in which the protrusion 133a is formed at a predetermined position. In addition, as shown in FIG. 10B, the first stopper 133, which is a simple ring member, may be fixed by a fixing member at a predetermined position of the key member 130. This detachable stopper 133 allows the key member 130 to be mounted in the crank pin 130 even when the key member mounting portions 111a and 111b are both through holes. More specifically, first, the stopper 133 is positioned in the crank pin 110, and the remaining key member 130 is inserted through the through holes to be coupled with the stopper 133.

On the other hand, in the key member 130, the protruding length of the second protrusion 132 is adjustable by the elastic force of the elastic member 140 during normal operation, as described above. However, when the compressor starts to operate, the crankshaft 23 and the crank pin 110 are accelerated abnormally sharply, so that a very large instantaneous centrifugal force can be applied to the key member 130. Due to the centrifugal force, the second protrusion 132 may protrude excessively, and the first protrusion 131 may be separated from the mounting portion 111. Accordingly, the key member 130 may further include a second stopper 134 for limiting the length of protrusion of the second protrusion 133 to the outside of the crank pin 110 in the centrifugal force action direction.

As shown in FIG. 11A, the second stopper 134 may be a hollow tubular member 134a installed to be movable in the longitudinal direction on the second protrusion 132. In this case, the elastic member 140 is interposed between the second stopper 134a and the second protrusion 132. The second stopper 134a is configured such that when the key member 130 moves in the centrifugal force direction, the second stopper 133 does not protrude for a predetermined length by contacting the inner wall of the first stopper 133 and the crank pin 110, respectively. do. As shown in FIG. 11B, the second stopper 134 may be an extension 134b having a thickness greater than at least the thickness of the second protrusion 133. That is, the second stopper 134b of FIG. 11B is substantially formed as a longitudinal extension of the first stopper 133. In this case, the elastic member 140 is installed on the outer circumferential surface of the second stopper 134b. In addition, the second stopper 134 may be a radial extension 134c of the second protrusion having a predetermined thickness, as shown in FIG. 11C, and is substantially similar in shape to the first stopper 133. Has The elastic member 140 is installed between the radially extending portion 134c and the inner circumferential surface of the crank pin 110. Each of the second stoppers 134b and 134c may be fixed to the key member 130 as a separate member, similar to the modification of the first stopper 133 described above with reference to FIGS. 10A and 10B.

Alternatively, instead of the second stopper 134, the elastic member 140 may move the key member 130, precisely, the second protrusion 132, as shown in FIG. 12. It may also be configured to restrict. To this end, the elastic member 140 has a non-uniform spring constant, so that some of the elastic member 140 has a relatively large elastic modulus compared to other parts. Thus, the elastic member 140 is relatively less deformed during operation of the compressor, which substantially reduces the protruding length of the second protrusion 132. Thus, even if an abnormally large centrifugal force is applied, the protrusion of the second protrusion 132 is considerably suppressed to prevent the key member 130, particularly the first protrusion 131, from being separated from the crank pin 110. More preferably, even when a part of the elastic member 140 has the maximum centrifugal force generated in the key member 130, the first protrusion 131 is displaced in a range not to be separated from the crank pin 110. In the case of having a large modulus of elasticity so as to occur, excessive protrusion of the second protrusion 132 may be completely prevented.

Referring to FIG. 12, the elastic member 140 may include a first elastic member 141 having a predetermined elastic modulus and a second elastic member 142 having a larger elastic modulus than the first elastic member 142. It includes. Here, the first elastic member 141 is in contact with the first stopper 133 so as to continuously project the first protrusion 131. The second elastic member 142 may likewise protrude the first protrusion 131 and may be deformed together with the first elastic member 141 to be in contact with the first elastic member 141 and the crank pin ( It is supported by the inner peripheral surface of 110. More specifically, as shown in the figure, when the elastic member 140 is in the form of a spring, the first elastic member 141 is a spring having a predetermined diameter. The second elastic member 142 is continuously formed from the first elastic member 141 and has a larger diameter than the first elastic member 141 so as to have the larger spring constant, that is, the elastic modulus. Becomes As described above, the second elastic member 141 has the first protrusion 131 even when the centrifugal force applied to the key member 130 is maximum to completely prevent excessive protrusion of the second protrusion 142. It is desirable to have a large modulus of elasticity so that displacement occurs in a range where the c) does not deviate from the crank pin 110. That is, in this case, only the first elastic member 141 is deformed and the second elastic member 142 is not deformed by centrifugal force. Thus, similar to the second stopper 134, the second elastic member 142 prevents excessive movement of the key member 140. Since the elastic member 140 prevents the key member 130 from being separated without the second stopper 134, the structure of the key member 130 is simplified and its assembly is also easy.

In summary, the key member 130 is basically movably mounted in the crank pin 110 and has a length that is at least a predetermined size larger than the diameter of the pin 110. The key member 130 has at least a portion (that is, the first protrusion) protrudes out of the crank pin 110 even when the operation stops, and another portion (the second protrusion) protrudes by the centrifugal force during operation. That is, the key member 130 is continuously caught at least a portion of the eccentric sleeve 120, and is configured to additionally be caught by the eccentric sleeve 120 during operation. Accordingly, the key member 130 is in contact with the eccentric sleeve 120 at a plurality of points, and more specifically, in contact with both ends of the eccentric sleeve 120 set based on an arbitrary center line. Done. As a result, the key member 130 is completely engaged with the crank pin 120 that rotates the eccentric sleeve 120 even in any rotational direction of the motor, thereby preventing relative rotation due to mutually generated rotation moments.

The operation of the double displacement compressor according to the invention described above is described next with reference to the associated drawings. 13A and 13B show the operation in the clockwise rotation and FIGS. 14A and 14B show the operation in the reverse rotation.

First, FIG. 13A shows the relative position between the key member 130 and the eccentric sleeve 120 when the crankshaft 23 begins to rotate in the forward direction, ie clockwise. As described above, the first protrusion 131 always protrudes outwardly of the crank pin 110 by its elastic force in its radially inward direction. When the crankshaft 23 starts to rotate clockwise while the first protrusion 131 is protruded, the crank pins, the eccentric sleeve and the key members 110, 120, and 130 are clockwise around the crankshaft center 23a. To start spinning. During this idle, the relative friction force f is generated between the crank pin 110 and the connecting rod 33 in the direction opposite to the rotation direction. Accordingly, the eccentric sleeve 120 rotates counterclockwise around the crank pin center 110a due to this frictional force f, and the thin thickness side boundary end 123b thereof protrudes from the first protrusion 131. Takes on Once the crankshaft 23 is rotated, the friction force f is continuously generated during the rotation of the crankshaft 23, so that the engagement between the first protrusion 131 and the boundary end 123b is maintained. . At this time, when the rotational angular velocity reaches a certain level, the key member 130 is moved along its extension direction between its center of action (23a, 110a) by the centrifugal force (F) as shown in Figure 13B. Accordingly, the second protrusion 132 is engaged with the thick thickness side boundary end 123a, and the first protrusion 131 also maintains contact with the boundary end 123b at the same time. This simultaneous multi-point contact causes the key member 130 to fully engage the eccentric sleeve 120. 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. 13B, 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, an eccentric sleeve 120 is connected to the connecting rod 33 (not shown). And crank pin 110 are arranged to produce a 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 starts to rotate in the opposite direction, that is, counterclockwise, the relative friction force f between the crank pin 110 and the connecting rod 33 is opposite to the rotational direction, that is, clockwise. Is caused by. The eccentric sleeve 120 rotates clockwise around the crank pin center 110a from the position shown in FIG. 13A, and as shown in FIG. 14A, a thick thickness side boundary end 123a is formed in the first protrusion ( 131). Similarly, the engagement between the first protrusion 131 and the boundary end 123a is maintained by the friction force f during the rotation of the crankshaft 23. As in the forward rotation, when the rotational angular velocity reaches a predetermined level, as shown in FIG. 14B, the second protrusion 232 is engaged with the thin thickness side boundary end 123b by the centrifugal force F, and the eccentric sleeve A multi-point contact state is made between the 120 and the key member 130. 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. . In addition, as shown in Fig. 14B, in the case of the reverse rotation, since the eccentric sleeve 120 is arranged to have the minimum amount of eccentricity, the piston reciprocates at the minimum stroke length Lmin, and the compressor according to the present invention has the minimum compression capacity.

As a result, the compressor according to the present invention is free of any operating state, i.e., by completely excluding the relative rotation between the crank pin 110 and the eccentric sleeve 120 by the key member 130. It can operate stably even in forward or reverse rotation.

On the other hand, as shown in FIGS. 15A and 15B, the eccentric sleeve 120 has a center of gravity G biased for structural reasons. That is, the center of gravity G is located towards the heavier limiting portion 122. The centrifugal force (C) acts along the extension line between the center of gravity (G) and the center (23a) of the crankshaft in the center of gravity (G) of the eccentric sleeve (120) during the rotation of the crankshaft (23). Since the center of gravity G is deflected, the centrifugal force C generates a rotation moment M with respect to the crank pin center 110a. More specifically, as shown, the rotation moment M is represented by the product of the centrifugal force C and the arm length d to the center of the crank pin 110a. This rotation moment (M) acts in the same direction as the rotation direction of the crankshaft (23). That is, as shown in FIG. 15A, a rotation moment in the clockwise direction is generated in the eccentric sleeve 120 by the center of gravity G during clockwise rotation, and as shown in FIG. 15B, counterclockwise. The counterclockwise rotation moment is generated during rotation. As described above, the friction force f rotates the eccentric sleeve 120 in the direction opposite to the rotational direction to be caught by the first protrusion 131, while such rotation moment M is the eccentric sleeve. There is a tendency to rotate 120 in the direction of rotation of the compressor. Therefore, the eccentric sleeve 120 may be intermittently finely rotated by the rotation moment M, and thus may be released from the key member 130. The rotation of the eccentric sleeve 120 prevents the protrusion and latching of the second protrusion 132.

The second embodiment 230 of the key member is configured to prevent the rotation of the eccentric sleeve 120 due to this centrifugal force C / rotation moment M. As shown in FIG. This key member 230 is shown in detail in FIGS. 16A-16C and 17.

As shown, the key member 230 according to the second exemplary embodiment basically includes a first protrusion 231 and a second protrusion 232 which always protrude to a predetermined length out of the crank pin 110 during operation. Include. The second protrusion 232 is not caught by the eccentric sleeve 120 when the compressor is stopped, and is moved by the eccentric sleeve 120 during the operation of the compressor. In addition, the key member 230 also includes a first stopper 233 that restricts movement in either direction thereof. The first stopper 233 limits the radially inward movement of the second protrusion 232 and thus the protrusion length. In addition, the elastic member 140 is installed on the key member 230 to adjust the position of the key member 230 as in the first embodiment. As shown in FIGS. 15A and 15B, the eccentric sleeve 120 rotates by the centrifugal force C and the rotation moment M, so that the key member 130 is radially outward of the eccentric sleeve 120. It gets hard with some. Accordingly, it is preferable that the key member 230 according to the second embodiment is continuously caught from the start of the operation of the compressor and a portion of the eccentric sleeve 120 located relatively outward of the crankshaft 23. The first protrusion 231 continuously protruding for this purpose is located radially outward of the crankshaft 23 and the crank pin 110 as shown, while the second protrusion 232 is radially outward. It is located inside. In other words, the first protrusion 231 is actually disposed in the crank pin 110 away from the crankshaft center 23a in order to prevent the rotation of the eccentric sleeve 120, and relatively the second protrusion 131 is disposed adjacent to the center 23a.

More specifically, the first protrusion 231 has a predetermined length so as to continuously protrude out of the crank pin 110 as shown in FIG. 16A. In addition, as mentioned above, the first protrusion 231 relatively protrudes radially outwardly of the crankshaft 23 and the crank pin 110, and faces in the same direction as the centrifugal force action direction generated during operation. Accordingly, as shown in FIG. 16C, the first protrusion 231 further protrudes radially outward by centrifugal force during operation, whereby the engagement with the eccentric sleeve 120 is continuously maintained even during operation of the compressor.

The second protrusion 232 protrudes out of the crank pin 110 in the opposite direction to the first protrusion 231 by the elastic force of the elastic member 140. To this end, the elastic member 140 is mounted on the first protrusion 231 to elastically support the first stopper 233 together with the inner wall of the crank pin 110. The protruding length of the second protrusion 232 is limited by the first stopper 233 positioned on the key member 130 being caught by the inner wall of the crank pin 110. On the other hand, the eccentric sleeve 120 is rotated around the crank pin 110 to change the amount of eccentricity when the rotation direction of the compressor is converted. Therefore, the second protrusion 232 should protrude out of the crank pin 110 so that the second protrusion 232 is not caught by the eccentric sleeve 120 when the operation is stopped so as not to interfere with the rotational movement of the eccentric sleeve 120. More specifically, as shown, the second protrusion 232 includes a channel 232a for passing the eccentric sleeve 130. The width of the channel 232a is preferably formed to be slightly larger than the maximum width of the eccentric sleeve 130. Due to this formation of the channel 232a, the end 232b of the second protrusion is actually located outside of the eccentric sleeve 120. The centrifugal force F generated along the key member 230 during operation increases gradually as the number of revolutions of the crankshaft 23 increases, and becomes greater than the elastic force of the elastic member 140. By the centrifugal force F, the second protrusion 232 moves in the centrifugal force direction (that is, the extension line direction between the centers 23a and 110a), and as shown in FIG. 16C, the end of the second protrusion ( 232b is caught in the eccentric sleeve 120. Thus, during operation, the first and second protrusions 231 and 232 of the key member 230 are caught simultaneously with the eccentric sleeve 120.

The key member 230 according to the second embodiment may be applied to the dual displacement compressor of the present invention without deformation of the crank pin 110 and the eccentric sleeve 120. Since the crank pin 110 and the eccentric sleeve 120 are described with reference to FIGS. 6A-7D, further description is omitted and only additional features of the key member 230 are briefly described below.

As shown in FIG. 18, the first stopper 233 includes a contact surface 233a having a shape coincident with the inner circumferential surface of the crank pin 110, and preferably, a receiving portion of the elastic member 140. 233b may be further included. This contact surface 233a and the receiving portion 233b substantially assist the stable operation of the key member 230 according to the second embodiment. In addition, the first stopper 233 may be integrally formed with the key member 230 or may be formed as a separate member.

Protrusion and movement of the first and second protrusions 231 and 232 are adjustable by the elastic force of the elastic member 140 during normal operation. However, as mentioned above, the key member 230 may be released by the instantaneous centrifugal force, or in particular, the second protrusion 232 may not be accurately caught by the eccentric sleeve 120. In order to prevent such an abnormal operation of the key member 230, preferably, the key member 230 further includes a second stopper 234 for limiting its movement in the centrifugal force direction. As shown in Figs. 19A-19C, the second stopper 234 is formed in the same manner as in the first embodiment. That is, the second stopper 234 of the second embodiment is a hollow tubular member 234a (FIG. 19A) and a length of the first stopper 133, which are installed to be movable in the longitudinal direction on the second stopper 234, respectively. Directional extension 234b (Fig. 19B) or radial extension 234c (Fig. 19C) of the first protrusion 231 having a predetermined thickness.

In addition, the elastic member 140 having a non-uniform elastic modulus as shown in FIG. 20 in place of the second stopper 234 is the same as the first embodiment in the key member 230 according to the second embodiment. Can be applied. As shown in the drawing, the elastic member 140 includes a first elastic member 141 having a predetermined elastic modulus and a second elastic member 142 having a larger elastic modulus than the first elastic member 142. In practice, the first elastic member 141 is a spring having a predetermined diameter, and the second elastic member 142 is larger than the first elastic member 141 to have a larger spring constant, that is, an elastic modulus. It is a spring having a diameter. In order to completely prevent excessive movement of the key member 230, the second elastic member 141 may allow the first protrusion 131 to have the crank pin () even when the centrifugal force generated in the key member 130 is maximum. It has a large modulus of elasticity so that displacement occurs in a range that does not deviate from 110). The elastic member 140 restricts the movement of the key member 230 in the centrifugal force direction to prevent the key member 230 from being detached or caught by the eccentric sleeve. And by excluding additional parts such as the second stopper 234, the structure simplification and ease of assembly of the key member 130 are achieved.

The operation of a double displacement compressor with a key member according to the second embodiment described above is described next with reference to the associated drawings. 21A and 21B show the operation in the clockwise rotation and FIGS. 22A and 22B show the operation in the reverse rotation.

FIG. 21A shows the relative position between the key member 130 and the eccentric sleeve 120 when the crankshaft 23 begins to rotate in the forward or clockwise direction. As described above, the first protrusion 231 always protrudes outwardly of the crank pin 110 by its elastic force and radially outward thereof. When the crankshaft 23 starts to rotate clockwise while the first protrusion 231 is protruded, the crank pins, the eccentric sleeve and the key members 110, 120, and 130 are clockwise around the crankshaft center 23a. To start spinning. During this idle, a relative friction force f is generated between the crank pin 110 and the connecting rod 33 in a direction opposite to the rotation direction, that is, counterclockwise. Thus, the eccentric sleeve 120 begins to rotate counterclockwise around the crank pin center 110a due to this frictional force f. And the eccentric sleeve 120, precisely the limiting portion 122, passes through the channel 232a of the second protrusion so that its thin side edge 123b is caught by the protruding first protrusion 231. As shown in FIG. 23A, since the first protrusion 231 is caught by the eccentric sleeve 120 in a relatively radially outward position of the crankshaft, the center of gravity G of the eccentric sleeve 120 Is located opposite the center of gravity of FIG. 15A with respect to the line of action of the centrifugal force (extension line between centers 23a and 110a). Due to this center of gravity G, the centrifugal force C generates a rotation moment M in a direction opposite to the rotation direction (counterclockwise). Therefore, together with the friction force f acting in the same direction, this rotation moment M acts to rotate the eccentric sleeve 120 in a direction opposite to the rotation direction, that is, counterclockwise, so as to rotate the first protrusion 231. ) And the boundary between the edge 123b is kept stable. Then, when the rotational angular velocity reaches a certain level, the key member 130 is moved along its extension direction between the centers of action 23a and 110a by the centrifugal force F as shown in Fig. 21B. Accordingly, as described with reference to FIG. 16C, the end 232b of the second protrusion 132 is engaged with the thick thickness side boundary end 123a, and the first protrusion 131 is simultaneously with the boundary end 123b. Keep contact. As described above, since the locking of the first protrusion 231 is stably maintained by the rotation moment M in the opposite direction to the rotation direction, the second protrusion 232 smoothly covers the eccentric sleeve 120. Can take This simultaneous multi-point contact causes the key member 130 to fully engage the eccentric sleeve 120. 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. 21B, the solid line portion of the figure shows the top dead center state and the dotted line portion the bottom dead center state, respectively. In the case of forward rotation, the eccentric sleeve 120 is arranged to have the minimum amount of eccentricity. Thus the piston reciprocates at the maximum stroke length Lmin and the compressor according to the invention has a minimum compression capacity.

When the crankshaft 23 starts to rotate in the opposite direction, that is, counterclockwise, a relative friction force f is generated between the crank pin 110 and the connecting rod 33 in the opposite direction of the rotational direction, that is, clockwise. do. Thus, the eccentric sleeve 120 begins to rotate clockwise around the crank pin center 110a through the channel 232a from the position shown in FIG. 21A. Thereafter, the eccentric sleeve 120 is engaged with the first protrusion 131 where the thick thickness side boundary end 123a projects radially outward as shown in FIG. 22A. For the same reason as the clockwise rotation, as shown in FIG. 23B, the center of gravity G of the eccentric sleeve is located opposite the center of gravity of FIG. 15B with respect to the line of action of the centrifugal force. Accordingly, the centrifugal force C generates the clockwise rotation moment M opposite to the rotation direction, and the first protrusion 231 and the first projection 231 are caused by the friction force f and the rotation moment M acting in the same direction. The locking between the boundary ends 123a is kept stable. As in the forward rotation, when the rotational angular velocity reaches a predetermined level, the second protrusion 232 is engaged with the thin thickness side boundary end 123b by the centrifugal force F as shown in FIG. 22B, and the eccentric sleeve A multi-point contact state is made between the 120 and the key member 130. At this time, the second protrusion 232 may be smoothly caught by the eccentric sleeve 120 as in the clockwise rotation due to the stable locking of the first protrusion 231. Therefore, in the reverse rotation, even if the external force P and any other force caused by the pressure applied to the piston during the compression process are transmitted, the relative rotation between the crank pin 110 and the eccentric sleeve 120 can be prevented. have. In addition, as shown in Fig. 22B, in the case of the reverse rotation, the eccentric sleeve 120 is arranged to have the maximum amount of eccentricity, so that the piston reciprocates at the maximum stroke length Lmax and the compressor according to the present invention has the maximum compression capacity.

As a result, by using the key member 230 of the second embodiment, the compressor of the present invention can basically operate stably without completely removing the relative rotation between the crank pin 110 and the eccentric sleeve 120. In addition, the rotation of the eccentric sleeve 120 due to the centrifugal force (C) and the rotation moment (M) by the key member 230 is prevented, thereby the compressor of the present invention can have an operational reliability.

On the other hand, in order to solve the instability of the locking of the second protrusion 132 raised above with reference to FIGS. 15A and 15B, the eccentric sleeve 120 is rotated as shown in FIG. 24 by the key member 130. It may further include a balance weight 127 for moving its center of gravity so as not to be released from). Since the center of gravity G is biased by the limiting portion 122 as described above, the rotational moment M and the resulting force before the eccentric sleeve 120 is completely constrained by the key member 130. Rotation occurs. In order to move the center of gravity G, the weight of the relatively light portion of the eccentric sleeve 120 must be increased. The balance weight 127 has a considerable weight to move the center of gravity, is installed on the track portion 121 of the relatively eccentric sleeve. The balance weight 127 may be integrally formed with the eccentric sleeve 120, and may be mounted to the eccentric sleeve 120 as a separate member.

25A and 25B show an eccentric sleeve 120 with the balance weight 127 during clockwise and counterclockwise rotation, respectively.

As shown, this balance weight 127 causes the eccentric sleeve 120 to be preferably moved within the extension line between the center 23a of the crankshaft and the center 110a of the crankshaft. May have By the center of gravity G1, the centrifugal force F of the crankshaft 23 / crank pin 110 and the centrifugal force C1 of the eccentric sleeve 120 act on the same line of action. Thus, since there is no arm length between the center of gravity G1 and the crank pin center 110a, no rotation moment occurs in both clockwise rotation (FIG. 25A) and counterclockwise rotation (FIG. 25B). In addition, rotational rotation is also essentially prevented since no rotation moment is generated.

In addition, the eccentric sleeve 120 is moved by the balance weight 127 opposite the extension line between the center of gravity (23a) of the crankshaft and the center (110a) of the crankshaft from the initial center of gravity (G) It may have a center G2. Due to this center of gravity (G2) centrifugal force (C2) generates a rotation moment (M2) in the direction opposite to the rotational direction. That is, as shown in FIG. 25A, the center of gravity G2 generates a counterclockwise rotation moment M2 when rotated clockwise, and as shown in FIG. 25B, a clockwise rotation moment when rotated counterclockwise as shown in FIG. 25B. (M2) is generated. The rotation moment M2 acts to rotate the eccentric sleeve 120 in a direction opposite to the rotation direction together with the friction force f. Accordingly, the first protrusion 131 is stably engaged with the eccentric sleeve 120, thereby allowing the second protrusion 132 to smoothly engage with the eccentric sleeve 120.

As a result, the balance weight 127 is separated from the key member 130 of the eccentric sleeve 120 by the centrifugal force C / rotation moment M, similarly to the key member 230 of the second embodiment. This prevents release and improves the reliability of the compressor of the present invention. In addition, although the balance weight 127 is described and illustrated in combination with the first embodiment 130 of the key member, it can be used with the second embodiment 230 of the key member without modification.

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, basically, the crank pin provided with the key member is also completely restrained with the eccentric sleeve by the eccentric sleeve and the key member contacting each other at a plurality of points 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. In other words, 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.

In addition, the initial engagement between the key member and the eccentric sleeve is changed or the center of gravity of the eccentric sleeve is moved using the balance weight. Thus, the eccentric sleeve is not rotated by centrifugal force and rotational moment before it is completely constrained by the key member. Thus, the key member can stably and completely restrain the eccentric sleeve, thereby improving the reliability of the compressor according to the present invention.

In addition, the compressor of the present invention does not require additional components for the same function by using an elastic member configured to appropriately restrict the centrifugal movement of the key member. Therefore, the structure of the present invention can be substantially simplified and its assembly is easy, so productivity can be improved.

Claims (44)

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 eccentric sleeve having 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; A key member for completely restraining the eccentric sleeve to the crank pin in all rotational directions of the crankshaft; And A balance weight for moving the center of gravity of the eccentric sleeve to prevent the eccentric sleeve from being released from the key member by rotation; The effective eccentricity and piston displacement are changed by rearrangement of the eccentric sleeve according to the rotation direction of the motor to have different compression capacities, and the operation between the crank pin and the eccentric sleeve by the key member regardless of the motor rotation direction. Dual-capacity compressor that substantially prevents relative movement. The method of claim 1, And the key member restrains the eccentric sleeve at a plurality of points. The method of claim 1, Wherein said key member simultaneously constrains two points of said eccentric sleeve set relative to an arbitrary center line in operation. The method of claim 1, And the key member has a length greater than an outer diameter of the crank pin. The method of claim 1, And wherein the key member is at least part of the eccentric sleeve and configured to additionally be hung in the eccentric sleeve during operation. The method of claim 1, And the key member is hung on at least a portion of the eccentric sleeve, which is located relatively radially inward of the crankshaft. The method of claim 1, And a second protrusion protruding out of the crank pin by a predetermined length only during operation, and the key member continuously protruding out of the crank pin by a predetermined length. The method of claim 7, wherein And the first protrusion continuously protrudes radially inward of the crankshaft. The method of claim 1, And the key member is configured to prevent rotation of the eccentric sleeve due to centrifugal force and thus rotational moment. delete The method of claim 1, And the key member is hung on at least a portion of the eccentric sleeve that is located relatively outward of the crankshaft. The method of claim 1, Wherein the key member includes a first protrusion continuously protruding out of the crank pin and a second protrusion continuously protruding out of the crank pin and configured to engage the eccentric sleeve upon operation of the compressor. compressor. 13. The method of claim 12, And the first projection protrudes radially outwardly of the crankshaft. 13. The method of claim 12, And the second protrusion protrudes out of the crank pin so as not to be caught by the eccentric sleeve when the compressor is stopped. 13. The method of claim 12, And the second projection comprises a channel through which the eccentric sleeve passes during shutdown of the compressor. The method of claim 1, And a stopper in which said key member is located within said crank pin and limits its movement. The method of claim 16, 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 16, And the stopper is a first stopper for limiting one-way movement of the key member. The method of claim 18, And the second stopper further comprises a second stopper for limiting movement of the key member in the opposite direction. The method of claim 1, And the key member further comprises an elastic member for supporting at least a portion of the key member to continuously protrude out of the crank pin regardless of the compressor operating state. The method of claim 20, The elastic member is configured to limit movement in either direction of the key member The method of claim 20, And the elastic member has a non-uniform elastic modulus. The method of claim 20, And a part of the elastic member has a relatively large modulus of elasticity compared to other parts. The method of claim 20, The portion of the elastic member has a large modulus of elasticity so that the displacement occurs in a range that does not leave the protrusion of the key member formed radially inward even when the centrifugal force generated in the key member is maximum . The method of claim 20, The elastic member is: A first elastic member in contact with the key member; And And a second elastic member in contact with the inner circumferential surfaces of the first elastic member and the crank pin, respectively, and having a larger elastic modulus than the first elastic member. The method of claim 25, The second elastic member has a large modulus of elasticity so that the displacement occurs in a range that does not leave the protrusion of the key member formed radially inward even when the centrifugal force generated in the key member is maximum. . The method of claim 25, And the first elastic member is a spring having a predetermined diameter and the second elastic member is a spring continuously formed from the first elastic member and having a larger diameter than the first elastic member. The method of claim 1, And a pair of key member mounting portions in which the crank pins are formed to face each other. 29. The method of claim 28, And the key member mounting portion of the crank pin is a through hole formed in the crank pin wall. 29. The method of claim 28, And the key member mounting portion of the crank pin includes a groove extending from a predetermined position of at least one of the crank pin walls to an upper end thereof. The method of claim 1, The eccentric sleeve is formed along the extending direction of the body itself, and includes a track portion for enabling the rotational movement of the key member protrusion and a restricting portion formed relative to the track portion to limit the rotational movement of the key member protrusion. Dual capacity compressor, characterized in that. The method of claim 31, wherein The track portion of the eccentric sleeve is a double displacement compressor, characterized in that the incision extending in the circumferential direction from the upper end to a predetermined depth. The method of claim 31, wherein And a boundary end formed between the track portion and the restricting portion is parallel to an extension line connecting the center of the crankshaft and the center of the crank pin. The method of claim 33, wherein And the boundary end is spaced apart from the extension line connecting the crankshaft center and the crank pin center by a length corresponding to half the thickness of the key member. The method of claim 31, wherein And a boundary end formed between the track portion and the restricting portion is inclined at a predetermined angle with respect to an extension line connecting the crank shaft center and the crank pin center. The method of claim 1, And the ring member is provided between the bottom surface of the eccentric sleeve and the top surface of the crankshaft. The method of claim 1, And the balance weight prevents the eccentric sleeve from rotating by the moment of rotation. The method of claim 1, The balance weight is a dual displacement compressor, characterized in that configured not to generate a rotation moment on the eccentric sleeve. The method of claim 1, And the balance weight is configured to position the center of gravity of the eccentric sleeve on an extension line between the crankshaft center and the crank pin center. The method of claim 1, And the balance weight rotates the eccentric sleeve in the direction of engagement with the key member. The method of claim 1, The balance weight is a dual displacement compressor, characterized in that for generating a rotation moment in the direction opposite to the rotation direction. The method of claim 1, And the balance weight is configured to move the center of gravity of the eccentric sleeve opposite to an extension line between the crankshaft center and the crank pin center. The method of claim 1, And the balance weight is installed on a portion of the eccentric sleeve having a relatively low weight. The method of claim 1, The balance weight is a dual displacement compressor, characterized in that installed in the track portion of the eccentric sleeve.

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