WO2021167265A1 - Clapet de non-retour et compresseur à plateau oscillant le comprenant - Google Patents

Clapet de non-retour et compresseur à plateau oscillant le comprenant Download PDF

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Publication number
WO2021167265A1
WO2021167265A1 PCT/KR2021/001276 KR2021001276W WO2021167265A1 WO 2021167265 A1 WO2021167265 A1 WO 2021167265A1 KR 2021001276 W KR2021001276 W KR 2021001276W WO 2021167265 A1 WO2021167265 A1 WO 2021167265A1
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WO
WIPO (PCT)
Prior art keywords
opening
refrigerant
check valve
pulsation
flow
Prior art date
Application number
PCT/KR2021/001276
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English (en)
Korean (ko)
Inventor
남궁규
이주영
공성규
김량수
김상호
손은기
안혜림
최형인
Original Assignee
한온시스템 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 한온시스템 주식회사 filed Critical 한온시스템 주식회사
Priority to CN202180015250.0A priority Critical patent/CN115135878A/zh
Publication of WO2021167265A1 publication Critical patent/WO2021167265A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0209—Check valves or pivoted valves

Definitions

  • the present invention relates to a check valve and a swash plate compressor including the same, and more particularly, to a check valve for reducing pulsation by delaying the flow of a refrigerant, and to a swash plate compressor including the same.
  • a compressor that compresses a refrigerant in a vehicle cooling system has been developed in various forms.
  • a configuration for compressing the refrigerant includes a reciprocating type that performs compression while reciprocating, and a rotary type that performs compression while rotating. There is a rotation type.
  • the reciprocating compressor includes a crank type in which the driving force of a driving source is transmitted to a plurality of pistons using a crank, a swash plate type in which a swash plate is installed and a wobble plate type using a wobble plate, and the rotary compressor has a rotating There is a vane rotary type using a rotary shaft and a vane, and a scroll type using an orbiting scroll and a fixed scroll.
  • the swash plate compressor there are a fixed capacity type in which the installation angle of the swash plate is fixed, and a variable capacity type in which the discharge capacity can be changed by changing the inclination angle of the swash plate.
  • FIG 1 one form of a conventional check valve (1) is disclosed.
  • a hook part (2) is provided on one side of the valve body (3), and an inlet (9) through which the refrigerant flows is provided on the central side of the hook part (2) from one side.
  • the other side of the valve body (3) is provided with an outlet (4) through which the refrigerant flowing into the inlet (9) is discharged.
  • FIG. 2 a state in which the check valve 1 disclosed in FIG. 1 is coupled to the stepped part 6a of the suction port 7 formed on the rear housing 6 of the swash plate compressor by a hook part 2 is disclosed.
  • the check valve 1 functions as a suction valve.
  • the piston reciprocates according to the movement of the swash plate inside the cylinder bore, and the refrigerant flows into the suction chamber of the rear housing 6 according to the internal pressure of the cylinder bore in order to introduce and compress the refrigerant.
  • the check valve 1 is disposed on the suction port 7 to control the flow of the refrigerant.
  • the refrigerant flowing in from the suction port 7 flows into the inlet 9 , and flows into the suction chamber 8 through the outlet 4 inside the valve body 3 .
  • the structure of the conventional check valve 1 does not significantly decrease the flow rate of the refrigerant therein. Therefore, the delay of the refrigerant flow does not occur smoothly inside the check valve 1 , and the refrigerant flowing in from the inlet 9 is directly discharged to the outlet 4 , and the pulsation reduction effect does not occur. This is one of the causes of noise and vibration of the compressor.
  • the present invention has been devised to solve the problems of the related art as described above, and an object of the present invention is to provide a check valve for reducing pulsation by delaying the flow of a refrigerant and a swash plate compressor including the same.
  • the present invention for achieving the above objects relates to a check valve, in which a first opening through which refrigerant flows is formed in a central portion of one side, and a hook portion is formed around one side to be fastened to a fastening groove formed in a suction port of the rear housing. and a valve body having a second opening at the other side through which the refrigerant is discharged; and a pulsation reducing means disposed inside the other end of the valve body so that when the refrigerant flows in from the first opening and is discharged through the second opening, the refrigerant flow is delayed to reduce the pulsation of the refrigerant. have.
  • the pulsation reducing means is directed toward the first opening from the inside of the other end of the valve body so that the refrigerant flowing in from the first opening collides and the flow is delayed to reduce the pulsation of the refrigerant. It may include; a protrusion block disposed to protrude.
  • a flat portion may be formed at the upper end of the protruding block so that the refrigerant flowing in from the first opening collides, the flow is delayed, and is discharged in the direction of the second opening.
  • the pulsation reducing means further includes a first depression formed between the second opening and the protrusion block inside the other end of the valve body, and the inside of the first depression is , the incoming refrigerant and the outgoing refrigerant collide with each other to reduce pulsation.
  • the first recessed portion may have a curved shape connecting the end of the protruding block and the end of the second opening.
  • an auxiliary flow hole through which the refrigerant flowing in from the first opening is additionally discharged is formed at the upper end of the protruding block to compensate for the flow obstruction of the refrigerant generated as the protruding block is formed.
  • a plurality of auxiliary flow holes may be formed at the upper end of the protruding block.
  • the pulsation reducing means is disposed adjacent to the second opening inside the other end of the valve body so as to reduce the pulsation by interfering with the flow of the refrigerant discharged to the second opening, and a barrier protrusion protruding in the direction of the first opening.
  • the barrier protrusion is disposed between the width gap D1 of the second opening, it is possible to prevent the flow of the refrigerant discharged to the second opening to reduce the pulsation.
  • the barrier protrusion may have a cylindrical shape.
  • a plurality of the second openings are formed on the other side of the valve body, and the pulsation reducing means disperses the flow of refrigerant flowing from the first opening to the second opening to pulsate.
  • the guide projection protruding in the direction of the first opening may include.
  • a plurality of the guide projections are disposed inside the other end of the valve body, and a pair of guide projections disposed on both sides of one of the plurality of second openings each face the second opening.
  • a straight part in the direction; may be formed, and guide the flow of the refrigerant in the direction of the second opening from the central side of the valve body.
  • the interval D2 of the pair of straight portions may be disposed within the width interval D1 of the second opening.
  • the pulsation reducing means further includes a second depression formed between the second opening and the guide protrusion inside the other end of the valve body, and the inside of the second depression is , the incoming refrigerant and the outgoing refrigerant collide with each other to reduce pulsation.
  • the pulsation reducing means is connected to the lower end of the second opening inside the other end of the valve body so that the refrigerant flowing in from the first opening collides and the flow is delayed to reduce the pulsation. and a base block disposed to protrude in the direction of the first opening.
  • a rounding part is formed around the outer periphery of the upper end of the base block, and after the refrigerant flowing in from the first opening collides with the upper end of the base block, the second opening along the rounding part The flow may flow.
  • the base block has an extension protrusion extending in the direction of the second opening from the center side of the base block; the extension protrusion is formed with the second opening part from the center side of the base block It is possible to guide the flow of refrigerant in the direction.
  • the width interval D4 of the extension protrusion may be disposed between the width interval D1 of the second opening.
  • the swash plate compressor of the present invention includes a cylinder block having a cylinder bore; a front housing coupled to the front of the cylinder block and forming a crankcase; a rear housing coupled to the rear of the cylinder block and forming a suction chamber and a discharge chamber; and the check valve of claim 1 disposed at the suction port formed in the suction chamber.
  • the piston reciprocates inside the cylinder bore according to the movement of the swash plate, and at this time, a pulsation is inevitably generated in the refrigerant flow.
  • 1 is a view showing a conventional check valve.
  • Figure 2 is a side cross-sectional view showing a state in which the conventional check valve disclosed in Figure 1 is mounted on the rear housing of the swash plate compressor.
  • Figure 3 is a side cross-sectional view showing the structure of the present invention swash plate compressor.
  • Figure 4 is a view showing a first embodiment of the present invention check valve.
  • FIG. 5 is a view showing a state in which the check valve disclosed in FIG. 4 is disposed in the discharge chamber of the rear housing.
  • Figure 6 is a view comparing the degree of pulsation between the conventional check valve and the check valve of the present invention.
  • Figure 7 is a side cross-sectional view showing a second embodiment of the present invention check valve.
  • Figure 8 is a plan view of the check valve disclosed in Figure 7;
  • FIG. 9 is a side cross-sectional view showing another form of the second embodiment of the present invention check valve.
  • Figure 10 is a side cross-sectional view showing a third embodiment of the check valve of the present invention.
  • FIG. 11 is a plan view of the check valve disclosed in FIG.
  • FIG. 12 is a side cross-sectional view showing a fourth embodiment of the check valve of the present invention.
  • FIG. 13 is a plan view of the check valve disclosed in FIG. 12 .
  • Figure 14 is a side cross-sectional view showing a fifth embodiment of the present invention check valve.
  • Figure 15 is a plan view of the check valve disclosed in Figure 14.
  • a basic form of a swash plate compressor to which the present invention is applied will be described with reference to FIG. 3 .
  • the present invention is not necessarily limited to this structure, and the description of the swash plate compressor is effective only within the limits of understanding the present invention.
  • the swash plate compressor 10 is provided with a cylinder block 20 that forms a part of the exterior and the skeleton. At this time, a center bore 21 is formed through the center of the cylinder block 20 , and a shaft 94 is rotatably installed in the center bore 21 .
  • the cylinder block 20, including the front housing 30 and the rear housing 40 may be referred to as a casing (60).
  • a plurality of cylinder bores 22 are formed to pass through the cylinder block 20 so as to radially surround the center bore 21 , and a piston 70 is installed in the cylinder bore 22 to be capable of linear reciprocating motion.
  • the piston 70 is formed in a cylindrical shape
  • the cylinder bore 22 is a cylindrical space corresponding thereto, and the refrigerant in the cylinder bore 22 is compressed by the reciprocating motion of the piston 70 .
  • the cylinder bore 22 and the piston 70 form a compression chamber.
  • the front housing 30 is coupled to the front of the cylinder block 20 .
  • the front housing 30 has a face opposite to the cylinder block 20 indented to form a crank chamber 31 therein together with the cylinder block 20 .
  • a pulley 32 connected to an external power source (not shown) such as an engine is rotatably installed in front of the front housing 30 , and the shaft 94 rotates in association with the rotation of the pulley 32 .
  • a rear housing 40 is coupled to the rear of the cylinder block 20 .
  • the discharge chamber 41 is formed in the rear housing 40 along a position adjacent to the outer peripheral side edge of the rear housing 40 to selectively communicate with the cylinder bore 22 .
  • the suction port 45 is formed on one side of the rear housing 40 , and is connected to the suction chamber 42 disposed in the central portion of the rear housing 40 .
  • the present invention is not necessarily limited thereto, and other positions are possible depending on the type of compressor.
  • valve plate 50 is interposed between the cylinder block 20 and the rear housing 40 , and the discharge chamber 41 communicates with the cylinder bore 22 through a discharge port formed in the valve plate 50 .
  • a rotor 93 is disposed on the outer peripheral surface of the shaft 94 , and the rotor 93 is interlocked with the swash plate 91 by a link 95 , and a shoe 62 provided along the edge of the swash plate 91 . is connected to each piston 70 by the swash plate 91 and the piston 70 is linearly reciprocated within the cylinder bore 22 by the rotation of the swash plate 91 .
  • the angle of the swash plate 91 with respect to the shaft 94 is variable so that the refrigerant discharge amount of the compressor 10 can be adjusted.
  • the discharge chamber 41 and the crank chamber 31 are communicated.
  • the opening degree of the flow path is controlled by a pressure control valve (not shown).
  • the conventional swash plate compressor having the above configuration has a so-called radially symmetrical structure in which a plurality of cylinder bores 22 formed in the cylinder block 20 are radially spaced apart from each other with respect to the shaft 94 .
  • the check valve 100 is disposed on the suction passage 43 connecting the outside and the suction chamber 42 .
  • the check valve 100 allows the refrigerant to flow into the suction chamber 42 from the outside by the pressure formed inside the piston 70 and the cylinder bore 22 according to the movement of the swash plate 61 .
  • a relatively uniform pressure is maintained, thereby reducing noise and vibration during operation of the compressor.
  • FIG. 4 is a view showing a first embodiment of the check valve 100 according to the present invention
  • FIG. 5 is a view showing a state in which the check valve 100 disclosed in FIG. 4 is disposed in the discharge chamber of the rear housing 40
  • 6 is a view comparing the degree of pulsation between the conventional check valve 100 and the check valve 100 of the present invention.
  • the first embodiment of the check valve 100 according to the present invention has a first opening 120, a hook part 112, a second opening 130, a valve body 110, and pulsation reduction. means 200 may be included.
  • the valve body 110 forms the body of the check valve 100, and may be implemented in an overall cylindrical shape.
  • the first opening 120 may be disposed in the central portion of one side of the valve body 110 and may be a portion through which the refrigerant flows.
  • the second opening 130 may be disposed along the periphery of the other side of the valve body 110 , and may be a portion through which the refrigerant introduced from the first opening 120 is discharged.
  • the hook part 112 may be disposed along the circumference of one side of the valve body 110 , and may be coupled to the coupling groove 45a formed in the suction port 45 of the rear housing 40 .
  • the pulsation reducing means 200 delays the flow of the refrigerant to reduce the pulsation of the refrigerant when the refrigerant is introduced from the first opening 120 and discharged to the second opening 130, the valve body ( 110) may be disposed inside the other end.
  • the pulsation reducing means 200 is the other of the valve body 110 so that the refrigerant flowing in from the first opening 120 collides and the flow is delayed to reduce the pulsation of the refrigerant. It may include a protrusion block 210 disposed to protrude in the direction of the first opening 120 from the inside of the end.
  • a flat portion 213 for allowing the refrigerant flowing in from the first opening 120 to collide and flow is delayed and to be discharged in the direction of the second opening 130 is formed.
  • the protruding block 210 is disposed, and the refrigerant flowing in through the first opening 120 collides with the upper portion of the protruding block 210 indicated by the X region. It is distributed along the outer circumference of the protrusion block 210 .
  • the refrigerant collides with the protruding block 210 and causes a delay in the flow in the process of detouring in the outer circumferential direction. That is, the flow rate of the refrigerant is lowered, and as the time remaining inside the check valve 100 increases, the pulsation of the refrigerant is reduced.
  • the pulsation reducing means 200 is a first depression formed between the second opening 130 and the protruding block 210 inside the other end of the valve body 110 . It may be configured to further include a part 211 .
  • the flow rate of the refrigerant is reduced through collision inside the check valve 100 through the configuration of the protrusion block 210 and the first depression 211 in which the flat portion 213 is formed. to achieve the effect of reducing pulsation.
  • the first recessed portion 211 may have a curved shape connecting the end of the protruding block 210 and the end of the second opening 130 . This is by connecting the end of the protruding block 210 and the end of the second opening 130 in a curved shape, so that the refrigerant with a reduced flow rate by offsetting the first recessed portion 211 smoothly flows through the second opening 130 . in order to be released into
  • the flow of the coolant is delayed, and the flow rate of the coolant is reduced, which means that the coolant inside the check valve 100 is The remaining time is increased, and ultimately, the pulsation of the refrigerant is reduced.
  • the pulsating pressure was measured to be 0.0248 bar, and in the case of the check valve (B) of the present invention, the pulsating pressure was measured to be 0.0214 bar. About 13% of the pulsation pressure was reduced.
  • the check valve (B) of the present invention reduces the flow rate of the refrigerant compared to the conventional check valve (A), thereby deriving the effect of reducing the pulsation of the refrigerant as a whole.
  • Figure 7 is a side cross-sectional view showing a second embodiment of the check valve 100 of the present invention
  • Figure 8 is a plan view of the check valve 100 disclosed in Figure 7
  • Figure 9 is the check valve 100 of the present invention. It is a side cross-sectional view showing another form of the second embodiment.
  • the structure of the second embodiment of the check valve 100 according to the present invention can be confirmed.
  • the first opening 120 , the second opening 130 , the hook portion 112 , the valve body 110 , the protruding block 210 , and the first depression In addition to the part 211 , it may further include an auxiliary flow hole 215 .
  • first opening 120 the second opening 130 , the hook part 112 , the valve body 110 , the protruding block 210 , and the first recessed part 211 are the same as those of the first embodiment. Therefore, the following description will be omitted.
  • the auxiliary flow hole 215 may be formed at the upper end of the protrusion block 210 .
  • the auxiliary flow hole 215 allows the refrigerant flowing in from the first opening 120 to be additionally discharged to the suction chamber 42 so as to compensate for the flow obstruction of the refrigerant generated as the protrusion block 210 is formed. may be provided for.
  • auxiliary flow hole 215 As the auxiliary flow hole 215 is formed, a portion of the refrigerant introduced from the first opening 120 is directly introduced into the suction chamber 42 through the auxiliary flow hole 215 , and the It is possible to compensate to some extent a change in the amount of refrigerant supplied due to a decrease in the flow rate in the protruding block 210 and the first recessed portion 211 .
  • auxiliary flow hole 215 shows a form in which one auxiliary flow hole 215 is formed with a relatively large diameter, and in FIG. 9 , a plurality of auxiliary flow holes 215 are formed at the upper end of the protruding block 210 with a relatively small attack.
  • the form formed in is disclosed.
  • the position, size, and number of the auxiliary flow holes 215 may be changed according to design specifications.
  • Figure 10 is a side cross-sectional view showing a third embodiment of the check valve 100 of the present invention
  • Figure 11 is a plan view of the check valve 100 disclosed in Figure 10.
  • the description of the first opening 120, the second opening 130, the hook part 112, and the valve body 110 in the third embodiment of the check valve 100 according to the present invention is the same as that of the first embodiment. The description will be omitted.
  • the pulsation reducing means 200 which is different from the first embodiment will be described.
  • the pulsation reducing means 200 may include a barrier protrusion 220 .
  • the barrier protrusion 220 is disposed adjacent to the second opening 130 inside the other end of the valve body 110 so as to reduce pulsation by obstructing the flow of the refrigerant discharged to the second opening 130 . and may be formed to protrude in the direction of the first opening 120 .
  • the barrier protrusion 220 may be implemented in a cylindrical shape, and as four second openings 130 are formed along the periphery of the other side of the valve body 110 , 4
  • the barrier protrusions 220 may be disposed adjacent to the second opening 130 , respectively.
  • the shape of the barrier protrusion 220 is not limited to a cylindrical shape.
  • the refrigerant flowing in from the first opening 120 is prevented from flowing when passing through the barrier protrusion 220 . , and enters in the direction of the second opening 130 .
  • the barrier protrusion 220 is disposed between the width gaps D1 of the second opening 130 , and prevents the flow of refrigerant discharged to the second opening 130 and reduces pulsation. function to do.
  • the barrier protrusion 220 may be formed to have a width smaller than the width D1 of the second opening 130 .
  • the barrier protrusion 220 is disposed in the center of the width gap D1 of the second opening 130 to be balanced in the left and right direction of the second opening 130 when the refrigerant is discharged to the second opening 130 . It may be desirable to induce a negative flow obstruction.
  • the refrigerant bypasses the barrier protrusion 220 and is discharged into the suction chamber 42 through the second opening 130 as shown by the arrow indicating the flow direction of the refrigerant.
  • the flow rate of the refrigerant is lowered due to the flow obstruction by the barrier protrusion 220 , and the time remaining inside the check valve 100 increases, resulting in an effect of reducing the pulsation of the refrigerant. .
  • Figure 12 is a side cross-sectional view showing a fourth embodiment of the check valve 100 according to the present invention
  • Figure 13 is a plan view of the check valve 100 disclosed in Figure 12.
  • the description of the first opening 120, the second opening 130, the hook part 112, and the valve body 110 in the fourth embodiment of the check valve 100 according to the present invention is the same as that of the first embodiment. The description will be omitted.
  • the pulsation reducing means 200 which is different from the first embodiment will be described.
  • the pulsation reducing means 200 distributes the flow of the refrigerant flowing from the first opening 120 to the second opening 130 to reduce pulsation.
  • a guide protrusion 230 protruding in the direction of the first opening 120 .
  • a plurality of guide protrusions 230 may be disposed inside the other end of the valve body 110 .
  • a pair of guide protrusions 230 disposed on both sides of one of the plurality of second openings 130 may each have a straight portion 231 formed in a direction facing the second opening 130 .
  • the pair of straight portions 231 guide the flow of the refrigerant from the central side of the valve body 110 in the direction of the second opening 130 .
  • the interval D2 between the pair of straight portions 231 may be disposed within the width interval D1 of the second opening 130 . This is to allow the refrigerant guided by the pair of straight parts 231 to be smoothly discharged to the second opening 130 .
  • the plurality of guide protrusions 230 are disposed between the plurality of second openings 130 and collide with the refrigerant flowing in from the first opening 120 to reduce the flow rate of the refrigerant and reduce the pulsation of the refrigerant.
  • the refrigerant discharge flow to the second opening 130 is compensated, for example, such as the auxiliary flow hole 215 in the first embodiment, so that the refrigerant supply can be compensated for by the amount of the refrigerant flow hindered, the straight part ( 231) was formed.
  • the refrigerant collides with the guide protrusion 230 and is guided along the straight line portion 231 while bypassing the guide protrusion 230 as shown in the arrow indicating the flow direction of the refrigerant disclosed in FIG. It is discharged to the suction chamber 42 through.
  • the flow rate of the refrigerant is lowered due to the flow obstruction by the guide protrusion 230 , and the time remaining inside the check valve 100 increases, resulting in an effect of reducing the pulsation of the refrigerant. .
  • the refrigerant flow is guided to the second opening 130 to compensate for the refrigerant supply.
  • the pulsation reducing means 200 further includes a second recessed part 233 formed between the second opening 130 and the guide protrusion 230 inside the other end of the valve body 110 . can do. Similar to the function of the first recessed part 211 of the first embodiment, in the second recessed part 233, the incoming and outgoing coolant collide with each other to reduce pulsation.
  • the flow rate of the refrigerant is reduced through collision within the check valve 100 through the configuration of the guide protrusion 230, the straight part 231 and the second recessed part 233. It is to achieve the effect of reducing the pulsation, guiding the flow of the refrigerant and compensating the flow of the refrigerant according to the reduction in the flow rate of the refrigerant.
  • Figure 14 is a side cross-sectional view showing a fifth embodiment of the check valve 100 of the present invention
  • Figure 15 is a plan view of the check valve 100 disclosed in Figure 14.
  • the description of the first opening 120, the second opening 130, the hook part 112, and the valve body 110 in the fifth embodiment of the check valve 100 according to the present invention is the same as that of the first embodiment. The description will be omitted.
  • the pulsation reducing means 200 which is different from the first embodiment will be described.
  • the pulsation reducing means 200 may be configured to include a base block 240 and an extension protrusion 245 .
  • the base block 240 has the lower end of the second opening 130 inside the other end of the valve body 110 so that the refrigerant flowing in from the first opening 120 collides and the flow is delayed to reduce pulsation. may be connected to and protrude in the direction of the first opening 120 .
  • a rounding part 241 is formed around the outer periphery of the upper end of the base block 240, and after the refrigerant flowing in from the first opening 120 collides with the upper end of the base block 240, the rounding part ( 241), the flow may be configured to flow in the direction of the second opening 130 .
  • the upper central portion of the base block 240 is flat, so that the refrigerant flowing in from the first opening 120 collides and the flow is delayed.
  • the base block 240 is disposed, and the refrigerant flowing in through the first opening 120 collides at the upper center of the base block 240 to collide with the base block ( 240) will be distributed along the outer perimeter.
  • the flow is gently induced along the rounding part 241 , it enters in the direction of the second opening 130 , and is discharged into the suction chamber 42 .
  • the refrigerant collides with the base block 240 and causes a delay in the flow in the process of detouring in the outer circumferential direction. That is, the flow rate of the refrigerant is lowered, and as the time remaining inside the check valve 100 increases, the pulsation of the refrigerant is reduced.
  • the extension protrusion 245 may be formed by extending in the direction of the second opening 130 from the central side of the base block 240 .
  • the extension protrusion 245 may perform a function of guiding the flow of the refrigerant in the direction of the second opening 130 from the central side of the base block 240 .
  • the width gap D4 of the extension protrusion 245 may be disposed between the width gap D1 of the second opening 130 . Accordingly, the refrigerant guided in the direction of the second opening 130 along the rounding portion 241 of the base block 240 is guided to the second opening 130 by the extension protrusion 245 .
  • the pulsation is reduced by reducing the flow rate of the refrigerant through collision inside the check valve 100 through the configuration of the base block 240 and the extension protrusion 245 , and the flow of the refrigerant and to achieve the effect of compensating for the refrigerant flow according to the reduction of the refrigerant flow rate.
  • the present invention relates to a check valve and a swash plate compressor, and has industrial applicability.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Check Valves (AREA)
  • Compressor (AREA)

Abstract

La présente invention concerne un clapet de non-retour et un compresseur à plateau oscillant le comprenant, et peut comprendre : un corps de vanne ayant, au centre d'une partie latérale de celui-ci, une première ouverture à travers laquelle s'écoule un fluide frigorigène, ayant, sur la circonférence de la partie latérale de celle-ci, une partie crochet liée à une rainure d'insertion formée dans une chambre d'aspiration d'un boîtier arrière, et ayant, sur l'autre partie latérale de celle-ci, une seconde ouverture à travers laquelle le fluide frigorigène est évacué ; et un moyen de réduction de pulsation disposé à l'intérieur de l'autre partie d'extrémité du corps de vanne de façon à retarder l'écoulement du fluide frigorigène et à réduire ainsi la pulsation, lorsque le fluide frigorigène s'écoule depuis la première ouverture à évacuer à travers la seconde ouverture.
PCT/KR2021/001276 2020-02-19 2021-02-01 Clapet de non-retour et compresseur à plateau oscillant le comprenant WO2021167265A1 (fr)

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CN202180015250.0A CN115135878A (zh) 2020-02-19 2021-02-01 止回阀及包括该止回阀的斜盘式压缩机

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KR1020200020135A KR20210105536A (ko) 2020-02-19 2020-02-19 체크밸브 및 이를 포함하는 사판식 압축기
KR10-2020-0020135 2020-02-19

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05288186A (ja) * 1992-04-06 1993-11-02 Zexel Corp 圧縮機の吸入弁
US20080107544A1 (en) * 2006-11-03 2008-05-08 Sokichi Hibino Suction throttle valve of a compressor
KR101194431B1 (ko) * 2007-10-19 2012-10-24 산덴 가부시키가이샤 가변 용량 압축기
KR20140104300A (ko) * 2013-02-20 2014-08-28 한라비스테온공조 주식회사 흡입체크밸브
KR20170043235A (ko) * 2015-10-13 2017-04-21 한온시스템 주식회사 압축기의 흡입 맥동 저감장치

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CN1250873C (zh) * 2001-12-27 2006-04-12 株式会社丰田自动织机 压缩机
KR101165947B1 (ko) * 2006-05-01 2012-07-18 한라공조주식회사 가변용량형 사판식 압축기
KR101452568B1 (ko) * 2012-02-13 2014-10-21 한라비스테온공조 주식회사 가변용량형 사판식 압축기
KR101852448B1 (ko) * 2012-10-26 2018-04-27 한온시스템 주식회사 사판식 압축기
KR101766508B1 (ko) * 2013-01-23 2017-08-08 한온시스템 주식회사 사판식 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05288186A (ja) * 1992-04-06 1993-11-02 Zexel Corp 圧縮機の吸入弁
US20080107544A1 (en) * 2006-11-03 2008-05-08 Sokichi Hibino Suction throttle valve of a compressor
KR101194431B1 (ko) * 2007-10-19 2012-10-24 산덴 가부시키가이샤 가변 용량 압축기
KR20140104300A (ko) * 2013-02-20 2014-08-28 한라비스테온공조 주식회사 흡입체크밸브
KR20170043235A (ko) * 2015-10-13 2017-04-21 한온시스템 주식회사 압축기의 흡입 맥동 저감장치

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KR20210105536A (ko) 2021-08-27

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