KR101576459B1 - Scoroll compressor and refrigsrator having the same - Google Patents

Scoroll compressor and refrigsrator having the same Download PDF

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Publication number
KR101576459B1
KR101576459B1 KR1020090015847A KR20090015847A KR101576459B1 KR 101576459 B1 KR101576459 B1 KR 101576459B1 KR 1020090015847 A KR1020090015847 A KR 1020090015847A KR 20090015847 A KR20090015847 A KR 20090015847A KR 101576459 B1 KR101576459 B1 KR 101576459B1
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KR
South Korea
Prior art keywords
pressure
compression chamber
refrigerant
compressor
chamber
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Application number
KR1020090015847A
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Korean (ko)
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KR20100096791A (en
Inventor
김철환
정철수
원인호
이병철
조양희
최세헌
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엘지전자 주식회사
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253Details concerning the base
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005Axial sealings for working fluid
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04Heating; Cooling; Heat insulation
    • F04C29/042Heating; Cooling; Heat insulation by injecting a fluid

Abstract

The present invention relates to a scroll compressor and a refrigeration apparatus using the same. According to the present invention, by appropriately designing an interval between the injection passage for guiding the refrigerant passed through the condenser back to the intermediate compression chamber and the back pressure passage for guiding the refrigerant to the back pressure chamber in the intermediate compression chamber, It is possible to prevent the refrigerant injected into the intermediate compression chamber from suddenly flowing out from the intermediate compression chamber to the back pressure chamber so as to properly maintain the pressure of the back pressure chamber and to increase the amount of refrigerant in the compression chamber, Performance can be improved.
Scroll compressor, backpressure, injection, phase difference

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a scroll compressor,

The present invention relates to a scroll compressor for bypassing a refrigerant from an intermediate compression chamber to a back pressure chamber while bypassing a refrigerant from the middle of a refrigeration cycle to an intermediate compression chamber and a refrigeration apparatus using the same.

Generally, a scroll compressor is a compressor that compresses a refrigerant gas by changing a volume of a compression chamber formed by a pair of opposing scrolls. The scroll compressor is more efficient than a reciprocating compressor or a rotary compressor, has low vibration and noise, can be made compact and lightweight, and is widely used particularly in air conditioners.

The scroll compressor may be divided into a low-pressure type and a high-pressure type according to the type of refrigerant supplied to the compression chamber. That is, in the low-pressure scroll compressor, the refrigerant is indirectly sucked into the compression chamber through the inner space of the casing, and the inner space of the casing is divided into the suction space and the discharge space. On the other hand, in the high-pressure scroll compressor, the refrigerant is directly supplied to the compression chamber without passing through the inner space of the casing, and is discharged to the inner space of the casing, so that the entire inner space of the casing is formed as the discharge space.

The scroll compressor may be divided into a tip chamber type and a back pressure type by a sealing method of a compression chamber. That is, in the tip chamber type, a tip chamber is provided at the tip of the lap of each scroll, so that the tip chamber of the compressor rises while the compressor is in operation, and is brought into close contact with the end plate of the opposite scroll. On the other hand, in the back pressure system, a back pressure chamber is formed on the back surface of one scroll, and oil or refrigerant of intermediate pressure is introduced into the back pressure chamber so that the scroll is pressed against the pressure of the back pressure chamber, Typically, the tip chamber method is applied to a low pressure scroll compressor while the back pressure method is applied to a high pressure scroll compressor.

The scroll compressor may be divided into a fixed capacity type and a variable capacity type by a circulation system of the refrigerant. That is, the fixed capacity type is a system in which the entire refrigerant discharged from the compressor is circulated through a refrigeration cycle including a condenser, an expander and an evaporator and is sucked to the suction side of the compressor. On the other hand, a part of the refrigerant discharged from the variable- The refrigerant is bypassed to the intermediate compression chamber of the compressor and the remaining refrigerant is sucked to the suction side of the compressor through the refrigerant cycle in turn. In general, the variable displacement scroll compressor is provided with an injection pipe connected to the outlet of the condenser, the injection pipe communicating with the intermediate compression chamber of the compressor, and the circulation direction of the refrigerant in the middle of the injection pipe or at the branch point of the injection pipe A valve for controlling the flow rate of the refrigerant is provided.

However, in the conventional scroll compressor described above, when the back pressure passage communicating with the back pressure chamber from the intermediate compression chamber and the injection passage communicating with the intermediate compression chamber of the compressor from the outlet of the condenser are provided together, the gap between the back pressure passage and the injection passage The effect on the performance of the compressor has been neglected. That is, in the refrigerating cycle, the refrigerant having the intermediate pressure flows into the intermediate compression chamber of the compressor through the injection passage. Therefore, when the back pressure passage and the injection passage are disposed too close to the advancing direction of the compression chamber, The refrigerant is rapidly discharged to the back pressure chamber through the back pressure passage so that the pressure of the back pressure chamber is excessively increased. As a result, the pressure of the back pressure chamber can not be properly maintained, The friction loss is generated as well as the wear of the lap and the reliability of the compressor is deteriorated.

The present invention solves the problems of the conventional scroll compressor as described above, and prevents the refrigerant injected from the refrigeration cycle to the intermediate compression chamber through the injection passage from suddenly flowing out from the intermediate compression chamber to the back pressure chamber, The present invention provides a scroll compressor and a refrigeration apparatus having the scroll compressor.

In order to accomplish the object of the present invention, there is provided a compressor comprising: a pair of compression chambers formed by two scrolls engaged with each other and moving continuously while moving relative to each other; and a part of the refrigerant compressed in the compression chamber, Wherein a portion of the refrigerant discharged from the compression chamber in the refrigeration cycle is injected into the intermediate compression chamber in the refrigeration cycle, the scroll compressor comprising: And an angle at which the refrigerant in the compression chamber starts to be depressurized by the back pressure chamber is at least 30 DEG or more.

Further, the fixed scroll; And an orbiting scroll which forms two pairs of compression chambers continuously moving while pivotally moving in association with the fixed scroll, wherein a back pressure chamber is formed in the back surface of the orbiting scroll so as to receive refrigerant bypassed from the compression chamber, At least one back pressure passage communicating between the compression chamber and the back pressure chamber is formed in the fixed scroll and a part of the refrigerant discharged from the compression chamber through the refrigeration cycle is injected into the intermediate compression chamber at one side of the back pressure passage An injection passage is formed and the backpressure passage is formed relatively closer to the suction side of the compression chamber than the injection passage.

In addition, A condenser connected to a discharge side of the compressor; An expander connected to the condenser; And an evaporator connected to the inflator and connected to the suction side of the compressor, wherein the compressor has an injection passage communicating with the intermediate compression chamber in the middle of the refrigeration cycle, There is provided a refrigeration apparatus comprising a compressor.

The scroll compressor and the refrigerating machine having the scroll compressor according to the present invention prevent the refrigerant injected into the intermediate compression chamber from the refrigeration cycle through the injection passage from suddenly flowing out from the intermediate compression chamber to the back pressure chamber, It is possible to increase the amount of refrigerant in the compression chamber and improve the performance of the scroll compressor and the refrigerating machine equipped with the scroll compressor.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a refrigeration apparatus having the scroll compressor according to the present invention will be described in detail with reference to an embodiment shown in the accompanying drawings.

1, a high-pressure scroll compressor according to the present invention includes a casing 10 having a closed internal space, a main frame 20 fixed to both upper and lower internal spaces of the casing 10, A driving motor 30 mounted between the main frame 20 and a subframe (not shown) to generate a rotational force; a driving motor 30 fixedly mounted on the upper surface of the main frame 20, A fixed scroll 40 directly coupled to the fixed scroll 40 and an orbiting scroll 50 pivotally mounted on the upper surface of the main frame 20 to form a compression chamber P, And an Oldham's ring (not shown) installed between the orbiting scroll 50 and the main frame 20 to rotate the orbiting scroll 50 while preventing the orbiting scroll 50 from rotating.

The closed space of the casing 10 is partitioned into an upper space S1 and a lower space S2 by the main frame 20 and the fixed scroll 40 so that the upper space S1 and the lower space S2 S2 are kept at a high pressure, and the bottom surface of the lower space S2 of the casing 10 is filled with oil. The gas suction pipe SP is coupled to the upper space S1 of the casing 10 and the gas discharge pipe DP is coupled to the lower space S2 of the casing 10. [

The main frame 20 is formed with a shaft hole 21 at the center thereof and an oil pocket 22 is formed at an upper end of the shaft hole 21 so as to collect oil picked up via a drive shaft 32 do. A back pressure groove (23) is formed in the upper surface of the main frame (20) to form a back pressure chamber (S3) in which a part of the refrigerant sucked and a part of the oil absorbed therein is mixed with the intermediate pressure. A sealing groove (not shown) is formed in an annular shape to seal the oil contained in the oil pocket 22 to maintain a high pressure. The back pressure chamber S3 is formed by combining the back pressure groove 23 of the main frame 20 with the longitudinal plate portion 41 of the fixed scroll 40 to be described later and the longitudinal plate portion 51 of the orbiting scroll 50 to be described later, .

The driving motor 30 includes a stator (not shown) having a coil 31 fixed to the inside of the casing 10 to receive power from the outside, and a stator A rotor (not shown) that rotates while interacting with the stator, and a drive shaft 32 coupled to the rotor by heat shrinkage and transmitting the rotational force of the drive motor 30 to the orbiting scroll 50. The drive shaft 32 is formed with an oil passage 32a in an axial direction and an oil pump (not shown) is installed at a lower end of the oil passage 32a.

The stationary scroll 40 is formed in a spiral shape with a fixed lap 42 forming a pair of two compression chambers P on the bottom surface of the rigid plate 41. On the side surface of the rigid plate 41, A discharge port 44 for discharging the compressed refrigerant into the upper space S1 of the casing 10 is formed at the center of the upper surface of the hard plate part 41. [ The compression chamber P and the back pressure chamber S3 are provided between the lap and the rap making up the compression chamber P on the bottom surface of the hard plate 41, that is, the surface forming the thrust bearing surface together with the orbiting scroll 50. [ The back pressure passage 110 is formed.

2 to 4, the back pressure passage 110 includes a first back pressure hole 111 communicating with the back pressure chamber S3 and a second back pressure hole 112 communicating with the compression chamber P, And a third back pressure hole 113 formed at a predetermined depth in the radial direction on the outer circumferential surface of the fixed scroll 40 so that the first back pressure hole 111 and the second back pressure hole 112 are communicated with each other. The first back pressure hole 111 is formed on the outlet end of the first back pressure hole 111, that is, the surface opposed to the back pressure groove 23 so that the first back pressure hole 111 can smoothly communicate with the back pressure groove 23, A communication groove 114 that is wider than the hole 111 is formed. The communication groove 114 may be formed in a long radial shape or a circular groove wider than the first back pressure hole 111. The diameters d1, d2, and d3 of the back pressure holes 111, 112, and 113 may be substantially equal to each other to reduce the flow resistance.

The first back pressure hole 111, the second back pressure hole 112 and the third back pressure hole 113 are formed so as to form one flow passage, and the one flow passage is formed alternately with the pair of compression chambers P Respectively. That is, one of the second back pressure holes 112 is formed, and the second back pressure hole 112 is formed to be positioned at the center between the adjacent fixed laps 42, 4, the inner diameter d1 of the second back pressure hole 112 is preferably not larger than the wrap thickness t of the orbiting scroll so that the refrigerant does not leak into the outer compression chamber.

A blocking member 115 is inserted into the third back pressure hole 113 at a predetermined depth from the outer end of the third back pressure hole 113 to separate the third back pressure hole 113 from the inner space of the casing 10. The blocking member 115 may be press-fitted and sealed by a non-ferrous metal having relatively elasticity, or may be fastened to a predetermined depth by using metal bolts provided with threads as shown in Figs. 3 and 4. Here, in the case of using the metal bolt, it is preferable that the sealing washer 116 is inserted into the head of the metal bolt and sealed.

2, the orbiting scroll 50 is provided with a fixed lap 42 of the fixed scroll 40 on the upper surface of the fixed plate 51, and a swinging lap 42 constituting a pair of compression chambers P And a boss portion 53 coupled to the drive shaft 32 and receiving the power of the drive motor 30 is formed at the center of the bottom surface of the hard plate portion 51.

The fixed lap 42 and the orbiting lap 52 may be formed symmetrically with each other with the lap length being equal to each other, and the lap length may be different, that is, the orbiting wrap may be formed in an asymmetric shape It is possible.

The scroll compressor of the present invention operates as follows.

That is, when power is applied to the driving motor 30, the driving shaft 32 rotates together with the rotor to transmit the rotational force to the orbiting scroll 50, and the orbiting scroll 50, Between the stationary wrap (42) of the fixed scroll (40) and the orbiting wrap (52) of the orbiting scroll (50) while rotating by eccentric distance from the upper surface of the main frame A pair of compression chambers P continuously moving are formed. The compression chamber (P) is moved to the center by the continuous swirling motion of the orbiting scroll (50), and the volume thereof is reduced to compress the refrigerant sucked.

At the same time, the oil filled in the casing 10 is pumped by the oil pump (not shown) provided at the lower end of the drive shaft 32, While a part of the oil is scattered at the upper end of the drive shaft 32 and flows into the back pressure chamber S3 of the main frame 20 . The oil introduced into the back pressure chamber S3 supports the orbiting scroll 50 and raises the orbiting scroll 50 toward the fixed scroll 40, The compression chambers P are sealed while being in close contact with the respective hard plates 51 (41) corresponding thereto.

In this state, the orbiting scroll 50 continuously compresses the refrigerant while pivotally moving, and a part of the refrigerant to be compressed moves to the back pressure chamber S3 through the back pressure passage 110, And the pressure of the pressure chamber S3 is kept constant. In this case, only one outlet of the back pressure passage 110, that is, the second back pressure hole 112 is formed, but the second back pressure hole 112 is formed in the both compression chambers P with the orbiting wrap 52 interposed therebetween. The oil can be uniformly supplied to the respective compression chambers P through the back pressure passage 110 as they are alternately communicated with each other.

When the scroll compressor is a variable capacity type, the compression capacity of the scroll compressor is increased by re-flowing the refrigerant into the intermediate compression chamber of the compressor in the middle of the refrigeration cycle including the scroll compressor, that is, the outlet side of the condenser, .

8, in the middle of the refrigerant pipe 5 connecting the condenser 2 and the inflator 3 of the refrigeration cycle, that is, at the outlet side of the condenser 2, And the injection pipe 6 is connected to the injection passage 120 provided in the fixed scroll 40 of the scroll compressor 1 shown in Figs. A bypass valve 7 for controlling the flow of the refrigerant may be installed in the middle of the injection pipe 6 or at a point where the injection pipe 6 is branched.

2, 3 and 5, the injection passage 120 includes a first injection hole 121 formed at a predetermined depth in the radial direction on the outer peripheral surface of the fixed scroll 40, And a second injection hole (122) formed in the axial direction so as to pass through the intermediate compression chamber at almost the end of the injection hole (121).

Here, depending on the formation position of the second injection hole 122, the refrigerant injected in the middle of the refrigeration cycle leaks to the back pressure chamber S3, which may lower the performance of the compressor. The second back pressure hole 112 of the back pressure passage 110 and the second injection hole 122 of the injection path 120 are formed at a position where the injection passage 120 is formed with respect to the back pressure passage 110, Is important for enhancing the performance of the compressor.

The second injection hole 122 of the injection passage 120 is formed in such a manner that the angle at which the refrigerant starts to be injected into the intermediate compression chamber P of the compressor 1 in the refrigeration cycle, As shown in Figs. 6 and 7, it is more accurate that the refrigerant starts to be backpressed to the back pressure chamber S3, that is, closer to the discharge side of the compression chamber than the second back pressure hole 112 of the back pressure passage 110, The refrigerant injected into the intermediate compression chamber through the injection passage 120 can be effectively prevented from leaking into the back pressure passage 110. [ The larger the phase difference alpha between the second back pressure hole 112 of the back pressure passage 110 and the second injection hole 122 of the injection path 120,

The diameter of the second injection hole 122 is formed to be substantially the same as the diameter of the second back pressure hole 112 so that the injection amount of the coolant can be smoothly performed. The diameter d4 of the second injection hole 122 is not greater than the thickness t of the orbiting scroll 52 of the orbiting scroll 50 because the refrigerant injected through the injection passage 120 It is possible to prevent the refrigerant from leaking from being communicated with both of the compression chambers.

The temperature of the refrigerant injected into the intermediate compression chamber may be lower than the outlet temperature of the condenser 2 and higher than the inlet side temperature of the compression chamber 2, which may be desirable to increase the injection amount of the refrigerant. That is, after the refrigerant discharged from the scroll compressor 1 passes through the condenser 2, a portion of the refrigerant at the outlet of the condenser 2 is bypassed to the injection pipe 6, The liquid refrigerant is expanded to be converted into a mixed refrigerant (gas refrigerant + liquid refrigerant) at about 20 ° C, the mixed refrigerant is heat-exchanged with the condenser 2 and is again converted to a low-temperature gas refrigerant, A piping is formed so as to be injected into the intermediate compression chamber through the injection passage 120.

When the gap between the back pressure passage 110 and the injection passage 120 in the scroll compressor having the back pressure passage 110 and the injection passage 120 has a phase difference alpha of at least 30 degrees, 9 (a), the actual pressure of the back pressure chamber becomes substantially similar to the design pressure, so that the orbiting scroll can be stably supported. If the gap between the back pressure passage and the injection passage is 20 °, the actual pressure of the back pressure chamber becomes higher than the design pressure as shown in FIG. 9 (b), causing the orbiting scroll to rise excessively, The friction loss or wear between the scroll and the fixed scroll may occur and the performance or reliability of the compressor may be lowered.

In this way, the gap between the injection passage and the back pressure passage maintains an appropriate phase difference so that the refrigerant injected into the intermediate compression chamber through the injection passage can not move along the advancing direction of the compression chamber and leaks to the back pressure chamber through the back pressure passage . Accordingly, the refrigerant injected into the intermediate compression chamber through the injection passage in the middle of the refrigeration cycle during the high-capacity operation of the scroll compressor is combined with the refrigerant sucked into the suction side of the compression chamber to increase the amount of refrigerant, thereby improving the performance of the scroll compressor .

On the other hand, when the scroll compressor according to the present invention is applied to a refrigerating machine, the efficiency of the refrigerating machine can be improved.

8, the refrigerating machine 700 includes a scroll compressor 1, a condenser 2, an inflator 3 and an evaporator 4, and a part of the refrigerant passing through the condenser 2 Is injected into the intermediate compression chamber of the scroll compressor (1). The scroll compressor 1 is connected to the main board 710 for controlling the overall operation of the refrigerating machine 700 and the fixed scroll 1 is installed inside the scroll compressor 1, A back pressure passage for discharging the refrigerant from the intermediate compression chamber to the back pressure chamber and an injection passage for re-introducing the refrigerant to the intermediate compression chamber at the outlet of the condenser are formed. The gap between the back pressure passage and the injection passage may be formed to be at least 30 degrees as described above. In this way, it is possible to prevent the refrigerant injected into the intermediate compression chamber through the injection passage from leaking through the back pressure passage, thereby improving the performance of the refrigeration apparatus having the scroll compressor.

The scroll compressor according to the present invention can be widely used in refrigeration machines such as air conditioners.

1 is a longitudinal sectional view showing a part of a scroll compressor according to the present invention,

FIG. 2 is a perspective view showing a compressed portion of the scroll compressor according to FIG. 1,

3 is a sectional view taken along the line "I-I" in Fig. 2,

Fig. 4 is a longitudinal sectional view enlargedly showing a back pressure passage in the scroll compressor according to Fig. 3,

Fig. 5 is a longitudinal sectional view showing an enlarged view of the injection passage in the scroll compressor according to Fig. 3,

Fig. 6 is a sectional view taken along line II-II in Fig. 2,

FIG. 7 is an enlarged view for explaining the phase difference between the back pressure passage and the injection passage in FIG. 6,

FIG. 8 is a systematic view showing a refrigeration cycle provided with the scroll compressor of the present invention,

9 is a graph showing a change in the back pressure chamber pressure of the scroll compressor according to the phase difference between the back pressure passage and the injection passage in the refrigeration cycle according to FIG. 8,

FIG. 10 is a schematic view showing an embodiment of an air conditioner to which the scroll compressor according to FIG. 1 is applied. FIG.

DESCRIPTION OF REFERENCE NUMERALS

1: scroll compressor 2: condenser

3: inflator 4: evaporator

5: Refrigerant pipe 6: Injection pipe

7: Bypass valve 10: Casing

20: main frame 23: back pressure groove

40: fixed scroll 41: fixed scroll hard plate part

42: stationary lap 50: orbiting scroll

51: orbiting scroll plate portion 110: back pressure passage

111, 112, 113: Back pressure hole 120: Injection passage

121: first injection hole 122: second injection hole

Claims (8)

  1. A pair of compression chambers are formed in which a plurality of scrolls are engaged to move successively while moving relative to each other, and a part of the refrigerant compressed in the compression chamber is bypassed to a backpressure chamber provided on a scroll back surface of one of the plurality of scrolls And an injection passage is formed such that a part of the refrigerant discharged from the compression chamber into the refrigeration cycle is injected into the intermediate compression chamber in the refrigeration cycle,
    Wherein the refrigerant is formed to have a phase difference of at least 30 degrees between an angle at which the refrigerant starts to be injected into the intermediate compression chamber in the refrigeration cycle and an angle at which the refrigerant in the compression chamber starts to be backpressed into the back pressure chamber.
  2. The method according to claim 1,
    Wherein the temperature of the refrigerant injected into the intermediate compression chamber has a temperature lower than an outlet side temperature of the condenser.
  3. 3. The method of claim 2,
    Wherein the temperature of the refrigerant injected into the intermediate compression chamber is higher than the suction side temperature of the compression chamber.
  4. Fixed scroll; And
    And an orbiting scroll which forms two pairs of compression chambers continuously moving while pivotally moving with the fixed scroll,
    A back pressure chamber is formed on a back surface of the orbiting scroll so as to receive refrigerant bypassed from the compression chamber,
    Wherein at least one back pressure passage communicating between the compression chamber and the back pressure chamber is formed in the fixed scroll,
    An injection passage is formed at one side of the back pressure passage so that a part of the refrigerant discharged from the compression chamber through the refrigeration cycle is injected into the intermediate compression chamber,
    The injection passage is formed closer to the discharge side of the compression chamber than the back pressure passage,
    And the diameter of the injection passage is formed to be equal to or larger than the diameter of the back pressure passage.
  5. 5. The method of claim 4,
    Wherein the gap between the back pressure passage and the injection passage is formed to have a phase difference of 30 DEG or more.
  6. delete
  7. 5. The method of claim 4,
    Wherein the injection passage is formed so as not to be larger than the thickness of the wraps provided on both the scrolls to form the compression chambers.
  8. compressor;
    A condenser connected to a discharge side of the compressor;
    An expander connected to the condenser; And
    And an evaporator connected to the inflator and connected to the suction side of the compressor,
    Wherein the compressor comprises the scroll compressor according to any one of claims 1 to 5 and 7.
KR1020090015847A 2009-02-25 2009-02-25 Scoroll compressor and refrigsrator having the same KR101576459B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020090015847A KR101576459B1 (en) 2009-02-25 2009-02-25 Scoroll compressor and refrigsrator having the same

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
KR1020090015847A KR101576459B1 (en) 2009-02-25 2009-02-25 Scoroll compressor and refrigsrator having the same
US12/706,913 US20100212352A1 (en) 2009-02-25 2010-02-17 Compressor and refrigerating apparatus having the same
EP10154576.2A EP2243958B1 (en) 2009-02-25 2010-02-24 Compressor and refrigerating apparatus having the same

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KR20100096791A KR20100096791A (en) 2010-09-02
KR101576459B1 true KR101576459B1 (en) 2015-12-10

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KR (1) KR101576459B1 (en)

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