CN114370385A - Reciprocating compressor - Google Patents

Abstract

Disclosed is a reciprocating compressor capable of minimizing an unbalance force generated during the movement of a rotary shaft and a piston, wherein the reciprocating compressor comprises: a piston; a rotating shaft; and a balancer coupled to the rotating shaft in a penetrating manner and rotating together with the rotating shaft, the balancer including: a coupling portion formed by extending and expanding from a coupling hole in contact with an outer circumferential surface of a rotary shaft toward a radial outer side of the rotary shaft; and an eccentric mass part coupled to one side of the coupling part, and one surface of the eccentric mass part, which is opposite to the housing in a height direction of the rotation shaft, is inclined toward a direction opposite to the housing.

Description

Reciprocating compressor

technical field

The present invention relates to reciprocating compressors, and more particularly, to a reciprocating compressor capable of minimizing unbalanced forces generated during movement of a rotating shaft and a piston.

Background technique

The compressor refers to a device that discharges high-pressure fluid by compressing the fluid, or operates a machine using energy generated when the high-pressure fluid is discharged.

A reciprocating compressor is a type of compressor that compresses refrigerant by reciprocating motion of a piston in a cylinder, and then discharges the refrigerant to a discharge space in a high-pressure state.

Specifically, the rotational motion of the rotary shaft is transmitted to a piston connected to the rotary shaft, whereby the refrigerant is compressed by the reciprocating motion of the piston, and then the refrigerant is discharged into the discharge space in a high-pressure state.

At this time, an unbalanced force is generated in the compressor due to the eccentric rotational motion of the rotating shaft and the reciprocating motion of the piston. This may cause vibration of the rotating shaft and the piston, and may increase the noise generated during the driving of the reciprocating compressor.

Therefore, in order to reduce this unbalanced force, an additional balancer can be provided on the rotating shaft.

Here, the balancer refers to a balancer that is attached to the outer periphery of the rotating body to balance the rotating body.

In the conventional reciprocating compressor, one surface of the balancer facing the casing is formed as a plane parallel to the radial direction of the rotating shaft.

However, in the conventional reciprocating compressor, the interval between the casing and the balancer has a minimum value. That is, the design of the reciprocating compressor may be limited. Therefore, the balancer cannot sufficiently balance the rotating body.

Korean Laid-Open Patent Publication No. 10-2004-0009500 discloses a hermetic reciprocating compressor. Specifically, a hermetic reciprocating compressor including a weight balance member is disclosed, wherein the weight balance member is located at a boundary portion of a main shaft portion and a crank portion of a crank member.

However, in this type of reciprocating compressor, the weight balance member is formed in a rectangular parallelepiped shape. Therefore, there is a minimum interval between the casing and the weight balance member, so that the design of the reciprocating compressor may be limited.

Korean Authorized Utility Model Publication No. 20-0126118 discloses a reciprocating compressor. Specifically, there is disclosed a reciprocating compressor provided with an eccentric portion and a weight balancer, wherein the eccentric portion is provided on a rotating shaft in an eccentric manner from the rotating shaft, and the weight balancer is opposite to the eccentric portion. The unbalanced forces created by the eccentric rotational motion are counteracted.

However, in this type of reciprocating compressor, the weight balancer is also formed in a rectangular parallelepiped shape. Thus, the design of the reciprocating compressor may be limited.

prior art literature

Patent Literature

Korean Laid-Open Patent Publication No. 10-2004-0009500 (2004.01.31)

Korea Authorized Utility Model Gazette No. 20-0126118 (1998.07.03)

SUMMARY OF THE INVENTION

An object of the present invention is to provide a reciprocating compressor capable of minimizing the unbalanced force generated during the movement of the rotary shaft and the piston.

Another object of the present invention is to provide a reciprocating compressor that can further reduce the space between the casing and the balancer and can further increase the balancing effect of the balancer.

Another object of the present invention is to provide a method to manufacture the interval between one end of the balancer and the casing and the interval between the other end of the balancer and the casing at the interval ratio most suitable for preset driving conditions of reciprocating compressors.

In order to achieve the objective, a reciprocating compressor according to an embodiment of the present invention includes: a piston; a rotating shaft, which is coupled to the piston in a manner capable of rotating relative to the piston; a balancer, which is penetratingly coupled to the rotating shaft, and rotates together with the rotating shaft; and a housing that accommodates the piston, the rotating shaft and the balancer inside, the rotating shaft including: a support portion extending in one direction; and an eccentric portion extending from the One end of the supporting portion is formed to extend in the one direction, and the central axis of the eccentric portion and the central axis of the supporting portion are not arranged in a straight line, and the balancer includes a joint portion connected from the The eccentric mass portion is connected to one side of the coupling portion and extends toward the radial inner side of the support portion, and the eccentric mass portion is connected to the radially inner side of the support portion, and the eccentric mass portion is formed by extending and expanding toward the radial outer side of the eccentric portion. One surface of the eccentric mass portion facing the housing in the height direction of the rotating shaft is inclined in a direction opposite to the housing.

In addition, the one surface of the eccentric mass portion may be formed as a curved surface.

In addition, at least a part of the one surface of the eccentric mass portion may be formed in a shape corresponding to the inner peripheral surface of the housing.

In addition, the one surface of the eccentric mass portion may be formed to be flat.

In addition, the uppermost end of the one surface of the eccentric mass portion in the height direction of the rotating shaft and the inner peripheral surface of the housing may be spaced apart from the height direction of the rotating shaft by a first interval, The lowermost end of the one surface of the eccentric mass portion in the height direction of the rotating shaft and the inner peripheral surface of the housing in the height direction of the rotating shaft may be separated by a second interval, so The value obtained by dividing the first interval by the second interval may be a preset prescribed interval ratio.

In addition, the predetermined interval ratio may be 0.9 or more and 1.1 or less.

In addition, a reciprocating compressor according to another embodiment of the present invention includes: a piston; a rotating shaft extending in one direction and coupled to the piston so as to be rotatable relative to the piston; and a balancer coupled to the rotation an outer circumference of a shaft that rotates together with the rotating shaft; and a housing that accommodates the piston, the rotating shaft, and the balancer inside, the rotating shaft including: a support portion extending toward the one direction and an eccentric portion extending from one end of the supporting portion toward the one direction, and the central axis of the eccentric portion and the central axis of the supporting portion are not arranged in a straight line, the balancer comprising: a coupling part, which extends from a coupling hole in contact with the outer peripheral surface of the eccentric part toward the radially outer side of the eccentric part and is formed by expansion; and an eccentric mass part, which is coupled to one side of the coupling part and faces the supporting part extending radially inside of the eccentric mass portion, and one surface of the eccentric mass portion facing the housing in the height direction of the rotating shaft is bent by a predetermined angle in a direction opposite to the housing.

In addition, on the one surface of the eccentric mass portion, a portion located on the radially outer side of the eccentric portion may be formed as a curved surface with reference to a bending line.

In addition, the part of the eccentric mass portion may be formed in a shape corresponding to the inner peripheral surface of the housing.

In addition, on the one surface of the eccentric mass portion, a portion located on the radially outer side of the eccentric portion may be formed as a flat surface with reference to a bending line.

In addition, the uppermost end of the one surface of the eccentric mass portion in the height direction of the rotating shaft may be spaced apart from the inner peripheral surface of the housing in the height direction of the rotating shaft by a first interval, The lowermost end of the one surface of the eccentric mass portion in the height direction of the rotating shaft may be spaced apart from the inner peripheral surface of the housing in the height direction of the rotating shaft by a second interval, and the The value obtained by dividing the first interval by the second interval may be a preset prescribed interval ratio.

In addition, the predetermined interval ratio may be 0.9 or more and 1.1 or less.

In addition, a reciprocating compressor according to another embodiment of the present invention includes: a piston formed in a cylindrical shape; a rotating shaft connected to the piston in a manner rotatable relative to the piston; and a balancer connected to the piston through the a rotating shaft that rotates together with the rotating shaft; and a casing that accommodates the piston, the rotating shaft, and the balancer inside, and a projection is formed in a part of the casing, the rotating shaft The shaft includes: a support part extending in one direction; and an eccentric part formed to extend from one end of the support part in the one direction, and the center axis of the eccentric part and the center axis of the support part are not arranged in a straight line On the line, the balancer includes: a coupling portion extending and expanding from a coupling hole in contact with the outer peripheral surface of the eccentric portion toward the radially outer side of the eccentric portion; and an eccentric mass portion coupled to the coupling portion one side of the support portion extends radially inward of the support portion, the protruding portion and the eccentric mass portion overlap in the height direction of the rotating shaft, and the protruding portion faces opposite to the eccentric mass portion The direction protrudes, and the protruding portion is formed in a shape corresponding to the eccentric mass portion.

In addition, the rotating shaft may include a balance portion disposed between the support portion and the eccentric portion and formed to expand from the one end of the support portion toward the radially outer side of the support portion.

In addition, a connecting rod may be included extending in a direction different from the one direction, one end of the connecting rod is coupled to the piston, and the other end of the connecting rod is coupled to the eccentric portion so as to be relatively rotatable.

Among the various effects of the present invention, the effects that can be obtained by the above solution are as follows.

First, one surface of the balancer opposite to the housing is inclined toward the opposite direction to the housing.

That is, one surface of the balancer facing the housing is formed in a shape corresponding to the inner peripheral surface of the housing.

Therefore, the balancing force generated by the balancer can be sufficiently ensured during the driving of the compressor, and the driving force generated during the movement of the rotating shaft and the piston and the balancing force generated by the balancer complement each other, so that the total Balance force is minimized.

Thereby, the vibration of the rotating shaft and the piston can be further reduced.

Furthermore, it is also possible to minimize the noise generated by the vibration of the rotating shaft and the piston.

In addition, the space between the balancer and the housing can be further reduced by inclining one surface of the balancer opposite to the housing in a direction opposite to the housing.

That is, the space between the balancer and the case can be further reduced.

Therefore, the balancing effect by the balancer can be further increased.

In addition, the interval between one end of the balancer and the housing, and the interval between the other end of the balancer and the housing can be adjusted according to preset driving conditions.

Therefore, the interval between one end of the balancer and the housing and the interval between the other end of the balancer and the housing can be manufactured at the interval ratio most suitable for the preset driving conditions.

Description of drawings

FIG. 1 is a cross-sectional view showing a reciprocating compressor according to an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing the reciprocating compressor of FIG. 1 .

3 is an enlarged cross-sectional view showing a balancer according to an embodiment of the present invention.

4 is an enlarged cross-sectional view of a balancer showing another embodiment of the present invention.

FIG. 5 is a side view showing the rotating shaft and the piston of FIG. 1 .

FIG. 6 is a plan view showing the rotating shaft and the piston of FIG. 1 .

FIG. 7 is a perspective view showing the balancer of FIG. 1 .

FIG. 8 is a plan view showing the balancer of FIG. 1 .

FIG. 9 is a cross-sectional view showing the balancer of FIG. 1 .

FIG. 10 is a cross-sectional view showing the balancer of FIG. 3 .

FIG. 11 is a cross-sectional view showing the balancer of FIG. 4 .

FIG. 12 is a graph illustrating unbalanced forces generated during movement of a rotating shaft and a piston according to an embodiment of the present invention.

Description of reference numerals

1: Reciprocating compressor 10: Housing

110: Upper case 111: Projection

120: Lower shell 11: Refrigerant suction pipe

12: Refrigerant discharge pipe 20: Oil supply device

21: Oil 30: Compression part

31: Cylinder bore module 311: Cylinder bore

312: Internal space of cylinder barrel 313: Bearing

314: Plate 32: Piston

321: Piston pin 322: Connecting rod

40: Drive Motor 41: Stator

42: Rotor 50: Rotary shaft

51: Support part 52: Eccentric part

53: Balance part 54: Oil supply passage

60: Balancer 61: Joint

611: Combination hole 62: Eccentric mass part

S1: Compression space S2: Suction space

S3: Spit out space S4: Oil storage space

g1: first interval g2: second interval

Detailed ways

Hereinafter, the reciprocating compressor 1 according to the embodiment of the present invention will be described in more detail with reference to the accompanying drawings.

In the following description, some descriptions about constituent elements may be omitted in order to clarify the characteristics of the present invention.

In this specification, even in mutually different embodiments, the same reference numerals will be assigned to the same configuration, and repeated descriptions thereof will be omitted.

The accompanying drawings are only for facilitating understanding of the embodiments disclosed in this specification, and do not limit the technical ideas disclosed in this specification.

Unless the context clearly dictates otherwise, expressions in the singular include expressions in the plural.

Hereinafter, the reciprocating compressor 1 according to the embodiment of the present invention will be described with reference to FIGS. 1 to 4 .

The reciprocating compressor 1 of the present invention includes a casing 10 , a refrigerant suction pipe 11 , a refrigerant discharge pipe 12 , an oil supply device 20 , a drive motor 40 , a compression unit 30 , and a rotating shaft 50 .

The casing 10 forms the appearance of the reciprocating compressor 1 .

A space for accommodating the oil supply device 20 , the compression unit 30 , the drive motor 40 , and the rotating shaft 50 is formed inside the casing 10 . That is, the oil supply device 20 , the compression part 30 , the drive motor 40 , and the rotating shaft 50 are accommodated inside the casing 10 .

The case 10 may include an upper case 110 and a lower case 120 .

In the illustrated embodiment, the upper case 110 and the lower case 120 are formed in a dome shape. Specifically, the upper case 110 is formed in a dome shape that is raised toward the upper side, and the lower case 120 is formed in a dome shape that is recessed toward the lower side.

A protrusion 111 may be formed in a part of the upper case 110 . This will be described in detail later (refer to FIG. 4 ).

The lower side end portion of the upper case 110 and the upper side end portion of the lower case 120 are combined. In one embodiment, the upper shell 110 and the lower shell 120 are combined by welding.

The combined upper case 110 and lower case 120 form an inner space of the case 10 . At this time, the inner space is hermetically sealed.

The inner space of the casing 10 includes a compression space S1, a suction space S2, a discharge space S3, and an oil storage space S4.

The compression space S1 is a space in which the refrigerant is compressed into a high-pressure state by the piston 32 .

The compression space S1 is formed between one end of the piston 32 and the inner circumference of the cylinder 311 .

The suction space S2 is a space through which the refrigerant flowing in from the refrigerant suction pipe 11 passes before flowing into the compression space S1.

The suction space S2 is combined with the open side of the refrigerant suction pipe 11 . Therefore, the refrigerant discharged from the one side of the refrigerant suction pipe 11 flows into the suction space S2.

The discharge space S3 is a space through which the refrigerant discharged from the compression space S1 in a high-pressure state passes before being discharged from the refrigerant discharge pipe 12 .

The discharge space S3 is connected to the open side of the refrigerant discharge pipe 12 . Therefore, the refrigerant existing in the discharge space S3 can be discharged to the outside of the casing 10 through the one side of the refrigerant discharge pipe 12 .

In short, the refrigerant flowing into the casing 10 through the refrigerant suction pipe 11 passes through the suction space S2 , the compression space S1 , and the discharge space S3 in this order, and then is discharged to the outside of the casing 10 through the refrigerant discharge pipe 12 .

The oil storage space S4 is a space for storing the oil 21 which assists the smooth movement of the compression part 30 and the rotating shaft 50 .

The oil storage space S4 is formed in the lower part of the inner space of the casing 10 .

The oil 21 in the oil storage space S4 is collected in the oil storage space S4 by gravity.

The oil storage space S4 will be described in more detail later together with the description of the oil supply device 20 .

The refrigerant suction pipe 11 and the refrigerant discharge pipe 12 are penetratingly coupled to the upper case 110 or the lower case 120 . In the illustrated embodiment, the refrigerant suction pipe 11 and the refrigerant discharge pipe 12 are penetratingly coupled to the lower casing 120 .

One side of the refrigerant suction pipe 11 is connected to the casing 10 . In addition, the other side of the refrigerant suction pipe 11 is disposed outside the reciprocating compressor 1, and a refrigerant suction port is formed.

In one embodiment, a suction valve (not shown) may be provided in the refrigerant suction pipe 11 .

The suction valve adjusts the inflow amount of the refrigerant flowing into the refrigerant suction pipe 11 .

When the refrigerant flows into the suction space S2, the suction valve is opened, and when the refrigerant is discharged from the discharge space S3 to the outside, the suction valve is closed. That is, when the compression space S1 increases, the suction valve opens, and when the compression space S1 decreases, the suction valve closes.

One side of the refrigerant discharge pipe 12 is connected to the casing 10 and is separated from the refrigerant suction pipe 11 . In addition, the other side of the refrigerant discharge pipe 12 is disposed outside the reciprocating compressor 1, and a discharge port for the refrigerant is formed.

In one embodiment, a discharge valve (not shown) may be provided in the refrigerant discharge pipe 12 .

The discharge valve adjusts the discharge amount of the refrigerant discharged from the refrigerant discharge pipe 12 .

When the refrigerant is discharged from the discharge space S3 to the outside, the discharge valve is opened, and when the refrigerant flows into the suction space S2, the discharge valve is closed. That is, when the compression space S1 is reduced, the discharge valve is opened, and when the compression space S1 is increased, the discharge valve is closed.

On the other hand, the oil 21 is also supplied to the reciprocating compressor 1 in addition to the refrigerant. Specifically, by supplying the oil 21 between the components that move inside the reciprocating compressor 1 , the components are moved smoothly.

For this purpose, an oil storage space S4 for supplying the oil 21 is provided in the lower space of the inner space of the casing 10 .

The oil 21 in the oil storage space S4 is supplied to each component of the reciprocating compressor 1 through the oil supply device 20 .

The oil supply device 20 sucks the oil 21 stored in the oil storage space S4 to move the oil 21 to the inside of the rotating shaft 50 to be described later.

The oil supply device 20 is coupled to the lower side of the rotating shaft 50 . At this time, the oil supply device 20 communicates with the oil supply passage 54 inside the rotary shaft 50 . This will be described in detail later together with the description of the rotating shaft 50 .

Moreover, the lower end part of the oil supply apparatus 20 is arrange|positioned in the oil storage space S4. Specifically, the lower end portion of the oil supply device 20 extends downward so as to be immersed in the oil 21 inside the oil storage space S4.

Therefore, the oil supply device 20 can supply the oil 21 from the oil storage space S4 to the compression part 30 and the rotation part.

In the illustrated embodiment, the oil supply device 20 is formed in a cylindrical shape extending in the same direction as the extending direction of the rotating shaft 50 .

However, the oil supply device 20 is not limited to the form shown, and may be formed in various forms. In one embodiment, the oil supply device 20 may be formed in the form of a centrifugal pump. In another embodiment, the oil supply device 20 may be formed in the form of a viscous pump.

The oil 21 sucked by the oil supply device 20 is supplied to the compression part 30 and the rotating shaft 50 . After that, the oil 21 sucked into the compression part 30 and the rotary shaft 50 falls to the oil storage space S4 by gravity.

As a result, the oil 21 in the oil storage space S4 repeats the process of being supplied to the compression part 30 and the rotary shaft 50 by the oil supply device 20, and then being recovered to the oil storage space S4 again, so that the oil 21 is inside the reciprocating compressor. to cycle.

At this time, the compression part 30 is constituted by the cylinder block 31 and the piston 32 .

The compression part 30 compresses the refrigerant in the compression space S1, and discharges it to the discharge space S3.

The cylinder module 31 includes a cylinder 311 , a cylinder inner space 312 , a bearing 313 and a plate portion 314 .

The cylinder bore 311 is formed in a cylindrical shape.

In the illustrated embodiment, the cylinder bore 311 is formed in a cylindrical shape extending laterally.

However, the cylinder tube 311 is not limited to the form shown, and may be formed in various forms. For example, the cylinder bore 311 may be formed as a V-shaped cylinder bore 311 .

A hollow is formed inside the cylinder tube 311 . Hereinafter, the hollow space will be referred to as "cylinder inner space 312".

The cylinder inner space 312 accommodates the piston 32 described later.

The inner wall of the cylinder inner space 312 will be ground. Therefore, the reciprocating motion of the piston 32 inserted into the cylinder inner space 312 can be made smoother.

The bearing 313 supports the rotational movement of the rotating shaft 50 to be described later.

The bearing 313 is coupled to the outer circumference of the rotating shaft 50 . Specifically, the bearing 313 is coupled to the outer circumference of the support portion 51 of the rotating shaft 50 .

The bearing 313 is formed around the rotation shaft 50 .

A plate portion 314 is coupled to one side of the bearing 313 .

The plate portion 314 is configured as a part of the outer circumference of the cylinder tube 311 .

In the illustrated embodiment, the plate portion 314 is formed in a plate shape extending laterally from one side of the bearing 313 .

However, the plate portion 314 is not limited to the form shown, and may be formed in various forms.

A piston 32 is inserted into the cylinder block 31 . Specifically, the piston 32 is inserted into the cylinder inner space 312 .

The piston 32 reciprocates in the cylinder inner space 312, and compresses the refrigerant in the compression space S1. Specifically, the piston 32 reciprocates while being in close contact with the inner wall of the cylinder inner space 312 .

The reciprocating compressor 1 is classified into a vertical compressor or a horizontal compressor according to the reciprocating direction of the piston 32 .

In the embodiment shown, the piston 32 reciprocates laterally. Therefore, the reciprocating compressor 1 corresponds to a horizontal compressor.

However, the piston 32 is not limited to the direction of reciprocation shown and may reciprocate in a variety of directions.

Additionally, in the illustrated embodiment, the piston 32 is formed in a cylindrical shape.

However, the piston 32 is not limited to the form shown, and may be formed in various forms. For example, the piston 32 may be formed in a disc shape.

The end of the piston 32 opposite to the rotation shaft 50 and one surface of the cylinder 311 are in an opposing relation to each other.

When the one end of the piston 32 and the one surface of the cylinder 311 are closest to each other, a gap is formed between the one end of the piston 32 and the one surface of the cylinder 311 .

That is, when the volume of the compression space S1 is the smallest, the one end of the piston 32 and the one surface of the cylinder 311 are spaced apart from each other.

In addition, a gap is also formed between the outer circumference of the piston 32 and the inner circumference of the cylinder 311 .

Therefore, the one end of the piston 32 and the one surface of the cylinder 311 can be prevented from colliding with each other. Thereby, damage to the piston 32 and the cylinder 311 can also be prevented.

However, when the gap is excessively increased, the compression efficiency of the refrigerant may be lowered.

Specifically, when the gap is excessively increased, the temperature of the cylinder bore 311 and the discharged refrigerant may increase. This causes deterioration and carbonization of the oil 21 , and increases the amount of residues of the oil 21 adhering to the cylinder bore 311 and the piston 32 . As a result, the volumetric efficiency of the cylinder bore 311 may be lowered, and the performance of the reciprocating compressor 1 may be lowered.

Therefore, the smaller the clearance is, the more advantageous it is in terms of the performance of the reciprocating compressor 1 . Thus, the clearance should be appropriately adjusted according to preset driving conditions of the reciprocating compressor 1 .

In one embodiment, a liner (not shown) of the cylinder 311 may be provided between the outer circumference of the piston 32 and the inner circumference of the cylinder 311 .

The inner tube of the cylinder tube 311 prevents abrasion of the outer circumference of the piston 32 and the inner wall of the cylinder tube 311 .

The inner circumference of the cylinder 311 is formed in a shape corresponding to the outer circumference of the piston 32 . In addition, the outer periphery of the inner pot of the cylinder tube 311 is formed in a shape corresponding to the inner wall of the cylinder tube 311 .

In one embodiment, the inner pot of the cylinder 311 may be formed in a cylindrical shape with a hollow inside.

The inner liner of the cylinder tube 311 reduces the contact surface between the piston 32 and the cylinder tube 311 , and guides the reciprocating motion of the piston 32 .

Therefore, the damage of the piston 32 and the cylinder 311 caused by the friction between the piston 32 and the cylinder 311 can be prevented.

In addition, when the inner liner of the cylinder tube 311 is worn out, it is only necessary to replace the inner liner of the cylinder tube 311 to perform repairs without replacing the piston 32 and the cylinder tube 311 .

When the piston 32 moves toward the rotating shaft 50, the volume of the compression space S1 formed by the piston 32 and the cylinder 311 increases and the pressure decreases. Therefore, the refrigerant flows into the compression space S1 through the refrigerant suction pipe 11 and the suction space S2 in this order.

Conversely, when the piston 32 moves in the opposite direction to the rotation shaft 50, the volume of the compression space S1 decreases and the pressure increases. Therefore, the pressure of the refrigerant in the compression space S1 increases, and the refrigerant is discharged to the outside of the reciprocating compressor 1 through the discharge space S3 and the refrigerant discharge pipe 12 in this order.

In the illustrated embodiment, as the piston 32 moves toward the right, the volume of the compression space S1 increases and the pressure decreases. Conversely, when the piston 32 moves toward the left, the volume of the compression space S1 decreases and the pressure increases.

On the other hand, the piston 32 includes a piston pin 321 and a connecting rod 322 .

The piston pin 321 is a device connecting the piston 32 and the connecting rod 322 .

The piston pin 321 is provided inside the piston 32 .

The piston pin 321 is formed in a cylindrical shape.

In one embodiment, a hollow is formed inside the piston pin 321 . Therefore, the weight of the piston 32 can be further reduced. Furthermore, the weight of the reciprocating compressor 1 can be further reduced.

The oil 21 is supplied to the piston pin 321 . Therefore, during the reciprocating motion of the piston 32, the piston pin 321 can be moved smoothly.

The piston pin 321 and the connecting rod 322 are combined. Specifically, the piston pin 321 and one end of the connecting rod 322 are combined.

Therefore, the connecting rod 322 is coupled to the piston 32 in a relatively movable manner.

The connecting rod 322 converts the rotational motion of the rotary shaft 50 into the reciprocating motion of the piston 32 .

The link 322 extends in one direction.

The link 322 is not limited to the illustrated form, and may be formed in various forms. For example, the link 322 may be formed in a shape in which an H-shaped cross section extends in a predetermined direction.

One end of the connecting rod 322 is coupled with the piston 32 . Specifically, one end of the connecting rod 322 is coupled with the piston pin 321 .

The other end of the link 322 is coupled to the rotation shaft 50 in a relatively rotatable manner.

In short, the connecting rod 322 connects the piston 32 and the rotating shaft 50 by being coupled to the piston pin 321 and the rotating shaft 50, respectively.

In one embodiment, an oil 21 supply portion (not shown) may be formed inside the connecting rod 322 . At this time, the oil 21 supply portion forms a flow path for supplying the oil 21 to the inside of the piston 32 .

Hereinafter, the drive motor 40 that supplies mechanical energy to the compression unit 30 will be described.

The drive motor 40 receives electrical energy from the outside, converts it into mechanical energy, and transmits it to the compression unit 30 .

The drive motor 40 includes a stator 41 and a rotor 42 .

The stator 41 is inserted into and fixed to the inner space of the casing 10 .

The stator 41 is formed in a cylindrical shape.

The stator 41 includes an iron core and a coil wound around the iron core. At this time, the coil is connected to the external power source of the reciprocating compressor 1 so as to be energizable.

The rotor 42 is rotatably provided inside the stator 41 . Specifically, the rotor 42 is rotatably provided in the hollow portion formed in the center portion of the iron core of the stator 41 .

A predetermined gap is formed between the outer circumference of the rotor 42 and the inner circumference of the stator 41 . Therefore, during the rotation of the rotor 42, the rotor 42 and the stator 41 do not collide.

The rotor 42 is formed in a cylindrical shape.

Permanent magnets are embedded in the rotor 42 . At this time, the permanent magnets extend in the same direction as the extending direction of the rotor 42 .

A rotating shaft 50 is coupled to the center of the rotor 42 .

The rotating shaft 50 transmits the energy received from the drive motor 40 to the connecting rod 322 and the piston 32 . Specifically, during driving of the drive motor 40 , the rotary shaft 50 performs a rotational motion, and transmits mechanical energy to the connecting rod 322 and the piston 32 . At this time, the piston 32 that has received the energy reciprocates.

The rotating shaft 50 extends in a predetermined direction. The predetermined direction is a direction different from the extending direction of the link 322 .

The rotating shaft 50 is coupled to the piston 32 so as to be relatively rotatable via the connecting rod 322 . Specifically, one end of the connecting rod 322 is coupled to the rotating shaft 50 in a relatively rotatable manner, and the other end of the connecting rod 322 is coupled to the piston 32 .

The rotating shaft 50 includes a support portion 51 , an eccentric portion 52 , a balance portion 53 , and an oil supply passage 54 .

The support portion 51 is inserted into the inside of the rotor 42 and guides the rotational movement of the rotating shaft 50 .

The support portion 51 is formed in a cylindrical shape extending in a predetermined direction.

The support portion 51 is rotatably inserted into the center portion of the bearing 313 of the cylinder block 31 . At this time, the support portion 51 is radially supported by the bearing 313 .

An eccentric portion 52 is formed at one end of the support portion 51 . Specifically, the eccentric portion 52 is formed radially eccentric with respect to the support portion 51 . That is, the central axis of the eccentric portion 52 and the central axis of the support portion 51 are not arranged on a straight line.

Therefore, during the rotation of the support portion 51, the eccentric portion 52 and the support portion 51 are rotated together.

The eccentric portion 52 is formed in a cylindrical shape extending in the same direction as the extending direction of the support portion 51 . At this time, the eccentric portion 52 extends from the one end of the support portion 51 in a direction opposite to the support portion 51 .

The link 322 and the balancer 60 are coupled to the outer periphery of the eccentric portion 52 .

The eccentric portion 52 is rotatable relative to the link 322 . Conversely, during the rotation of the eccentric portion 52, the balancer 60 and the eccentric portion 52 rotate together.

In summary, during the rotation of the eccentric portion 52, although the balancer 60 and the eccentric portion 52 rotate together, the link 322 does not rotate together with the eccentric portion 52, but performs an eccentric rotational motion.

A balance portion 53 is arranged between the eccentric portion 52 and the support portion 51 .

The balance portion 53 counteracts a part of the unbalanced force generated during the movement of the piston 32 and the rotary shaft 50 .

The balance portion 53 is formed at the one end of the support portion 51 .

The balance portion 53 is formed to expand from the one end of the support portion 51 toward the radially outer side of the support portion 51 .

An oil supply passage 54 is formed inside the support portion 51 , the eccentric portion 52 , and the balance portion 53 .

The oil supply passage 54 supplies the oil 21 to the rotary shaft 50 to smoothly rotate the rotary shaft 50 .

The oil supply passage 54 communicates with the inside of the oil supply device 20 . Thereby, a movement path of the oil 21 supplied from the oil storage space S4 to the rotary shaft 50 and the piston 32 via the oil supply device 20 is formed.

In one embodiment, the oil supply passage 54 may be connected to the oil 21 supply of the connecting rod 322 and piston 32 .

During the movement of the rotating shaft 50 and the piston 32, an unbalanced force may be generated.

In order to reduce this unbalanced force, an additional balancer 60 is provided on the rotating shaft 50 .

The balancer 60 is penetratingly coupled to the rotating shaft 50 and rotates together with the rotating shaft 50 .

The balancer 60 will be described in more detail later (refer to FIGS. 7 to 11 ).

Hereinafter, referring to FIGS. 2 to 6 , the coupling relationship between the piston 32 , the rotating shaft 50 and the balancer 60 will be described in more detail.

As described above, the piston 32 is coupled to the rotating shaft 50 via the connecting rod 322 .

Specifically, one end of the connecting rod 322 is coupled to the piston 32 , and the other end is coupled to the rotating shaft 50 in a relatively rotatable manner.

In addition, a balancer 60 is coupled to the outer circumference of the rotating shaft 50 . Specifically, the balancer 60 is coupled to the outer periphery of the eccentric portion 52 .

The balancer 60 penetrates through the eccentric portion 52 of the rotating shaft 50 and rotates together with the rotating shaft 50 .

At this time, the outer circumference of the rotating shaft 50 and the inner circumference of the coupling hole 611 of the balancer 60 to be described later are arranged adjacent to each other.

In one embodiment, the balancer 60 may be combined with the outer circumference of the eccentric portion 52 by hot pressing.

In another embodiment, the balancer 60 can be coupled to the outer periphery of the eccentric portion 52 by inserting the eccentric portion 52 into the coupling hole 611 .

The balancer 60 is not limited to the illustrated embodiment, and may be formed in various forms.

In the illustrated embodiment, the balancer 60 is arranged above the link 322 .

In an example not shown, the balancer 60 may be arranged below the link 322 .

Hereinafter, the balancer 60 will be described in more detail with reference to FIGS. 2 to 11 .

The balancer 60 includes a coupling portion 61 and an eccentric mass portion 62 .

The coupling portion 61 is a member directly coupled to the eccentric portion 52 of the rotating shaft 50 .

The coupling portion 61 is formed in a plate shape with a predetermined cross section extending in the height direction of the rotating shaft 50 .

The joint portion 61 is formed to extend toward the radially outer side of the eccentric portion 52 and to expand.

The coupling portion 61 is coupled to the outer periphery of the eccentric portion 52 .

A coupling hole 611 is formed through the central portion of the coupling portion 61 .

The coupling hole 611 is a hollow formed with a predetermined cross section extending in the height direction of the rotating shaft 50 .

The inner peripheral surface of the coupling hole 611 is in contact with the outer peripheral surface of the eccentric portion 52 . At this time, the inner circumference of the coupling hole 611 is formed in a shape corresponding to the outer circumference of the eccentric portion 52 .

Therefore, the coupling portion 61 can be firmly coupled to the outer periphery of the eccentric portion 52 .

In the illustrated embodiment, the coupling hole 611 is provided with a protrusion formed to protrude toward the eccentric portion 52 . At this time, a plurality of the protrusions are provided in one coupling hole 611 .

The protrusions are formed in shapes corresponding to the recesses formed on the outer peripheral surface of the eccentric portion 52 . Therefore, the protrusion and the concave portion of the eccentric portion 52 can be snapped and combined with each other.

That is, the coupling portion 61 and the eccentric portion 52 may be coupled in concave and convex. Thereby, the balancer 60 can be prevented from rotating with respect to the eccentric portion 52 while the rotating shaft 50 is rotating.

The coupling hole 611 is not limited to the illustrated form, and may be formed in various forms. For example, the coupling hole 611 may be a hollow formed with a circular cross section extending in the height direction of the rotating shaft 50 . At this time, by inserting the eccentric portion 52 into the coupling hole 611 , the coupling hole 611 can be coupled to the eccentric portion 52 .

An eccentric mass portion 62 is coupled to one side of the coupling portion 61 .

The eccentric mass portion 62 extends from the one side of the coupling portion 61 toward the radially inner side of the support portion 51 .

In the illustrated embodiment, the eccentric mass portion 62 and the coupling hole 611 are spaced apart from each other. However, the eccentric mass portion 62 is not limited to the form shown in the figure, and may be formed in various forms. For example, the eccentric mass portion 62 may be arranged adjacent to the coupling hole 611 .

In an embodiment of the present invention, one surface of the eccentric mass portion 62 opposite to the upper casing 110 in the height direction of the rotating shaft 50 is inclined toward the opposite direction to the upper casing 110 . That is, when viewed from the side, the eccentric mass portion 62 is formed obliquely (refer to FIGS. 2 and 7 to 9 ).

The one surface may be formed as a flat surface or a curved surface.

In the case where the one surface is formed as a curved surface, at least a part of the one surface may be formed in a shape corresponding to the inner circumference of the upper case 110 . Preferably, the entirety of the one surface may be formed in a shape corresponding to the inner circumference of the upper case 110 .

In another embodiment of the present invention, one surface of the eccentric mass portion 62 opposite to the upper case 110 in the height direction of the rotating shaft 50 is bent by a predetermined angle in a direction opposite to the upper case 110 . That is, when the eccentric mass portion 62 is viewed from the side, a part of the one surface is formed obliquely (see FIGS. 3 and 10 ).

At this time, the predetermined angle is larger than 0 degrees and smaller than 90 degrees.

In the one surface, a portion located on the radially outer side of the eccentric portion 52 may be formed as a flat surface or a curved surface with reference to the bending line.

In the case where the part of the one surface is formed as a curved surface, the part may be formed in a shape corresponding to the inner circumference of the upper case 110 .

In addition, in the said one surface, the remaining part located in the radial inner side of the eccentric part 52 is formed as a flat surface with reference to the bending line.

At this time, the remaining portion of the one surface may be formed as a plane parallel to the radial direction of the eccentric portion 52 .

In another embodiment of the present invention, the eccentric mass portion 62 and the protruding portion 111 of the upper case 110 overlap in the height direction of the rotating shaft 50 (refer to FIGS. 4 and 11 ).

In the other embodiment, a protrusion 111 is formed in a part of the upper case 110 .

The protruding portion 111 protrudes in a direction opposite to the eccentric mass portion 62 .

The protruding portion 111 is formed in a shape corresponding to the eccentric mass portion 62 .

In the embodiments shown in FIGS. 4 and 11 , the upper and lower surfaces of the eccentric mass portion 62 are formed as planes parallel to the radial direction of the eccentric portion 52 . At this time, the protruding portion 111 is formed in a shape corresponding to the eccentric mass portion 62 .

However, the eccentric mass portion 62 and the protruding portion 111 are not limited to the illustrated embodiment, and may be formed in various forms.

In a not-shown embodiment, one surface of the eccentric mass portion 62 opposite to the housing 10 in the height direction of the rotating shaft 50 may be bent in the opposite direction to the housing 10, and the protruding portion 111 may be formed to be opposite to the housing 10. The corresponding shape of the eccentric mass portion 62 .

As a result, in the embodiment of the present invention, the interval between the eccentric mass portion 62 and the inner circumference of the upper case 110 can be further reduced.

In particular, when one surface of the eccentric mass portion 62 facing the housing 10 in the height direction of the rotating shaft 50 is formed in a shape corresponding to the inner circumference of the housing 10, the eccentric mass portion 62 and the upper case 110 can be The interval between inner weeks is minimized.

In addition, the center of weight of the eccentric mass portion 62 can move toward the central axis of the support portion 51 .

Therefore, when the rotating shaft 50 rotates, the absolute value of the balance force generated by the balancer 60 can be further increased. That is, when the reciprocating compressor 1 is driven, the balance force generated by the balancer 60 can be sufficiently ensured.

Thereby, the driving force generated during the movement of the rotary shaft 50 and the piston 32 and the balancing force generated by the balancer 60 complement each other, and the total unbalanced force can be further reduced.

Furthermore, the vibration of the rotating shaft 50 and the piston 32 can be further reduced.

Also, the noise caused by vibration can be further reduced.

As a result, while reducing the space between the balancer 60 and the upper case 110 , the design limitation of the balancer 60 can be overcome, and the vibration of the rotating shaft 50 can be reduced.

On the other hand, the interval between the eccentric mass portion 62 and the inner circumference of the upper casing 110 may be adjusted according to preset driving conditions of the reciprocating compressor 1 .

One surface of the eccentric mass portion 62 facing the upper case 110 in the height direction of the rotation shaft 50 and the inner circumference of the upper case 110 are spaced apart from each other.

The uppermost end of the one surface of the eccentric mass portion 62 in the height direction of the rotation shaft 50 is spaced apart from the inner circumference of the upper case 110 by the first interval g1 in the height direction of the rotation shaft 50 .

That is, the first interval g1 refers to the distance in the height direction of the rotation shaft 50 between the uppermost end of the one surface and the inner circumference of the upper case 110 .

In addition, the lowermost end of the one surface of the eccentric mass portion 62 in the height direction of the rotating shaft 50 is spaced apart from the inner circumference of the upper case 110 by a second gap g2 in the height direction of the rotating shaft 50 .

That is, the second interval g2 refers to the distance in the height direction of the rotation shaft 50 between the lowermost end of the one surface and the inner circumference of the upper case 110 .

At this time, the value obtained by dividing the first interval g1 by the second interval g2 is a predetermined predetermined interval ratio.

The prescribed interval ratio may be adjusted according to preset driving conditions of the reciprocating compressor 1 .

Therefore, the first interval g1 and the second interval g2 can be formed at the interval ratio most suitable for the preset driving conditions. That is, the predetermined interval ratio can be formed as the interval ratio most suitable for the preset driving conditions.

In one embodiment, the predetermined interval ratio is 0.9 or more and 1.1 or less.

In another embodiment, the one surface of the eccentric mass portion 62 is formed in a shape corresponding to the inner circumference of the upper case 110 , and the predetermined interval ratio is 1.

The balancing process of the balancer 60 during the rotational movement of the rotating shaft 50 will be described in more detail below with reference to FIG. 12 .

In the graph shown in FIG. 12 , the dashed-dotted line represents the unbalanced force Fun generated during the movement of the rotary shaft 50 and the piston 32 , the broken line represents the balance force Fbw for counteracting the unbalanced force, and the solid line represents the unbalanced force Fbw on the rotary shaft The resultant force of the unbalanced force Fun generated during the movement of the piston 50 and the piston 32 and the balance force Fbw for counteracting the unbalanced force, that is, the final unbalanced force Fun+Fbw.

As described above, the rotary shaft 50 performs rotational motion by receiving mechanical energy from the drive motor 40 .

The rotating shaft 50 is provided with an eccentric portion 52 , and the piston 32 is coupled to one side of the rotating shaft 50 , so the rotating shaft 50 is unbalanced in weight.

Therefore, during the rotational movement of the rotary shaft 50, the rotary shaft 50 and the piston 32 are rotated in an eccentric state. As a result, the rotating shaft 50 and the piston 32 may be vibrated by centrifugal force. That is, during the rotational movement of the rotational shaft 50 , an unbalanced force may be generated between the rotational shaft 50 and the piston 32 .

In the graph shown in FIG. 12 , the unbalanced force Fun generated during the movement of the rotary shaft 50 and the piston 32 is an elliptical shape that is eccentric in a specific direction.

The balancer 60 may be coupled to the rotating shaft 50 , or a balance portion 53 may be formed on the rotating shaft 50 by itself to cancel out the unbalanced force Fun generated during the movement of the rotating shaft 50 and the piston 32 .

In the graph shown in FIG. 12 , the balance force Fbw for canceling the unbalanced force is in the shape of a circle centered on the coordinates (0, 0).

As described above, in the embodiment of the present invention, the interval between the balancer 60 and the upper case 110 can be further reduced, and the center of weight can be moved toward the center axis of the support portion 51 .

Therefore, the mass point of the balancer 60 can also be moved toward the center axis of the support portion 51 .

Thereby, the distance from the center axis of the support portion 51 to the mass point of the balancer 60 can be further reduced.

As a result, the size of Fbw can be increased.

In the graph shown in FIG. 12 , when compared with the conventional balancer, there is little variation in the magnitude of the final unbalanced force Fun+Fbw.

That is, when compared with the existing balancer, the unbalanced force Fun generated during the movement of the rotary shaft 50 and the piston 32 is sufficiently compensated by the balance force Fbw for counteracting the unbalanced force.

At this time, the final unbalanced force Fun+Fbw cannot become 0, and it is designed to minimize it.

As described above, in the reciprocating compressor 1 of the present invention, the absolute values of Fbwx and Fbwy can be further increased.

Therefore, the absolute value of Funx+Fbwx can be increased and the absolute value of Funy+Fbwy can be decreased. That is, the variation in the magnitude of the final unbalanced force Fun+Fbw can be further reduced.

Thereby, vibration and noise generated by the rotary shaft 50 and the piston 32 during the rotational movement of the rotary shaft 50 can be further reduced.

As described above, the preferred embodiments of the present invention have been described, but the present invention is not limited to the configurations of the above-described embodiments.

In addition, various modifications and changes can be made to the present invention by those skilled in the art without departing from the spirit and scope of the present invention described in the appended claims.

In addition, a plurality of the described embodiments may be constructed by selectively combining all or part of the respective embodiments to realize various modifications.

Claims (15)

1. A reciprocating compressor, comprising:

a piston;

a rotating shaft coupled to the piston so as to be rotatable relative to the piston;

a balancer that is coupled to the rotating shaft and rotates together with the rotating shaft; and

a housing accommodating the piston, the rotary shaft, and the balancer therein,

the rotating shaft includes:

a support part extending in one direction; and

an eccentric portion formed to extend in the one direction from one end of the support portion, and a central axis of the eccentric portion and a central axis of the support portion are not arranged on a straight line,

the balancer includes:

a coupling portion formed by extending and expanding from a coupling hole contacting an outer circumferential surface of the eccentric portion toward a radial outer side of the eccentric portion; and

an eccentric mass part coupled to one side of the coupling part, extending toward a radially inner side of the support part, and one surface of the eccentric mass part opposite to the housing in a height direction of the rotation shaft is inclined toward a direction opposite to the housing.

2. The reciprocating compressor of claim 1, wherein,

the one surface of the eccentric mass portion is formed as a curved surface.

3. The reciprocating compressor of claim 2, wherein,

at least a portion of the one surface of the eccentric mass portion is formed in a shape corresponding to an inner circumferential surface of the housing.

4. The reciprocating compressor of claim 1, wherein,

the one surface of the eccentric mass portion is formed as a plane.

5. The reciprocating compressor of claim 1, wherein,

an uppermost end of the one surface of the eccentric mass portion in a height direction of the rotating shaft is spaced apart from an inner circumferential surface of the housing by a first interval in the height direction of the rotating shaft,

a lowermost end of the one surface of the eccentric mass portion in a height direction of the rotating shaft is spaced apart from an inner circumferential surface of the housing by a second interval in the height direction of the rotating shaft,

a value obtained by dividing the first interval by the second interval is a preset predetermined interval ratio.

6. The reciprocating compressor of claim 5,

the predetermined spacing ratio is 0.9 or more and 1.1 or less.

7. A reciprocating compressor, comprising:

a piston;

a rotating shaft extending in one direction and coupled to the piston so as to be rotatable relative to the piston;

a balancer coupled to an outer circumference of the rotating shaft and rotating together with the rotating shaft; and

a housing accommodating the piston, the rotary shaft, and the balancer therein,

the rotating shaft includes:

a support portion extending in the one direction; and

an eccentric portion formed to extend in the one direction from one end of the support portion, and a central axis of the eccentric portion and a central axis of the support portion are not arranged on a straight line,

the balancer includes:

a coupling portion formed by extending and expanding from a coupling hole contacting an outer circumferential surface of the eccentric portion toward a radial outer side of the eccentric portion; and

an eccentric mass part coupled to one side of the coupling part and extending toward a radial inner side of the support part,

one surface of the eccentric mass portion facing the housing in a height direction of the rotating shaft is bent at a predetermined angle in a direction opposite to the housing.

8. The reciprocating compressor of claim 7,

in the one surface of the eccentric mass portion, a portion located radially outside the eccentric portion is formed as a curved surface with reference to a bending line.

9. The reciprocating compressor of claim 8,

the portion of the eccentric mass portion is formed in a shape corresponding to an inner circumferential surface of the housing.

10. The reciprocating compressor of claim 7,

in the one surface of the eccentric mass portion, a portion located radially outside the eccentric portion is formed as a flat surface with reference to a bending line.

11. The reciprocating compressor of claim 7,

an uppermost end of the one surface of the eccentric mass portion in a height direction of the rotating shaft is spaced apart from an inner circumferential surface of the housing by a first interval in the height direction of the rotating shaft,

a lowermost end of the one surface of the eccentric mass portion in a height direction of the rotating shaft is spaced apart from an inner circumferential surface of the housing by a second interval in the height direction of the rotating shaft,

a value obtained by dividing the first interval by the second interval is a preset predetermined interval ratio.

12. The reciprocating compressor of claim 11, wherein,

the predetermined spacing ratio is 0.9 or more and 1.1 or less.

13. A reciprocating compressor, comprising:

a piston formed in a cylindrical shape;

a rotating shaft coupled to the piston so as to be rotatable relative to the piston;

a balancer that is coupled to the rotating shaft and rotates together with the rotating shaft; and

a housing accommodating the piston, the rotating shaft, and the balancer therein, a protrusion being formed at a portion of the housing,

the rotating shaft includes:

a support part extending in one direction; and

an eccentric portion formed to extend in the one direction from one end of the support portion, and a central axis of the eccentric portion and a central axis of the support portion are not arranged on a straight line,

the balancer includes:

a coupling portion formed by extending and expanding from a coupling hole contacting an outer circumferential surface of the eccentric portion toward a radial outer side of the eccentric portion; and

an eccentric mass part coupled to one side of the coupling part and extending toward a radial inner side of the support part,

the protrusion portion and the eccentric mass portion are overlapped in a height direction of the rotating shaft, the protrusion portion protrudes toward a direction opposite to the eccentric mass portion, and the protrusion portion is formed in a shape corresponding to the eccentric mass portion.

14. The reciprocating compressor of claim 13,

the rotating shaft includes a balance portion disposed between the support portion and the eccentric portion and formed to be expanded from the one end of the support portion toward a radially outer side of the support portion.

15. The reciprocating compressor of claim 14, wherein,

the piston includes a connecting rod extending in a direction different from the one direction, one end of the connecting rod is coupled to the piston, and the other end thereof is coupled to the eccentric portion so as to be rotatable with respect to the eccentric portion.

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