CN114370385B

CN114370385B - Reciprocating compressor

Info

Publication number: CN114370385B
Application number: CN202011374084.7A
Authority: CN
Inventors: 孙映夫; 朴馥安; 朴仁范; 金敬晧
Original assignee: LG Electronics Inc
Current assignee: LG Electronics Inc
Priority date: 2020-10-15
Filing date: 2020-11-30
Publication date: 2023-09-12
Anticipated expiration: 2040-11-30
Also published as: KR102344890B1; DE102021108327A1; CN114370385A

Abstract

The present invention discloses a reciprocating compressor capable of minimizing unbalanced force generated during movement of a rotary shaft and a piston, wherein the reciprocating compressor comprises: a piston; a rotation shaft; and a balancer coupled to the rotation shaft in a penetrating manner and rotated together with the rotation shaft, the balancer including: a coupling portion extending radially outward of the rotation shaft from a coupling hole in contact with an outer peripheral surface of the rotation shaft and expanding; and an eccentric mass portion coupled to one side of the coupling portion, and one surface of the eccentric mass portion 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 a reciprocating compressor, and more particularly, to a reciprocating compressor capable of minimizing an unbalance force generated during movement of a rotary shaft and a piston.

Background

A compressor refers to a device that discharges a fluid of high pressure by compressing the fluid, or that operates a machine using energy generated when discharging the fluid of high pressure.

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

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

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

Therefore, in order to reduce such unbalanced forces, an additional balancer may be provided at the rotation shaft.

Here, the balancer refers to a balancing device attached to an outer circumference of the rotating body to balance the rotating body.

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

However, in the conventional reciprocating compressor, there is a minimum interval between the housing and the balancer. 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 balancing member located at a boundary portion of a main shaft portion and a crank portion of a crank member is disclosed.

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

Korean laid-open patent publication No. 20-0126118 discloses a reciprocating compressor. Specifically, disclosed is a reciprocating compressor provided with an eccentric portion that is provided to a rotating shaft in an eccentric manner to the rotating shaft, and a weight balancer that counteracts an imbalance in force generated by an eccentric rotational movement of the eccentric portion.

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)

Korean patent laid-open publication No. 20-0126118 (1998.07.03)

Disclosure of Invention

An object of the present utility model is to provide a reciprocating compressor capable of minimizing an unbalance force generated during a movement of a rotary shaft and a piston.

Another object of the present utility model is to provide a reciprocating compressor capable of further reducing a space between a housing and a balancer and further increasing a balancing effect of the balancer.

Another object of the present invention is to provide a reciprocating compressor that makes a space between one end of a balancer and a housing and a space between the other end of the balancer and the housing at a space ratio most suitable for a preset driving condition.

To achieve the object, a reciprocating compressor according to an embodiment of the present invention includes: a piston; a rotary shaft rotatably coupled to the piston; a balancer connected to the rotation shaft in a penetrating manner and rotated together with the rotation shaft; and a housing accommodating the piston, the rotation shaft, and the balancer therein, the rotation shaft including: a support portion extending in one direction; and an eccentric portion formed to extend from one end of the support portion in the one direction, and a center axis of the eccentric portion and a center axis of the support portion are not arranged on a straight line, the balancer including: a coupling portion extending radially outward of the eccentric portion from a coupling hole in contact with an outer peripheral surface of the eccentric portion and expanding; and an eccentric mass portion coupled to one side of the coupling portion, extending toward a radial inner side of the supporting portion, and one surface of the eccentric mass portion opposite to the housing in a height direction of the rotation shaft is inclined toward 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 portion of the one surface of the eccentric mass portion may be formed in a shape corresponding to an inner peripheral surface of the housing.

In addition, the one surface of the eccentric mass portion may be formed in a plane.

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

The predetermined interval ratio may be 0.9 or more and 1.1 or less.

In addition, a reciprocating compressor of another embodiment of the present invention includes: a piston; a rotation shaft extending in one direction and coupled to the piston so as to be rotatable with respect to the piston; a balancer coupled to an outer circumference of the rotation shaft and rotated together with the rotation shaft; and a housing accommodating the piston, the rotation shaft, and the balancer therein, the rotation shaft including: a support portion extending in the one direction; and an eccentric portion formed to extend from one end of the support portion in the one direction, and a center axis of the eccentric portion and a center axis of the support portion are not arranged on a straight line, the balancer including: a coupling portion extending radially outward of the eccentric portion from a coupling hole in contact with an outer peripheral surface of the eccentric portion and expanding; and an eccentric mass portion coupled to one side of the coupling portion and extending radially inward of the support portion, wherein one surface of the eccentric mass portion facing the housing in a height direction of the rotation shaft is bent by a predetermined angle in a direction opposite to the housing.

In addition, a portion of the one surface of the eccentric mass portion, which is located radially outward of the eccentric portion with respect to a bending line, may be formed as a curved surface.

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

In addition, in the one surface of the eccentric mass portion, a portion located radially outward of the eccentric portion may be formed as a plane with respect to a bending line.

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

The predetermined interval ratio may be 0.9 or more and 1.1 or less.

In addition, a reciprocating compressor of another embodiment of the present invention includes: a piston formed in a cylindrical shape; a rotary shaft rotatably coupled to the piston; a balancer connected to the rotation shaft in a penetrating manner and rotated together with the rotation shaft; and a housing accommodating the piston, the rotation shaft, and the balancer therein, a projection being formed at a portion of the housing, the rotation shaft including: a support portion extending in one direction; and an eccentric portion formed to extend from one end of the support portion in the one direction, and a center axis of the eccentric portion and a center axis of the support portion are not arranged on a straight line, the balancer including: a coupling portion extending radially outward of the eccentric portion from a coupling hole in contact with an outer peripheral surface of the eccentric portion and expanding; and an eccentric mass portion coupled to one side of the coupling portion and extending toward a radial inner side of the supporting portion, the protrusion portion and the eccentric mass portion overlapping in a height direction of the rotation shaft, the protrusion portion protruding toward a direction opposite to the eccentric mass portion, the protrusion portion being formed in a shape corresponding to the eccentric mass portion.

In addition, the rotating shaft may include a balancing portion disposed between the supporting portion and the eccentric portion and formed to be expanded radially outward of the supporting portion from the one end of the supporting portion.

Further, a connecting rod may be included, extending in a direction different from the one direction, one end of the connecting rod being coupled to the piston, and the other end thereof being coupled to the eccentric portion in a relatively rotatable manner.

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 opposite to the housing is formed in a shape corresponding to the inner peripheral surface of the housing.

Accordingly, the balance 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 rotation shaft and the piston and the balance force generated by the balancer can be mutually offset, so that the total unbalance force can be minimized.

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

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

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

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

Therefore, the balance 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 an interval ratio most suitable for a preset driving condition.

Drawings

Fig. 1 is a sectional view illustrating a reciprocating compressor according to an embodiment of the present invention.

Fig. 2 is an enlarged sectional view illustrating the reciprocating compressor of fig. 1.

Fig. 3 is an enlarged sectional view showing a balancer of an embodiment of the present invention.

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

Fig. 5 is a side view illustrating the rotary shaft and the piston of fig. 1.

Fig. 6 is a top view illustrating the rotary shaft and the piston of fig. 1.

Fig. 7 is a perspective view illustrating the balancer of fig. 1.

Fig. 8 is a top view illustrating the balancer of fig. 1.

Fig. 9 is a sectional view illustrating the balancer of fig. 1.

Fig. 10 is a sectional view illustrating the balancer of fig. 3.

Fig. 11 is a sectional view illustrating the balancer of fig. 4.

Fig. 12 is a graph showing unbalanced forces generated during movement of a rotary shaft and a piston according to an embodiment of the present invention.

Description of the reference numerals

1: reciprocating compressor 10: shell body

110: upper shell 111: projection part

120: lower shell 11: refrigerant suction pipe

12: refrigerant discharge pipe 20: oil supply device

21: oil 30: compression part

31: cylinder module 311: cylinder barrel

312: cylinder inner space 313: bearing

314: plate portion 32: piston

321: piston pin 322: connecting rod

40: a drive motor 41: stator

42: rotor 50: rotary shaft

51: support portion 52: eccentric part

53: balance portion 54: oil supply passage

60: balancer 61: joint portion

611: the coupling hole 62: eccentric mass part

S1: compression space S2: suction space

S3: discharge space S4: oil storage space

g1: first interval g2: second interval

Detailed Description

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 to clarify the features of the present invention.

In this specification, even in the embodiments different from each other, the same reference numerals are given to the same components, and a repetitive description thereof will be omitted.

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

The expression in the singular includes the expression in the plural unless the context clearly indicates otherwise.

Hereinafter, a reciprocating compressor 1 according to an embodiment of the present invention will be described with reference to fig. 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 driving motor 40, a compression part 30, and a rotation shaft 50.

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

A space accommodating the oil supply device 20, the compression portion 30, the driving motor 40, and the rotation shaft 50 is formed inside the housing 10. That is, the oil supply device 20, the compression portion 30, the driving motor 40, and the rotation shaft 50 are accommodated inside the casing 10.

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

In the illustrated embodiment, the upper and lower shells 110 and 120 are formed in a dome (dome) shape. Specifically, the upper case 110 is formed in a dome shape bulging toward an upper side, and the lower case 120 is formed in a dome shape recessing toward a lower side.

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

The lower end of the upper case 110 is coupled with the upper end of the lower case 120. In one embodiment, the upper and lower shells 110 and 120 are joined by welding.

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

A compression space S1 is formed between one end of the piston 32 and the inner periphery 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 an 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 coupled 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 is then 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, and the oil 21 assists the smooth movement of the compression part 30 and the rotation shaft 50.

The oil storage space S4 is formed at a lower portion of the inner space of the housing 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 connected 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 case 120.

One side of the refrigerant suction pipe 11 is connected to the housing 10. 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 regulates 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, the suction valve is opened when the compression space S1 increases, and is closed when the compression space S1 decreases.

One side of the refrigerant discharge pipe 12 is connected to the casing 10 and is spaced apart from the refrigerant suction pipe 11. The other side of the refrigerant discharge pipe 12 is disposed outside the reciprocating compressor 1, and a refrigerant discharge port 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 to the outside from the discharge space S3, 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, in addition to the refrigerant, oil 21 is also supplied to the reciprocating compressor 1. Specifically, the oil 21 is supplied between the components moving inside the reciprocating compressor 1, thereby smoothly moving the components.

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

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

The oil supply device 20 sucks the oil 21 stored in the oil storage space S4, and moves the oil 21 into a rotation shaft 50 described later.

The oil supply device 20 is coupled to the lower side of the rotation 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 a description of the rotation shaft 50.

The lower end portion of the oil supply device 20 is disposed in the oil storage space S4. Specifically, the lower end portion of the oil supply device 20 extends downward to be immersed in the oil 21 in 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 portion 30 and the rotation portion.

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

However, the oil supply device 20 is not limited to the illustrated form, and may be formed in various forms. In an 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 portion 30 and the rotation shaft 50. After that, the oil 21 sucked into the compression portion 30 and the rotation shaft 50 falls down to the oil storage space S4 by the gravity.

As a result, the oil 21 in the oil storage space S4 repeats the following process: after being supplied to the compression unit 30 and the rotary shaft 50 by the oil supply device 20, the oil 21 is recovered to the oil storage space S4, and is circulated inside the reciprocating compressor.

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

The compression unit 30 compresses the refrigerant in the compression space S1 and discharges the compressed refrigerant to the discharge space S3.

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

The cylinder 311 is formed in a cylindrical shape.

In the illustrated embodiment, the cylinder 311 is formed in a cylindrical shape extending in the lateral direction.

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

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

The cylinder interior space 312 accommodates a piston 32 described later.

The inner wall of the cylinder inner space 312 is subjected to grinding. Therefore, the reciprocating motion of the piston 32 inserted into the cylinder tube internal space 312 can be made smoother.

The bearing 313 supports a rotational movement of the rotary shaft 50 described later.

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

The bearing 313 is formed to surround the rotation shaft 50.

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

The plate 314 is formed as a part of the outer periphery of the cylinder 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 illustrated form, and may be formed in various forms.

A piston 32 is inserted into the cylinder module 31. Specifically, the piston 32 is inserted into the cylinder tube 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 in a state of being closely attached to the inner wall of the cylinder tube 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 illustrated embodiment, the piston 32 reciprocates in a lateral direction. Thus, the reciprocating compressor 1 corresponds to a horizontal compressor.

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

In addition, 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.

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

When the one end of the piston 32 and the one surface of the cylinder 311 are closest, 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 minimum, the one end of the piston 32 and the one surface of the cylinder 311 are spaced apart from each other.

A gap is also formed between the outer periphery of the piston 32 and the inner periphery 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, if the gap is excessively increased, the compression efficiency of the refrigerant may be reduced.

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

Therefore, the smaller the gap, the more advantageous in terms of the performance of the reciprocating compressor 1. Thereby, the gap should be appropriately adjusted according to preset driving conditions of the reciprocating compressor 1.

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

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

The inner periphery of the cylinder 311 liner is formed in a shape corresponding to the outer periphery of the piston 32. The outer periphery of the inner tube of the cylinder 311 is formed in a shape corresponding to the inner wall of the cylinder 311.

In an embodiment, the cylinder 311 liner may be formed in a hollow cylindrical shape formed inside thereof.

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

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

In addition, in the case where the inner liner of the cylinder 311 is worn out, repair can be performed by replacing only the inner liner of the cylinder 311 without replacing the piston 32 and the cylinder 311.

When the piston 32 moves toward the rotation 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.

In contrast, 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, when 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 disposed 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. Further, the weight of the reciprocating compressor 1 can be further reduced.

The oil 21 is supplied to the piston pin 321. Accordingly, the piston pin 321 can be smoothly moved during the reciprocation of the piston 32.

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

Accordingly, 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 rotational 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 to the piston 32. Specifically, one end of the connecting rod 322 is coupled to the piston pin 321.

The other end of the link 322 is coupled to the rotation shaft 50 so as to be rotatable relative to each other.

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

In one embodiment, an oil 21 supply (not shown) may be formed inside the link 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 driving motor 40 for supplying mechanical energy to the compression unit 30 will be described.

The driving motor 40 receives electric power from the outside, converts it into mechanical power, and transmits it to the compressing part 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 housing 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 electrically connected to an external power source of the reciprocating compressor 1.

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

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

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 rotation shaft 50 is coupled to the center of the rotor 42.

The rotational shaft 50 transfers 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 rotary motion, and transmits mechanical energy to the connecting rod 322 and the piston 32. At this time, the piston 32, which receives the energy, reciprocates.

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

The rotary shaft 50 is coupled to the piston 32 via a connecting rod 322 so as to be rotatable relative to each other. Specifically, one end of the link 322 is coupled to the rotation shaft 50 so as to be relatively rotatable, and the other end of the link 322 is coupled to the piston 32.

The rotary 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 rotor 42 and guides the rotational movement of the rotation 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 a center portion of the bearing 313 of the cylinder module 31. At this time, the supporting 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 to be eccentric in the radial direction with respect to the support portion 51. That is, the center axis of the eccentric portion 52 and the center axis of the support portion 51 are not arranged on a straight line.

Therefore, during rotation of the support portion 51, the eccentric portion 52 and the support portion 51 rotate 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 toward the opposite direction to the support portion 51.

A link 322 and a balancer 60 are coupled to the outer circumference of the eccentric portion 52.

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

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

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

The balance portion 53 counteracts a portion 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 radially outward of the support portion 51 from the one end of the support portion 51.

An oil supply passage 54 is formed in 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, thereby smoothly rotating the rotary shaft 50.

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

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

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

In order to reduce such unbalanced forces, an additional balancer 60 is provided at the rotating shaft 50.

The balancer 60 is coupled to the rotation shaft 50 through the penetration, and rotates together with the rotation shaft 50.

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

The coupling relationship between the piston 32, the rotary shaft 50, and the balance 60 will be described in more detail below with reference to fig. 2 to 6.

As described above, the piston 32 is coupled to the rotation shaft 50 through 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 rotary shaft 50 in a relatively rotatable manner.

Further, a balancer 60 is coupled to the outer periphery of the rotary shaft 50. Specifically, the balancer 60 is coupled to the outer circumference of the eccentric portion 52.

The balancer 60 penetrates the eccentric portion 52 coupled to the rotation shaft 50 and rotates together with the rotation shaft 50.

At this time, the outer periphery of the rotation shaft 50 and the inner periphery of a coupling hole 611 of the balancer 60 described later are disposed adjacently.

In one embodiment, the balancer 60 may be coupled to the outer circumference of the eccentric part 52 by a hot pressing manner.

In another embodiment, the balancer 60 can be coupled to the outer circumference 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 disposed above the link 322.

In an embodiment not shown, the balancer 60 may be disposed below the link 322.

Hereinafter, the balancer 60 will be described in more detail with reference to fig. 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 rotation shaft 50.

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

The coupling portion 61 is formed to extend radially outward of the eccentric portion 52 and expand.

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

A coupling hole 611 is formed to penetrate the center of the coupling portion 61.

The coupling hole 611 is hollow with a predetermined cross section extending in the height direction of the rotation 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 portion Zhou Xing of the coupling hole 611 has a shape corresponding to the outer periphery 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, a protrusion protruding toward the eccentric portion 52 is provided in the coupling hole 611. At this time, a plurality of the protrusions are provided at one coupling hole 611.

The protrusions are formed in a shape corresponding to the concave portions formed on the outer circumferential surface of the eccentric portion 52. Thus, the protrusions and the depressions of the eccentric portion 52 can be engaged and coupled with each other.

That is, the coupling portion 61 and the eccentric portion 52 may be coupled with each other in a concave-convex manner. Thus, the balancer 60 can be prevented from rotating relative to the eccentric section 52 during rotation of the rotation shaft 50.

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 by extending a circular cross section in the height direction of the rotation shaft 50. At this time, the eccentric portion 52 is inserted into the coupling hole 611, whereby 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 illustrated form, and may be formed in various forms. For example, the eccentric mass portion 62 may be disposed 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 case 110 in the height direction of the rotation shaft 50 is inclined toward the opposite direction to the upper case 110. That is, the eccentric mass portion 62 is formed obliquely when viewed from the side (refer to fig. 2 and 7 to 9).

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

In the case where the one surface is formed as a curved surface, at least a portion of the one surface may be formed in a shape corresponding to the inner circumference of the upper case 110. Preferably, the one surface may be integrally 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 rotation shaft 50 is bent at a prescribed angle toward the opposite direction 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 (refer to fig. 3 and 10).

At this time, the predetermined angle is greater than 0 degrees and less than 90 degrees.

In the one surface, a portion located radially outside the eccentric portion 52 may be formed in a plane or a curved surface with reference to the bending line.

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

In addition, in the one surface, the remaining portion located radially inward of the eccentric portion 52 is formed as a plane based on 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 rotation shaft 50 (refer to fig. 4 and 11).

In the other embodiment, a protrusion 111 is formed at a portion of the upper case 110.

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

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

In the embodiment shown in fig. 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 an embodiment not shown, one surface of the eccentric mass portion 62 opposite to the housing 10 in the height direction of the rotation shaft 50 may be bent toward the opposite direction to the housing 10, and the protrusion 111 may be formed in a shape corresponding to 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 periphery of the upper case 110 can be further reduced.

In particular, when one surface of the eccentric mass portion 62 opposed to the housing 10 in the height direction of the rotation shaft 50 is formed in a shape corresponding to the inner periphery of the housing 10, the interval between the eccentric mass portion 62 and the inner periphery of the upper housing 110 can be minimized.

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

Therefore, when the rotation 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 rotation shaft 50 and the piston 32 and the balance force generated by the balancer 60 compensate each other, and the total unbalance force can be further reduced.

Further, the vibration of the rotary shaft 50 and the piston 32 can be further reduced.

Further, 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 restriction of the balancer 60 can be overcome, and the vibration of the rotation shaft 50 can be reduced.

On the other hand, the interval of the eccentric mass portion 62 from the inner circumference of the upper case 110 may be adjusted according to a preset driving condition of the reciprocating compressor 1.

One surface of the eccentric mass portion 62, which is opposite to the upper case 110 in the height direction of the rotation shaft 50, is spaced apart from the inner circumference of the upper case 110.

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 a first interval g1 in the height direction of the rotation shaft 50.

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

In addition, the lowermost 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 periphery of the upper case 110 by a second gap g2 in the height direction of the rotation shaft 50.

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

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

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

Accordingly, the first interval g1 and the second interval g2 may be formed as an interval ratio most suitable for a preset driving condition. That is, the prescribed interval ratio may be formed as an interval ratio most suitable for a preset driving condition.

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 prescribed interval ratio is 1.

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

In the graph shown in fig. 12, the chain line indicates the unbalanced force Fun generated during the movement of the rotary shaft 50 and the piston 32, the broken line indicates the balanced force Fbw for canceling the unbalanced force, and the solid line indicates the resultant force of the unbalanced force Fun generated during the movement of the rotary shaft 50 and the piston 32 and the balanced force Fbw for canceling the unbalanced force, that is, the final unbalanced force fun+fbw.

As described above, the rotation shaft 50 performs the rotation motion by receiving the mechanical energy from the driving motor 40.

Since the eccentric portion 52 is provided in the rotary shaft 50 and the piston 32 is coupled to one side of the rotary shaft 50, the rotary shaft 50 is unbalanced in weight.

Therefore, during the rotational movement of the rotation shaft 50, the rotation shaft 50 and the piston 32 rotate in an eccentric state. Thus, the rotation shaft 50 and the piston 32 may be vibrated by centrifugal force. That is, during the rotational movement of the rotating shaft 50, unbalanced forces may be generated at the rotating 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 in an elliptical shape eccentric in a specific direction.

The balancer 60 may be coupled to the rotation shaft 50, or a balancing part 53 may be formed at the rotation shaft 50 itself to offset an unbalanced force Fun generated during the movement of the rotation shaft 50 and the piston 32.

In the graph shown in fig. 12, the balance force Fbw for canceling the unbalanced force is a circular shape 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 part 51.

Therefore, the particles of the balancer 60 can be moved toward the center axis of the support 51.

This can further reduce the distance from the center axis of the support 51 to the mass point of the balancer 60.

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

In the graph shown in fig. 12, the magnitude of the final unbalanced force fun+fbw is not greatly deviated when compared with the conventional balancer.

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 balancing force Fbw for counteracting the unbalanced force.

At this time, the final unbalanced force fun+fbw cannot be 0, so that it is designed in a direction 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.

Thus, the absolute value of funx+fbwx can be increased, while the absolute value of funy+fbwy is decreased. That is, the variation in the magnitude of the final unbalanced force fun+fbw can be further reduced.

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

Although the present invention has been described above with reference to the preferred embodiments, the present invention is not limited to the configurations of the plurality of embodiments described above.

In addition, various modifications and changes may be made by those skilled in the art without departing from the spirit and scope of the invention as set forth in the appended claims.

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

Claims

1. A reciprocating compressor, comprising:

a piston;

a rotation shaft extending in one direction and coupled to the piston so as to be rotatable with respect to the piston;

A balancer connected to the rotation shaft in a penetrating manner and rotated together with the rotation shaft; and

a housing in which the piston, the rotary shaft, and the balancer are accommodated,

the rotating shaft includes:

a support portion extending in the one direction; and

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

the balancer includes:

a coupling portion extending radially outward of the eccentric portion from a coupling hole in contact with an outer peripheral surface of the eccentric portion and expanding; and

and an eccentric mass portion coupled to one side of the coupling portion, extending toward a radial inner side of the supporting portion, and one surface of the eccentric mass portion 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 peripheral 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 rotation shaft is spaced apart from an inner peripheral surface of the housing by a first interval in the height direction of the rotation shaft,

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

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

6. The reciprocating compressor of claim 5, wherein,

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

7. A reciprocating compressor, comprising:

a piston;

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

The rotating shaft includes:

a support portion extending in the one direction; and

the balancer includes:

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

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

8. The reciprocating compressor of claim 7, wherein,

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

9. The reciprocating compressor of claim 8, wherein,

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

10. The reciprocating compressor of claim 7, wherein,

In the one surface of the eccentric mass portion, a portion located radially outward of the eccentric portion is formed as a plane with respect to a bending line.

11. The reciprocating compressor of claim 7, wherein,

12. The reciprocating compressor of claim 11, wherein,

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

13. A reciprocating compressor, comprising:

a piston formed in a cylindrical shape;

A housing in which the piston, the rotary shaft, and the balancer are accommodated, a projection being formed at a portion of the housing,

the rotating shaft includes:

a support portion extending in the one direction; and

the balancer includes:

the protruding portion and the eccentric mass portion overlap in a height direction of the rotating shaft, the protruding portion protruding toward a direction opposite to the eccentric mass portion, the protruding portion being formed in a shape corresponding to the eccentric mass portion.

14. The reciprocating compressor of claim 13, wherein,

the rotary shaft includes a balance portion disposed between the support portion and the eccentric portion and formed to expand radially outward of the support portion from the one end 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 being coupled to the piston, and the other end thereof being coupled to the eccentric portion so as to be rotatable with respect to the eccentric portion.