KR100543164B1 - Dual capacity compressor - Google Patents

Abstract

The present invention relates to a double displacement compressor that prevents relative movement between components to maintain the amount of eccentricity. To this end, the present invention includes a power generation unit 20 including a motor (21, 22) capable of reverse rotation with respect to a predetermined rotation direction and a crankshaft (23) inserted into the motor (21, 22); A compression unit (30) comprising a cylinder (32) of a predetermined size, a piston (31) located in the cylinder (32), and a connecting rod (33) connected to the piston (31); Crank pins (110,210) formed eccentrically at the center of the upper end of the crankshaft (23); An eccentric sleeve (120,220) having an inner circumferential surface rotatably coupled to the outer circumferential surfaces of the crank pins (110,210) and an outer circumferential surface rotatably coupled to the ends of the connecting rod (33); And a key member (130,230) for completely constraining the eccentric sleeve (120,220) to the crank pins (110,210) in both clockwise and counterclockwise rotation of the motor.

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 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 rotation moment which appears appears and the direction of action of this rotation moment 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 crankshaft 1 so that the key 5 is connected 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.

On the other hand, in addition to the above-mentioned US Patent No. 4,236,874, many patent publications disclose the technologies related to the double capacity 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 during the compressor rotational direction change. 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.

As explained above, the applicants have found that the factors that make the operation of the dual displacement compressor unstable are local centrifugal force of the eccentric sleeve and external load through the connecting rod during operation. Applicants have found that these factors inevitably occur when using an eccentric mechanism, but can be solved if the crank pin and the eccentric sleeve can be reliably restrained from each other during operation. Applicant has focused on the key member with this restraint structure and modified the key member and its related members to prevent relative rotation between the crank pin and the eccentric sleeve as follows.

Accordingly, the present invention includes a power generation unit 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; And a key member which makes the eccentric sleeve completely hook the crank pin in both clockwise and counterclockwise rotation of the motor.

Preferably, the key member is in contact with the eccentric sleeve at a plurality of points, and more preferably simultaneously with both ends of the eccentric sleeve set relative to the center line in any direction.

In addition, the key member preferably has a first protrusion projecting out of the crank pin by a predetermined length even when the operation stops, and a second protrusion projecting out of the crank pin by a predetermined length during operation. The distance between the first and second protrusions has a length larger than the diameter of the pin by a predetermined size or more.

To describe each component in more detail, first, the crank pin includes a pair of key member mounting portions formed to face each other, and the key member mounting portions may be arranged along an inclined extension line with respect to the horizontal plane.

The key member mounting portion may be a through hole formed in the crank pin wall or a groove extending from a predetermined position of the at least one crank pin wall to an upper end. On the other hand, the crank pin is preferably extended higher than the eccentric sleeve.

The eccentric sleeve is formed along an extending direction of the body itself, and includes a track portion for enabling the rotational movement of the key member protrusion and a restriction portion formed relative to the track portion to limit the rotational movement of the key member protrusion. .

The track portion of the eccentric sleeve may be a through hole extending in a predetermined length along the circumferential direction at a predetermined depth from the upper end or a cutout extending in the circumferential direction at a predetermined depth from the upper end.

The boundary end formed between the track portion and the restricting portion is preferably parallel to an extension line connecting the center of rotation of the crankshaft and the center of the crank pin, more preferably spaced apart by a length corresponding to half the thickness of the key member. . In addition, the boundary end may be formed to be inclined at a predetermined angle with respect to the extension line connecting the center of rotation of the crank shaft and the center of the crank pin. On the other hand, it is preferable that the eccentric sleeve further comprises an oil supply hole formed to face each other at a predetermined height.

The key member includes: a first protrusion projecting out of the crank pin by a predetermined length to engage a boundary end of the eccentric sleeve; And a first stopper defining a protrusion length of the first protrusion, and a second protrusion projecting in a direction opposite to the first protrusion when engaged with the other boundary end of the eccentric sleeve.

Preferably, the thicknesses of the first and second protrusions of the key member are the same and the cross section of the first and second protrusions of the key member may be any of circular, square, and hexagon. Also preferably, the length of the protrusion during operation from the outer surface of the crank pin of the first protrusion may have a size greater than or equal to half the width of the boundary end, and the end of the second protrusion may not protrude to the outer surface of the crank pin when the operation stops. Has a length.

The first stopper may include a crank pin contact surface having a shape coincident with the inner circumferential surface of the crank pin and may have a detachable structure.

In the case of such a detachable structure, the first stopper may be inserted into a circumferential groove formed at a predetermined position of the key member or may be fixed by a fixing member at a predetermined position of the key member.

Meanwhile, the key member may further include an elastic member inserted into the second protrusion to support the first protrusion so as to continuously protrude regardless of the compressor operating state. To this end, the first stopper may further include the elastic member. It may further include a receiver.

On the other hand, the key member preferably further comprises a second stopper for limiting the protruding length to the outside of the crank pin of the second projection along the centrifugal force action direction. Here, the second stopper may be a hollow tubular member installed to be movable in the longitudinal direction in the second protrusion, a longitudinal extension of the first stopper having a diameter larger than the diameter of the second protrusion, and the first having a predetermined thickness. 2 can be a radial extension of the projection.

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.

The features and advantages of the present invention may be better understood with reference to the following accompanying drawings in conjunction with the following detailed description of embodiments of the invention, of which:

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 showing a first embodiment of a double displacement compressor according to the present invention, including some cross sections;

5b is a plan view of a first embodiment of a double displacement compressor according to the invention, including a partial cross section;

6A is a perspective view showing a crank pin according to the first embodiment of the present invention;

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

7A is a perspective view showing an eccentric sleeve according to the first embodiment of the present invention;

7B and 7C are a plan view and a side view showing a modification of the eccentric sleeve according to the first embodiment of the present invention;

8 is a perspective view showing a key member according to a first embodiment of 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 modification of the key member having a detachable first stopper;

11A-11C are plan views showing modifications of the key member having the second stripper;

12A is a side view showing a second embodiment of a double displacement compressor according to the present invention, including a partial cross section;

12B is a plan view of a second embodiment of a double displacement compressor according to the present invention, including a partial cross section;

13 is a perspective view showing a modification of the eccentric sleeve according to the second embodiment;

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

15A-15C are plan views showing modifications of the key member according to the second embodiment with the second stopper;

16A and 16B are plan views showing the operation of the second embodiment of the present invention in forward rotation; And

17A and 17B are plan views showing the operation of the second embodiment of the present invention in the reverse rotation.

BEST MODE FOR CARRYING OUT THE INVENTION

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. 4.

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 below 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. Here, 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 part 40 is a crank pin which is eccentrically formed on the upper end of the crankshaft, an eccentric sleeve rotatably mounted between the crank pin outer circumferential surface and the connecting rod, and a key for fixing the crank pin and the eccentric sleeve to each other. Member. With this configuration, the rearrangement of the eccentric sleeve is 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.

In the present invention, the key member is basically movably mounted in the crank pin, has a length that is at least larger than a predetermined size larger than the diameter of the pin so that at least a part of the key member protrudes out of the crank pin even when the operation is stopped and the centrifugal force during the operation. The other end protrudes. Thus, the key member is in contact with the eccentric sleeve at substantially multiple points, and more particularly in contact with both ends of the eccentric sleeve set on the basis of an arbitrary center line. As a result, even in any rotational direction of the motor, the key member completely engages the eccentric sleeve with the rotating crank pin, thereby preventing relative rotation by mutually generated rotational moments.

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

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 of explanation. And FIGS. 6A-11C show the individual components individually. Referring to the drawings, a first embodiment of the present invention will be described.

The dual displacement compressor 100 according to the first embodiment partially restricts the rotational movement of the crank pin 110, the key member protrusion and the pair of key member mounting portions 111 which face each other and are inclined at a predetermined angle. An allowable eccentric sleeve 120 and a key member 130 are installed through the mounting portion such that at least a portion protrudes out of the crank pin 110, the other parts being the same as the compressor of FIG. Here, the component weight (W) is generated in the key member 130 due to the inclined orientation, and the component adjusts the movement and position of the key member. In other words, at least a portion of the key member protrudes out of the crank pin 110 by its own weight W when stopped.

In the configuration of this first embodiment, the crank pin 110 has a partially hollow tubular shape, as shown in Figure 5a, the oil passage 112 formed in the lower portion together with the key member mounting portion 111 And an oil supply hole 113.

The mounting portions 111a and 111b are respectively formed in the hollow tube portion to be arranged in a vertical plane including the crankshaft center 23a and the crank pin center 110a. In addition, the mounting portions 111a and 111b are arranged along an extension line inclined at a predetermined angle with respect to the horizontal plane as mentioned above. Accordingly, the key member 130 positioned in the mounting portions 111a and 111b simultaneously influences the centrifugal force (F) component force acting on the extension line between the centers 23a and 110a along its own weight and its longitudinal direction. Receive. On the other hand, in the first embodiment, such mounting portions 111a and 111b are actually formed as through holes as shown in Fig. 6A. Therefore, the detachment of the key member 130 can be prevented during operation by the mounting portion, 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.

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 lubricating oil contained in the bottom of the compressor is scattered to be supplied to the contact surface between the parts for the first time through the oil groove and the oil passage 112 and to prevent wear 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 rotatably coupled to the outer circumferential surface of the crank pin 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 centrifugal sleeve 120 includes a track portion 121 formed along an extension direction of the body itself and a restriction 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. The track portion 121 enables the relative rotational movement of the eccentric sleeve 120 itself relative to the protrusion when the key member 130 is stopped. That is, since at least a portion of the key member 130 is protruded during the stop, the eccentric sleeve 120 may rotate around the crank pin 110 at the stop as much as the formation range of the track portion 120. . In addition, the limiting portion 122 restricts the rotational movement of the sleeve itself by the protrusion of the key member 130 during stop and operation relative to the track portion 121, and the protrusions of the key member 130 are substantially It is caught by the boundary end 123.

In the eccentric sleeve 120, the track portion 121 may be a cutout extending in the circumferential direction to a predetermined depth to the upper end of the eccentric sleeve 120. The boundary ends 123a and 123b are formed in parallel with 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 substantially parallel to the extension line between the maximum thickness and the minimum thickness of the eccentric sleeve 110 and have different widths, and the extension lines are the centers 23a and 110a. Coincide with the extension line between them. The boundary ends 123a and 123b are also located together on any extension line parallel to the extension lines of the centers 23a and 110a. Accordingly, the key members 130 arranged on the same extension line may be caught by the boundary end 123, and the boundary ends 123 may form a common contact surface with respect to the key member 130. The boundary ends 123a and 123b are preferably spaced 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 reliably 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 may be formed along a radial extension line of the crank pin center 110a inclined at a predetermined angle with respect to the extension line between the centers 23a and 110a. . In addition, boundary ends 123e and 123f may be formed to be inclined at a predetermined angle toward the limiting portion at the intersection of the boundary ends 123a and 123b and the inner circumferential surface of the eccentric sleeve 120. In each of these cases, the boundary ends 123c, 123d, 123e, and 123f may be engaged with each other by having at least a common contact point with the key member 130.

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 114 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. Therefore, any one of the two oil supply holes 125 is in communication with the oil supply hole 113 regardless of the rotation direction during the operation of the compressor, the lubricant 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.

As shown in FIG. 8, 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 is stopped, and the operation of the key member 130. The second protrusion 132 protrudes to the outside of the crank pin 110 by a predetermined length. The key member 130 also includes a first stopper 133 that defines the protruding length of the first protrusion. In this case, the second protrusion 132 is actually disposed in the crank pin 110 away from the crankshaft center 22a in order to be greatly influenced by the centrifugal force, and the first protrusion 131 is relatively disposed at the center. It is arrange | positioned adjacent to 22a.

In the first embodiment, as shown in FIG. 5A, the first protrusion 131 protrudes when stopped by its own weight to engage with any one of the boundary ends 123a and 123b and to be engaged with the boundary end during operation. Is maintained. This protruding depth is limited by the first stopper 133 positioned on the key member 130 being caught on the inner wall of the crank pin 110. In this case, the protrusion length of the first protrusion may have a size of at least half of the minimum width of the boundary ends 123a and 123b for more stable operation.

The second protrusion 132 protrudes in the opposite direction of the first protrusion 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 movement and protrusion of the second protrusion are made in the centrifugal force direction (ie, an extension line between the centers 23a and 110a) as the component force of the centrifugal force generated along the key member 130 becomes larger than the component weight of its own weight during operation. 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. Therefore, the second protrusion 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 during operation, in particular the second protrusion 132 is engaged with the boundary ends 123a and 123b during operation. . Since the key member 130 is arranged in an extension line or at least parallel between the centers 23a and 110a, if the thicknesses t1 and t2 of the first and second protrusions 131 and 132 are different from each other, the boundary end The contact positions with the fields 123a and 123b are 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. 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 in the radial direction, 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. 11A, 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 to some extent by the self-weight component of the key member 130 itself acting in the opposite direction to the component force of the centrifugal force as described above. Can be adjusted. However, when the compressor starts to operate, rapid acceleration is generated in the crankshaft 23 and the crank pin 110, and thus a very large instantaneous centrifugal force is 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. 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 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

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.

Second embodiment

The second embodiment of the present invention has an installation structure of the above key member as compared with the first embodiment described above as a whole.

For this second embodiment, FIGS. 12A and 12B are side and top views showing a second embodiment of a double displacement compressor according to the invention, and FIGS. 13-15C show the main components separately. Herein, the respective components are shown assembled together with some cross-sections for ease of explanation and clarity as in the first embodiment. A second embodiment of the present invention will be described in detail with reference to the drawings.

The dual displacement compressor 200 according to the second embodiment has a crank pin 210 having a pair of key member mounting portions 211 opposed to and parallel to each other, and an eccentric sleeve that partially limits and permits rotational movement of the key member protrusions. 220 and at least a portion of the key member 230 installed through the mounting portion 211 to protrude out of the crank pin 210. In addition, the second embodiment includes an elastic member 240 for adjusting the position of the key member 230 during the compressor stop and operation. As shown in the figure, unlike the first embodiment, the key member of the second embodiment is mounted horizontally so that a separate auxiliary member is required, such as the elastic member 240.

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, the crank pin 210 includes an oil passage 212 and an oil supply hole 213 formed at the bottom along with the key member mounting portions 211a and 211b. The mounting portions 211a, 211b are located on or at least parallel to the extension line between the centers 23a, 210a as shown in Fig. 12b, and are arranged in the same horizontal plane as shown in Fig. 12a. Accordingly, the key member 230 positioned in 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. The mounting parts 211a and 211b may be formed as actual through holes, and preferably include at least one groove extending from an upper end of the wall of the crank pin 210 to a predetermined position.

The eccentric sleeve 220 includes a track portion 221, a restricting portion 222 and two boundary ends 223 formed therebetween as in the first embodiment. In the second embodiment, the track portion 221 may be a through hole extending along a circumferential direction at a predetermined depth from the upper end as shown in FIG. 13 as well as the cutout of FIG. 7A. The track part 221 which is a through hole is applicable because the key member 230 is horizontally arranged, and restrains the protrusion when the key member 230 is stopped so that the key member 230 is not separated in the vertical direction. The boundary ends 223a and 223b may be formed parallel to the extension line between the centers 23a and 210a and may be formed to be inclined at a predetermined angle.

The key member 230 includes a first protrusion 131, a second protrusion 132, and a first stopper 233. Here, the first protrusion 231 protrudes out of the crank pin 210 regardless of the compressor operating state (stop or operation) by the elastic force of the elastic member 240, so that any one of the boundary ends 223a and 223b may be formed. Engage with one. To this end, the elastic member 240 is mounted on the second protrusion to elastically support the first stopper 233 together with the inner wall of the crank pin 210. In addition, the centrifugal force generated along the key member 230 during operation is greater than the elastic force, so that 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). .

On the other hand, as shown in Figure 14, the first stopper 233 includes a contact surface 233a having a shape matching the inner peripheral surface of the crank pin 210, preferably of the elastic member 240 It may further include a receiving portion (233b). The contact surface 133a 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 130 or may be formed as a separate member.

The protruding length of the second protruding member is adjustable by the elastic force of the elastic member 240 during normal operation. However, preferably, the key member 230 further includes a second stopper 234 to prevent separation of the second protruding member by the above-mentioned instantaneous centrifugal force.

As shown in Figs. 15A to 15C, 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 each a hollow tubular member 234a, which is installed to be movable in the longitudinal direction on the second stopper 234, the longitudinal extension of the first stopper 133 or A radial extension 134c of the second protrusion having a predetermined thickness. In the second embodiment, only its relative position is distinguished from the first embodiment due to the presence of the elastic member 240. In more detail, in the hollow tubular shape 234a, the elastic member 240 is interposed between the second stopper 234a and the second protrusion 232. In the case of the longitudinally extending portion 234b, the elastic member 240 is installed on the outer circumferential surface of the second stopper 234b, and in the case of the radially extending portion 234c, the second stopper 234b and the crank. It is installed between the inner peripheral surface of the pin (210).

The operation of the present invention according to the first and second embodiments described above is described next with reference to the associated drawings. In the present invention, the first and second embodiments are distinguished in the key member 130, 230 movement control method such as self-weight or elastic force due to the inclined orientation, and are substantially the same in practical operation. Thus, the operation of the present invention is described with reference to the second embodiment to avoid duplication.

16A and 16B show the operation of the second embodiment in the forward rotation and FIGS. 17A and 17B show the operation of the second embodiment in the reverse rotation.

First, FIG. 16A shows the relative position between the key member 230 and the eccentric sleeve 220 when the crankshaft 23 begins to rotate in the forward direction, ie clockwise. The first protrusion 231 protrudes out of the crank pin 210 by the elastic force and is engaged with the thin thickness side boundary end 223b of the eccentric sleeve 220. In addition, the parts 210, 220, and 230 except the connecting rod 33 connected to the piston start to rotate clockwise. At this time, when the rotational angular velocity reaches a predetermined level, the key member 230 is moved along its extension direction between its working directions, that is, the centers 23a and 210a, by the centrifugal force F as shown in FIG. 16B. Accordingly, the second protrusion 232 is engaged with the thick thickness side boundary end 223a, and the first protrusion 231 also maintains contact with the boundary end 223b at the same time. This simultaneous multi-point contact causes the key member 230 to fully engage the eccentric sleeve 220. Therefore, in the forward rotation, the relative rotation between the crank pin 210 and the eccentric sleeve 220 even if the external force P and any other force are transmitted through the connecting rod 33 by the re-expansion of the working fluid after the compression process. This is avoided. And even when a local rotation moment occurs in the eccentric sleeve 220, the relative rotation with respect to the crank pin 110 can also be prevented. In addition, as shown in FIG. 7B, 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 220 is arranged to have a maximum amount of eccentricity. Thus the piston reciprocates at the maximum stroke length Lamx and the compressor according to the invention has a maximum compression capacity.

On the other hand, when the crankshaft 23 and the crank pin 210 integral with it start to rotate in the opposite direction, that is, counterclockwise, the eccentric sleeve 220 is between the crank pin 210 and the connecting rod 33. Relative rotation in the opposite direction, ie forward direction. Thus, as shown in FIG. 17A, the thick thickness side boundary end 223a is engaged with the first protrusion 231. As in the forward rotation, when the rotational angular velocity reaches a certain level, the second protrusion 232 is engaged with the thin thickness side boundary end 223b by the centrifugal force F, as shown in FIG. 17B, and the eccentricity. A multipoint contact is made between the sleeve 220 and the key member 230. 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 210 and the eccentric sleeve 220 can be prevented. . On the other hand, as shown in Figure 7b, it is understood that the compressor has a minimum compression capacity because the eccentric sleeve 220 is arranged to have a minimum amount of eccentricity in the reverse rotation.

As a result, the compressor according to the invention can be operated stably in any operating state, ie forward or reverse rotation, by completely excluding the relative rotation between the components that maintain the amount of eccentricity, that is, the crank pin and the eccentric sleeve.

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 key member is located is also completely restrained by 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. 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 (57)

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; And Consisting of a key member which completely constrains the eccentric sleeve to the crank pin in both clockwise and counterclockwise rotation of the motor, 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 2, 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 2, And the key member has a length greater than an outer diameter of the crank pin. The method of claim 1, And a second protrusion projecting out of the crank pin by a predetermined length during operation, and a second protrusion projecting out of the crank pin by a predetermined length during operation. The method of claim 5, And the distance between the ends of the first and second protrusions is greater than the outer diameter of the crank pin. The method according to claim 3 or 5, And a pair of key member mounting portions in which the crank pins are formed to face each other. The method according to claim 3 or 5, And the crank pin extends higher than the eccentric sleeve. The method according to claim 3 or 5, 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 9, 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 9, The track portion of the eccentric sleeve is a double capacity compressor, characterized in that the through-hole extending in a predetermined length along the circumferential direction at a predetermined depth from the upper end. The method of claim 9, 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 12, 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 9, And the boundary end formed between the track portion and the restricting portion is inclined at a predetermined angle with respect to the extension line connecting the crankshaft center and the crank pin center. The method of claim 14, And the boundary end is formed on a radial extension line from the crank pin center inclined at a predetermined angle with respect to the extension line connecting the crank shaft center and the crank pin center. The method of claim 14, And the boundary end is inclined at a predetermined angle toward the limiting part about an intersection point between the inner circumferential surface of the eccentric sleeve and the boundary end. The method according to claim 3 or 5, The dual displacement compressor characterized in that the eccentric sleeve further comprises an oil supply hole formed to face each other at a predetermined height. The method of claim 17, And a oil groove for diffusing the lubricating oil supplied with the oil supply hole around the oil supply hole. The method according to claim 3 or 5, And the cross section of the first and second protrusions of the key member is any one of a circle, a rectangle and a hexagon. The method of claim 5, And the first and second protrusions of the key member have the same thickness. The method of claim 9, And a protruding length during operation from the crank pin outer circumferential surface of the first protrusion has a size equal to or more than half the width of a boundary end formed between the track portion and the restricting portion. The method of claim 5, And the second protrusion has a length such that an end thereof does not protrude to an outer circumferential surface of the crank pin when the second protrusion is stopped. The method of claim 7, wherein And the key member mounting portion of the crank pin is a through hole formed in the crank pin wall. The method of claim 7, wherein 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 23 or 24, And the key member comprises a stopper for limiting its movement within the crank mount. The method of claim 25, And the key member mounting portion is arranged along an inclined extension line with respect to a horizontal plane. The method of claim 25, And the key member further comprises an elastic member for supporting at least a portion of the key member so as to continuously project out of the crank pin regardless of the compressor operating state. The method of claim 27, And the stopper further comprises a receiving portion of the elastic member. The method of claim 25, 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 25, And the stopper is a first stopper for limiting one-way movement of the key member. The method of claim 25, And the stopper further comprises a second stopper for limiting movement of the key member in the other direction. The method of claim 31, wherein And the second stopper is a hollow tubular member movably installed in the key member longitudinal direction. The method of claim 31, wherein And the second stopper is a longitudinal extension having a diameter at least greater than the diameter of the key member. The method of claim 31, wherein And the second stopper is a radial extension of the key member with a predetermined thickness. The method of claim 7, wherein The key member mounting portion of the crank pin is a through hole formed in the crank pin wall, and the key member includes a detachable stopper for restricting its movement in the crank mounting portion. 36. The method of claim 35 wherein And the stopper is inserted into a circumferential groove formed at a predetermined position of the key member. 36. The method of claim 35 wherein And the stopper is fixed to a predetermined position of the key member by a fixing member. The method of claim 7, wherein A 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, wherein the key member includes an integral stopper for restricting its movement within the crank mounting portion; Dual capacity compressor, characterized in that. The method of claim 35 or 38, And a resilient member for supporting the key member so that at least a portion thereof protrudes out of the crank pin continuously regardless of the compressor operating state. The method of claim 39, And the stopper further comprises a receiving portion of the elastic member. The method of claim 35 or 38, And the crank pin contact surface of the stopper has a shape coincident with the inner circumferential surface of the crank pin. The method of claim 35 or 38, And the key member mounting portion is arranged along an inclined extension line with respect to a horizontal plane. A hollow cylindrical crank pin formed to face each other and having a pair of key member mounting portions arranged along an extension line inclined at a predetermined angle; An eccentric sleeve formed along an extending direction of the body itself and including a track portion for allowing a 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; A first protrusion projecting out of the crank pin to a predetermined length to engage a boundary end formed between the track portion and the restricting portion, a stopper defining a protrusion length of the first protrusion, and a direction opposite to the first protrusion when rotating; And a second member which protrudes from and engages with the other boundary of the eccentric sleeve, the key member being inclined through the mounting portion. The method of claim 43, And the distance between the first and second protrusions is greater than the outer diameter of the fin. A hollow cylindrical crank pin having a pair of key member mounting portions formed to face each other; An eccentric sleeve formed along an extending direction of the body itself and including a track portion for allowing a rotational movement of the key member protrusion and a restricting portion relatively continuous to restrict the rotational movement of the key member protrusion; A first protrusion projecting out of the crank pin to a predetermined length to engage a boundary between the track portion and the restricting portion, a stopper defining a protrusion length of the first protrusion, and a protrusion protruding in a direction opposite to the first protrusion when rotating; A key member including a second projection to engage the other boundary of the eccentric sleeve; And And a resilient member inserted into the second protrusion to elastically support the first protrusion to continuously protrude regardless of the compressor operating state. The method of claim 45, And the distance between the first and second protrusions is greater than the outer diameter of the fin. The method of claim 45, The key member mounting portion of the crank pin is a through hole formed in the crank pin wall, and the key member includes a detachable stopper for restricting its movement in the crank mounting portion.  The method of claim 45, A 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, wherein the key member includes an integral stopper for restricting its movement within the crank mounting portion; Dual capacity compressor, characterized in that. A hollow cylindrical crank pin having a pair of key member mounting portions formed to face each other; An eccentric sleeve formed along an extending direction of the body itself and including a track portion for allowing a rotational movement of the key member protrusion and a restricting portion formed relatively continuously to limit the rotational movement of the key member protrusion; A key member that completely engages the eccentric sleeve on the crank pin in both clockwise and counterclockwise rotation of the motor, the key member having a length greater than the outer diameter of the crank pin; And And an elastic member mounted to the key member to support 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 49, And the key member comprises a stopper for limiting its movement within the crank mount. 51. The method of claim 50, And the stopper is a first stopper for limiting one-way movement of the key member. 51. The method of claim 50, And the second stopper further comprises a second stopper for limiting movement of the key member in another direction. The method of claim 52, wherein And the second stopper is a hollow tube member installed in the key member so as to be movable in the longitudinal direction. The method of claim 52, wherein And the second stopper is a longitudinal extension having a diameter larger than the diameter of the key member. The method of claim 52, wherein And the second stopper is a radial extension of the key member with a predetermined thickness. The method of claim 49, The key member mounting portion of the crank pin is a through hole formed in the crank pin wall, and the key member includes a detachable stopper for restricting its movement within the clink mounting portion. The method of claim 49, A 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, wherein the key member includes an integral stopper for restricting its movement within the crank mounting portion; Dual capacity compressor, characterized in that.

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