US20100158710A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
US20100158710A1
US20100158710A1 US12/641,908 US64190809A US2010158710A1 US 20100158710 A1 US20100158710 A1 US 20100158710A1 US 64190809 A US64190809 A US 64190809A US 2010158710 A1 US2010158710 A1 US 2010158710A1
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United States
Prior art keywords
chamber
pressure
backpressure
receiving surface
valve member
Prior art date
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Abandoned
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US12/641,908
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English (en)
Inventor
Satoshi Umemura
Tatsuya Ito
Masahiro Kawaguchi
Ken Suitou
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Toyota Industries Corp
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Toyota Industries Corp
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Publication date
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Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ITO, TATSUYA, KAWAGUCHI, MASAHIRO, SUITOU, KEN, UMEMURA, SATOSHI
Publication of US20100158710A1 publication Critical patent/US20100158710A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-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
    • F04C18/0207—Rotary-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
    • F04C18/0215—Rotary-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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/21—Pressure difference

Definitions

  • the present invention relates to a scroll compressor.
  • a conventional scroll compressor is disclosed in Japanese Unexamined Patent Application Publication No. 57-76291.
  • the compressor has a housing, a fixed scroll and a movable scroll that cooperate to form a suction chamber, a compression chamber, a discharge chamber and a backpressure chamber.
  • the movable scroll is pressed against the fixed scroll by backpressure in the backpressure chamber.
  • high pressure such as discharge pressure in the discharge chamber is introduced into the backpressure chamber thorough a fixed throttle, and an adjusting valve is provided between the backpressure chamber and the suction chamber.
  • the adjusting valve has a valve chamber connected to the backpressure chamber through a backpressure passage and connected to the suction chamber through a low-pressure passage.
  • the adjusting valve has a ball-shaped valve member provided in the valve chamber and urged so as to close the backpressure passage.
  • the valve member is operated by pressure difference between the backpressure in the backpressure chamber and the suction pressure in the suction chamber so as to adjust the backpressure.
  • the movable scroll is pressed against the fixed scroll by load that is based on the backpressure.
  • the backpressure needs to be controlled appropriately by the adjusting valve in order to reduce power loss and prevent poor compression.
  • backpressure Pb load
  • discharge pressure Pd in order to reduce power loss and prevent poor compression, as shown in FIG. 8 .
  • the fixed throttle and the adjusting valve are adjusted in the above compressor so as to prevent poor compression in a condition where the discharge pressure is high, the backpressure (load) becomes too high in a condition where the discharge pressure is low, which results in power loss as indicated by hatching in FIG. 8 .
  • the backpressure in the above compressor, it is difficult to control the backpressure appropriately in various operating conditions of the compressor, which may cause power loss and poor compression.
  • the discharge pressure is introduced through the fixed throttle into the backpressure chamber.
  • the inner diameter of the fixed throttle is large, compression efficiency of the compressor may be reduced.
  • the inner diameter of the fixed scroll is small, it may be difficult to design the arrangement of the fixed throttle.
  • Japanese Unexamined Patent Application Publication No. 11-132165 discloses a control valve for controlling the backpressure.
  • the control valve has a valve member to which not only the backpressure and the suction pressure but also the discharge pressure are applied.
  • the backpressure is appropriately controlled, as compared to the above compressor using the fixed throttle and the adjusting valve.
  • the backpressure Pb (load) is appropriately controlled depending on the discharge pressure Pd, which allows reduction of power loss and prevents poor compression in various operating conditions of the compressor.
  • the backpressure, the suction pressure and the discharge pressure are applied to the valve member, however, when the amount of backpressure applied to the valve member is large, the backpressure, which is to be controlled, greatly affects the control of the backpressure itself, so that the movement of the valve member may become unstable. For example, if the valve member is moved by high backpressure so that the backpressure chamber is connected to the suction chamber, the backpressure is decreased quickly, so that the valve member in turn is moved in opposite direction. Thus, the movement of the valve member becomes unstable, which makes it difficult to control the control valve appropriately.
  • the present invention is directed to providing a scroll compressor that allows a backpressure control valve to be controlled appropriately thereby to reduce power loss and prevent poor compression in various operating conditions of the compressor.
  • a scroll compressor in accordance with an aspect of the present invention, includes a housing, a fixed scroll, a movable scroll and a control valve.
  • the housing has a suction chamber, a discharge chamber and a backpressure chamber formed therein.
  • the fixed scroll is accommodated in the housing.
  • the movable scroll is accommodated in the housing.
  • the movable scroll cooperates with the fixed scroll to form therebetween a compression chamber.
  • the movable scroll and the fixed scroll are pressed against each other by backpressure in the backpressure chamber.
  • the control valve is provided for controlling the backpressure in the backpressure chamber by communication with the suction chamber, the discharge chamber or the compression chamber.
  • the control valve has a first chamber, a second chamber and a third chamber arranged in this order.
  • the first chamber is connected to the discharge chamber or the compression chamber
  • the second chamber is connected to the backpressure chamber
  • the third chamber is connected to the suction chamber.
  • the control valve has a valve member.
  • the valve member has a first pressure-receiving surface located in the first chamber, a second pressure-receiving surface located in the second chamber and a third pressure-receiving surface located in the third chamber.
  • the area of the third pressure-receiving surface is larger than the area of the first pressure-receiving surface and larger than the area of the second pressure-receiving surface.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention
  • FIG. 2 is a schematic block diagram of the compressor of FIG. 1 ;
  • FIG. 3 is a sectional view of a control valve of the compressor of FIG. 1 ;
  • FIG. 4 is a schematic view showing pressure-receiving surfaces of a valve member of the control valve of FIG. 3 ;
  • FIG. 5 is a schematic block diagram of a scroll compressor according to a second embodiment of the present invention.
  • FIG. 6 is a sectional view of the second embodiment of the control valve
  • FIG. 7 is a schematic view showing pressure-receiving surfaces of a valve member of the control valve of FIG. 6 ;
  • FIG. 8 is a graph showing a characteristic of a conventional compressor and a calculated ideal value.
  • FIG. 9 is a graph showing a characteristic of the compressor according to the embodiments of the present invention.
  • FIG. 1 shows a scroll compressor according to the first embodiment of the present invention. It is noted that the right-hand side and the left-hand side as viewed in FIG. 1 are the front side and the rear side of the scroll compressor, respectively, and that the upper and lower sides as viewed in FIG. 1 are the upper and lower sides of the scroll compressor when installed in place, respectively.
  • the scroll compressor (hereinafter referred to as compressor) is used, for example, in a vehicle air conditioner.
  • the compressor has a cylindrical front housing 11 the opening of which is covered by a rear housing 12 .
  • the front housing 11 and the rear housing 12 form a housing assembly 10 (housing) of the compressor.
  • the housing assembly 10 accommodates therein a shaft support 15 , a fixed scroll 16 and a movable scroll 22 .
  • the fixed scroll 16 is located behind the shaft support 15 .
  • the front housing 11 and the rear housing 12 are connected to each other by using bolts 13 while keeping the shaft support 15 in contact with the fixed scroll 16 .
  • the compressor has a suction chamber 42 formed between the front housing 11 and the shaft support 15 and a discharge chamber 47 formed between the fixed scroll 16 and the rear housing 12 .
  • the shaft support 15 has a cylindrical base 17 and a flange 18 that projecting radially outward from the rear end of the base 17 .
  • the base 17 has an end wall 17 A through which a shaft hole 19 is formed.
  • the flange 18 is engaged with a step 21 that is formed in the inner peripheral surface of the front housing 11 .
  • the shaft support 15 has a pin 23 A fixed to the rear end thereof for preventing the rotation of the movable scroll 22 on its own axis.
  • the compressor has a rotary shaft 24 extending in the front housing 11 in longitudinal direction of the compressor.
  • the front end of the rotary shaft 24 is rotatably supported by a bearing 25 that is mounted on the middle of the end wall 11 A of the front housing 11 .
  • the rear end of the rotary shaft 24 is rotatably supported by a bearing 26 that is mounted in the base 17 of the shaft support 15 .
  • the gap between the shaft support 15 and the rotary shaft 24 is sealed by a seal member 30 that is retained on the shaft support 15 by a circlip 31 .
  • the rotary shaft 24 has at the rear end thereof an eccentric pin 32 that is eccentric to the axis of the rotary shaft 24 .
  • the eccentric pin 32 is fitted into a cylindrical bush 33 .
  • the bush 33 has a sector-shaped balance weight 35 formed in the half of the circumference thereof. The balance weight 35 serves to cancel the centrifugal force caused by the rotation of the movable scroll 22 .
  • the fixed scroll 16 has a cylindrical base 16 C and a scroll wall 16 D.
  • the base 16 C is formed by an end wall 16 A and a side wall 16 B.
  • the scroll wall 16 D is located radially inward of the side wall 16 B and projects forward from the end wall 16 A.
  • the movable scroll 22 is located between the fixed scroll 16 and the shaft support 15 and coupled to the bush 33 through a bearing 34 .
  • the movable scroll 22 has a circular base plate 22 A and a scroll wall 22 B that projects rearward from the base plate 22 A.
  • the fixed scroll 16 and the movable scroll 22 are engaged with each other so that the end of the scroll wall 16 D slides on the base plate 22 A and the end of the scroll wall 22 B slides on the end wall 16 A of the base 16 C.
  • the base plate 22 A of the movable scroll 22 is formed with a recess 37 into which a ring 23 B is loosely fitted for receiving the pin 23 A on the shaft support 15 .
  • the pin 23 A slides and rolls on the inner peripheral surface of the ring 23 B.
  • the fixed scroll 16 cooperates with the movable scroll 22 to form therebetween a compression chamber 38 that is defined by the scroll walls 16 D and 22 B.
  • the base plate 22 A of the movable scroll 22 cooperates with the shaft support 15 to form therebetween a backpressure chamber 39 that faces the rear end of the rotary shaft 24 .
  • the compressor has a suction region 41 that is defined by the shaft support 15 , the side wall 16 B of the fixed scroll 16 and the radially outermost portion of the movable scroll 22 .
  • the suction chamber 42 communicates with the suction region 41 through a suction passage 43 that is formed in the lower portion of the front housing 11 .
  • a stator 44 is fixedly mounted on the inner peripheral surface of the front housing 11
  • a rotor 45 is fixed to the rotary shaft 24 at a position radially inward of the stator 44 .
  • the rotor 45 , the stator 44 and the rotary shaft 24 constitute a motor mechanism 40 that allows the rotary shaft 24 to rotate integrally with the rotor 45 when the stator 44 is energized.
  • the side wall of the front housing 11 has an inlet port 46 formed therethrough.
  • the inlet port 46 is connected via a pipe to an evaporator that is connected to an expansion valve and a condenser via a pipe.
  • the compressor, the evaporator, the expansion valve and the condenser constitute a refrigeration circuit of a vehicle air conditioner. Low-pressure and low-temperature refrigerant gas in the refrigeration circuit is introduced from the inlet port 46 through the suction chamber 42 and the suction passage 43 into the suction region 41 .
  • the discharge chamber 47 is formed between the base 16 C of the fixed scroll 16 and the rear housing 12 .
  • the base 16 C has a discharge port 48 through which the compression chamber 38 communicates with the discharge chamber 47 .
  • the discharge port 48 is normally closed by a discharge valve (not shown) the opening of which is restricted by a retainer 49 mounted to the rear end of the base 16 C.
  • the rear housing 12 is formed with an oil separation chamber 51 that extends vertically behind the discharge chamber 47 .
  • the oil separation chamber 51 is separated from the discharge chamber 47 by a partition wall 52 .
  • the partition wall 52 is formed therethrough with a discharge hole 53 through which the oil separation chamber 51 communicates with the discharge chamber 47 .
  • an oil separator 55 is provided in the oil separation chamber 51 for separating lubricating oil contained in refrigerant gas.
  • the oil separator 55 is of a generally cylindrical shape and fitted into the upper portion of the oil separation chamber 51 .
  • the lower portions of the oil separation chamber 51 and the discharge chamber 47 are connected through an oil hole 54 .
  • the lower portion of the discharge chamber 47 is also connected to the backpressure chamber 39 through a supply passage 57 .
  • the supply passage 57 is formed by a communication hole 59 and a circular slit 60 .
  • the communication hole 59 extends through the side wall 16 B of the fixed scroll 16 .
  • the slit 60 is formed in a plate 61 that is interposed between the shaft support 15 and the movable scroll 22 , so as to extend to the backpressure chamber 39 .
  • the slit 60 serves as a fixed throttle for throttling the supply passage 57 at a position upstream of the backpressure chamber 39 as viewed in flowing direction of refrigerant gas.
  • the communication hole 59 is located upstream of the slit 60 .
  • High-pressure refrigerant gas in the discharge chamber 47 which contains lubricating oil, is delivered through the supply passage 57 into the backpressure chamber 39 (see FIG. 2
  • the backpressure chamber 39 is connected to the suction chamber 42 through a bleed passage 71 that is provided with a backpressure control valve 72 (hereinafter referred to as control valve).
  • the bleed passage 71 is formed by a low-pressure passage 71 A and a backpressure passage 71 B.
  • the low-pressure passage 71 A connects the suction chamber 42 to the control valve 72 .
  • the backpressure passage 71 B connects the control valve 72 to the backpressure chamber 39 .
  • the control valve 72 has a case 73 that cooperates with the front housing 11 to form a valve chamber 74 .
  • the valve chamber 74 includes a first chamber 74 A connected to the discharge chamber 47 through a high-pressure passage 75 , a second chamber 74 B connected to the backpressure chamber 39 through the backpressure passage 71 B, and a third chamber 74 C connected to the suction chamber 42 through the low-pressure passage 71 A.
  • the first, second and third chambers 74 A, 74 B and 74 C are arranged in this order as viewed from the bottom of FIG. 3 .
  • the valve chamber 74 may be formed by any suitable member other than the front housing 11 and the case 73 .
  • the control valve 72 has O-rings 78 A and 78 B provided between the front housing 11 and the case 73 .
  • the control valve 72 has a valve member 76 accommodated in the valve chamber 74 so as to move up and down.
  • the valve member 76 includes a tapered portion 76 A tapered downward and a cylindrical portion 76 B arranged coaxially with the tapered portion 76 A.
  • the cylindrical portion 76 B is formed integrally with the tapered portion 76 A and extends downward from the lower end of the tapered portion 76 A.
  • the tapered portion 76 A is tapered to the second chamber 74 B.
  • the tapered portion 76 A has a spring seat 76 C formed in the upper surface thereof for retaining a spring 77 .
  • the valve member 76 has a first pressure-receiving surface S 1 located in the first chamber 74 A, a second pressure-receiving surface S 2 located in the second chamber 74 B and a third pressure-receiving surface S 3 located in the third chamber 74 C.
  • the area of the first pressure-receiving surface S 1 corresponds to the area of the lower surface of the cylindrical portion 76 B.
  • the area of the third pressure-receiving surface S 3 corresponds to the cross-sectional area of the large end of the tapered portion 76 A.
  • the area of the second pressure-receiving surface S 2 corresponds to the difference between the cross-sectional area of the large end of the tapered portion 76 A and the cross-sectional area of the cylindrical portion 76 B, that is, the difference between the areas of the first and third pressure-receiving surfaces S 1 and S 3 .
  • This relation could be slightly changed depending on the relative position of the tapered portion 76 A and the second and third chambers 74 B and 74 C.
  • the area of the third pressure-receiving surface S 3 is larger than the area of the first pressure-receiving surface S 1 and also larger than the area of the second pressure-receiving surface S 2 .
  • the area of the third pressure-receiving surface S 3 is the sum of the areas of the first and second pressure-receiving surfaces S 1 and S 2 .
  • the lower surface of the cylindrical portion 76 B located in the first chamber 74 A forms the first pressure-receiving surface S 1
  • the upper surface of the tapered portion 76 A located in the third chamber 74 C forms the third pressure-receiving surface S 3
  • the tapered surface of the tapered portion 76 A located in the second chamber 74 B forms the second pressure-receiving surface S 2 .
  • the area of the second pressure-receiving surface S 2 corresponds to the area of the tapered portion 76 A located in the second chamber 74 B in axial direction of the valve member 76 .
  • the tapered portion 76 A of the valve member 76 is located across the third chamber 74 C and the second chamber 74 B.
  • the cylindrical portion 76 B of the valve member 76 is slidably fitted in the first chamber 74 A so that the first chamber 74 A is hermetically sealed from the second chamber 74 B.
  • the control valve 72 has a valve seat 74 D provided between the third chamber 74 C and the second chamber 74 B.
  • the valve seat 74 D is associated with the tapered portion 76 A of the valve member 76 .
  • the third chamber 74 C is connected to the suction chamber 42 through the low-pressure passage 71 A.
  • the lower portion of the second chamber 74 B is connected to the backpressure chamber 39 through the backpressure passage 71 B.
  • the valve seat 74 D faces the tapered portion 76 A of the valve member 76 .
  • the valve seat 74 D has an inner diameter that is slightly larger than the diameter of the large end of the tapered portion 76 A.
  • the tapered portion 76 A is slidable in the second chamber 74 B so that the second chamber 74 B is hermetically sealed from the third chamber 74 C.
  • the O-ring 78 A is provided between the low-pressure passage 71 A and the backpressure passage 71 B.
  • the lower portion of the first chamber 74 A is connected to the discharge chamber 47 through the high-pressure passage 75 .
  • the O-ring 78 B is provided between the high-pressure passage 75 and the backpressure passage 71 B.
  • the spring 77 is interposed between the valve seat 76 C of the valve member 76 and the inner surface of the case 73 so as to urge the tapered portion 76 A toward the valve seat 74 D.
  • the refrigerant gas is then introduced into the compression chamber 38 and compressed therein.
  • the pressure of the refrigerant gas is increased to a predetermined discharge pressure
  • the refrigerant gas is discharged through the discharge port 48 into the discharge chamber 47 .
  • the refrigerant gas is delivered through the discharge hole 53 into the oil separation chamber 51 where lubricating oil contained in the refrigerant gas is separated.
  • the refrigerant gas from which the lubricating oil has been separated is delivered through the oil separator 55 and the outlet port 56 into the condenser.
  • the vehicle air conditioner is thus operated.
  • Lubricating oil separated from the refrigerant gas is dropped from the oil separator 55 into the bottom of the oil separation chamber 51 and stored therein.
  • the lubricating oil stored in the oil separation chamber 51 is delivered through the slit 60 of the supply passage 57 to the backpressure chamber 39 , along with a small amount of refrigerant gas (see FIG. 2 ).
  • the discharge pressure Pd in the discharge chamber 47 is applied through the high-pressure passage 75 to the first pressure-receiving surface S 1 of the valve member 76 so as to move the valve member 76 upward.
  • the tapered portion 76 A is moved apart from the valve seat 74 D.
  • the amount of refrigerant gas flowing from the backpressure chamber 39 through the backpressure passage 71 B, the second chamber 74 B, the valve seat 74 D, the third chamber 74 C and the low-pressure passage 71 A into the suction chamber 42 is increased, so that the backpressure Pb in the backpressure chamber 39 is decreased.
  • the suction pressure Ps in the suction chamber 42 is applied through the low-pressure passage 71 A to the third pressure-receiving surface S 3 of the valve member 76 so as to move the valve member 76 downward.
  • the valve member 76 is moved downward, the tapered portion 76 A is moved toward the valve seat 74 D. In this case, the amount of refrigerant gas flowing from the backpressure chamber 39 into the suction chamber 42 is decreased, so that the backpressure Pb is increased.
  • the valve member 76 receives not only the backpressure Pb and the suction pressure Ps but also the discharge pressure Pd. Therefore, the backpressure Pb is appropriately controlled, as compared to the conventional compressor using the fixed throttle and adjusting valve as described in the background section. Also, the backpressure Pb (load) is appropriately controlled depending on the discharge pressure Pd, which allows reduction of power loss and prevents poor compression in various operating conditions of the compressor.
  • the area of the third pressure-receiving surface S 3 is larger than the area of the second pressure-receiving surface S 2 , the amount of backpressure Pb applied to the valve member 76 becomes smaller.
  • the backpressure which is to be controlled, less affects the control of the backpressure itself, so that the movement of the valve member 76 becomes stable. This results in highly-responsive control valve 72 .
  • the amount of discharge pressure Pd applied to the valve member 76 also becomes smaller. In this case, the valve member 76 is moved easily as the suction pressure Ps is decreased.
  • FIG. 9 is a graph showing a characteristic of the compressor according to the embodiments of the present invention.
  • the first embodiment of the compressor allows reduction of power loss not only in a condition where the suction pressure Ps is high and the discharge pressure Pd is high, but also in a condition where the suction pressure Ps is low and the discharge pressure Pd is high.
  • the compressor as a comparative example in FIG. 9 is composed in such a way that the backpressure Pb, the suction pressure Ps and the discharge pressure Pd are applied to the valve member of the control valve, and the area of the surface of the valve member receiving the suction pressure Ps is the same as the area of the surface of the valve member receiving the discharge pressure Pd.
  • the compressor according to the first embodiment has good performance in the condition where the suction pressure Ps is low, as compared to the comparative example.
  • the operation of the compressor is affected by the suction pressure Ps. Therefore, the first embodiment of the compressor achieving good performance regardless of the change in the suction pressure Ps is very practical.
  • the first embodiment of the compressor allows not only the appropriate control of the highly-responsive control valve 72 but also reduction of power loss and prevention of poor compression in various operating conditions of the compressor.
  • the discharge chamber 47 is connected to the backpressure chamber 39 through the supply passage 57 , and the amount of refrigerant gas flowing from the backpressure chamber 39 into the suction chamber 42 is limited to the minimum by the control valve 72 . Therefore, the discharge pressure Pd relieved to the suction chamber 42 is minimum, which results in high compression efficiency of the compressor.
  • valve member 76 since the tapered portion 76 A of the valve member 76 is tapered toward the second chamber 74 B, the opening of the valve member 76 is gradually varied as the valve member 76 is moved. This offers more flexibility in designing and selecting specifications for the spring 77 .
  • the compressor requires neither sensors for detecting pressures such as the discharge pressure Pd and the suction pressure Ps nor controllers for calculating load condition for operating the valve member 76 , which allows manufacturing cost reduction.
  • FIGS. 5 , 6 and 7 show the second embodiment of the present invention.
  • same reference numerals are used for the common elements or components in the first and second embodiment, and the description of such elements or components for the second embodiment will be omitted.
  • the backpressure chamber 39 is connected to the discharge chamber 47 through the supply passage 57 that is provided with a backpressure control valve 82 (hereinafter referred to as control valve).
  • the supply passage 57 is formed by high-pressure passages 81 A and 81 B and a backpressure passage 81 C.
  • the high-pressure passages 81 A and 81 B connect the discharge chamber 47 to the control valve 82 .
  • the backpressure passage 81 C connects the control valve 82 to the backpressure chamber 39 .
  • the backpressure chamber 39 and the suction chamber 42 are connected through the bleed passage 71 that is provided with a fixed throttle 80 .
  • the control valve 82 has a case 83 that cooperates with the front housing 11 to form a valve chamber 84 .
  • the valve chamber 84 includes chambers 84 A and 84 B (first chamber) connected to the discharge chamber 47 through the high-pressure passages 81 A and 81 B, a chamber 84 C (second chamber) connected to the backpressure chamber 39 through the backpressure passage 81 C, and a chamber 84 D (third chamber) connected to the suction chamber 42 through a low-pressure passage 85 .
  • the chambers 84 A, 84 B, 84 C and 84 D are arranged in this order as viewed from the bottom of FIG. 6 .
  • the valve chamber 84 may be formed by any suitable member other than the front housing 11 and the case 83 .
  • the control valve 82 has O-rings 88 A and 88 B provided between the front housing 11 and the case 83 .
  • the control valve 82 has a valve member 86 accommodated in the valve chamber 84 so as to move up and down.
  • the valve member 86 includes a cylindrical head portion 86 A, a cylindrical neck portion 86 B arranged coaxially with the head portion 86 A, a tapered portion 86 C tapered upward and a cylindrical portion 86 D arranged coaxially with the tapered portion 86 C.
  • the neck portion 86 B is formed integrally with the head portion 86 A and extends downward from the lower end of the head portion 86 A.
  • the tapered portion 86 C is formed integral with the neck portion 86 B and tapered to the chamber 84 C.
  • the cylindrical portion 86 D is formed integrally with the tapered portion 86 C and extends downward from the lower end of the tapered portion 86 C.
  • the valve member 86 has a first pressure-receiving surface S 1 located in the chamber 84 A, a second pressure-receiving surface S 2 located in the chamber 84 C and a third pressure-receiving surface S 3 located in the chamber 84 D.
  • the area of the first pressure-receiving surface S 1 corresponds to the area of the lower surface of the cylindrical portion 86 D.
  • the area of the third pressure-receiving surface S 3 corresponds to the area of the upper surface of the head portion 86 A.
  • the area of the second pressure-receiving surface S 2 corresponds to the difference between the lower surface of the head portion 86 A and the cross-sectional area of the cylindrical portion 86 D, that is, the difference between the areas of the first and third pressure-receiving surfaces S 1 and S 3 .
  • This relation could be slightly changed depending on the relative position of the tapered portion 86 C and the chambers 84 B and 84 C.
  • the area of the third pressure-receiving surface S 3 is larger than the area of the first pressure-receiving surface S 1 and also larger than the area of the second pressure-receiving surface S 2 .
  • the area of the third pressure-receiving surface S 3 is the sum of the areas of the first and second pressure-receiving surfaces S 1 and S 2 .
  • the cylindrical portion 86 D of the valve member 86 is slidably fitted in the chamber 84 A so that the chamber 84 A is hermetically sealed from the chamber 84 B.
  • the tapered portion 86 C of the valve member 86 is located across the chamber 84 B and the chamber 84 C.
  • the control valve 82 has a valve seat 84 E provided between the chamber 84 B and the chamber 84 C.
  • the valve seat 84 E is associated with the tapered portion 86 C of the valve member 86 .
  • the chamber 84 D is connected to the suction chamber 42 through the low-pressure passage 85 .
  • the upper portion of the chamber 84 C is connected to the backpressure chamber 39 through the backpressure passage 81 C.
  • the valve seat 84 E faces the tapered portion 86 C of the valve member 86 .
  • the valve seat 84 E has an inner diameter that is slightly larger than the diameter of the large end of the tapered portion 86 C.
  • the tapered portion 86 C is slidable in the chamber 84 C so that the chamber 84 C is hermetically sealed from the chamber 84 B.
  • the O-ring 88 A is provided between the low-pressure passage 85 and the backpressure passage 81 C.
  • the chambers 84 A and 84 B are connected to the discharge chamber 47 through the high-pressure passages 81 A and 81 B.
  • the O-ring 88 B is provided between the high-pressure passages 81 A and 81 B and the backpressure passage 81 C.
  • the control valve 82 has a spring 87 that is interposed between the upper surface of the head portion 86 A of the valve member 86 and the inner surface of the case 83 so as to urge the tapered portion 86 C away from the valve seat 84 E.
  • the discharge pressure Pd in the discharge chamber 47 is applied through the high-pressure passages 81 A and 81 B to the first pressure-receiving surface S 1 of the valve member 86 so as to move the valve member 86 upward.
  • the valve member 86 is moved upward, the tapered portion 86 C is moved toward the valve seat 84 E.
  • the amount of refrigerant gas flowing from the discharge chamber 47 through the high-pressure passage 81 B, the chamber 84 B, the valve seat 84 E, the chamber 84 C and the backpressure passage 81 C into the backpressure chamber 39 is decreased.
  • Refrigerant gas in the backpressure chamber 39 is delivered through the bleed passage 71 to the suction chamber 42 , and the backpressure Pb in the backpressure chamber 39 is decreased, accordingly.
  • the suction pressure Ps in the suction chamber 42 is applied through the low-pressure passage 85 to the third pressure-receiving surface S 3 of the valve member 86 so as to move the valve member 86 downward.
  • the valve member 86 is moved downward, the tapered portion 86 C moved apart from the valve seat 84 E. In this case, the amount of refrigerant gas flowing from the discharge chamber 47 into the backpressure chamber 39 is increased, so that the backpressure Pb is increased.
  • the second embodiment offers the advantages similar to those of the first embodiment.
  • the present invention is applied to the scroll compressor with the motor mechanism 40 , that is, a motor-driven compressor.
  • the present invention may be applied to a scroll compressor with no electric motor.
  • the supply passage 57 and the high-pressure passage 75 connect the discharge chamber 47 to the backpressure chamber 39 .
  • the supply passage 57 and the high-pressure passage 75 may connect the compression chamber 38 to the backpressure chamber 39 .
  • the movable scroll 22 is pressed against the fixed scroll 16 by backpressure.
  • the fixed scroll 16 may be pressed against the movable scroll 22 by backpressure.
  • the first chamber 74 A ( 84 A, 84 B) is connected to the discharge chamber 47 .
  • the first chamber 74 A ( 84 A, 84 B) may be connected to the compression chamber 38 .
  • the first chamber 74 A ( 84 A, 84 B) may be connected to the radially innermost portion of the compression chamber 38 between the fixed and movable scrolls 16 and 22 , for example.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US12/641,908 2008-12-24 2009-12-18 Scroll compressor Abandoned US20100158710A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-328142 2008-12-24
JP2008328142A JP2010150967A (ja) 2008-12-24 2008-12-24 スクロール型圧縮機

Publications (1)

Publication Number Publication Date
US20100158710A1 true US20100158710A1 (en) 2010-06-24

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US12/641,908 Abandoned US20100158710A1 (en) 2008-12-24 2009-12-18 Scroll compressor

Country Status (5)

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US (1) US20100158710A1 (zh)
EP (1) EP2206926A2 (zh)
JP (1) JP2010150967A (zh)
KR (1) KR101128756B1 (zh)
CN (1) CN101761478A (zh)

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US20090320283A1 (en) * 2003-03-26 2009-12-31 Ishikawajima-Harima Heavy Industries Co., Ltd. Suction filter, turbo compressor, and method for compact assembling of the same
DE102015120151A1 (de) * 2015-11-20 2017-05-24 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug
WO2017164628A1 (ko) * 2016-03-22 2017-09-28 한온시스템 주식회사 특히 차량 에어컨 또는 열 펌프 내 스크롤 압축기를 위한 제어 유량 조정 밸브
US10036386B2 (en) 2013-07-31 2018-07-31 Trane International Inc. Structure for stabilizing an orbiting scroll in a scroll compressor
US20180258933A1 (en) * 2017-03-10 2018-09-13 OET GmbH Positive-displacement machine according to the spiral principle, method for operating a positive-displacement machine, positive-displacement spiral, vehicle air-conditioning system and vehicle
DE102016218396B4 (de) 2015-12-23 2019-02-07 OET GmbH Kältemittelverdichter
US20190128579A1 (en) * 2016-07-15 2019-05-02 Hanon Systems Compression device and control mass flow separation method
US10738777B2 (en) 2016-06-02 2020-08-11 Trane International Inc. Scroll compressor with partial load capacity
US11131306B2 (en) 2017-05-19 2021-09-28 OET GmbH Displacement machine including only one displacement spiral passage and gas connection line in communication with a counter pressure chamber
US20220170461A1 (en) * 2019-03-20 2022-06-02 Sanden Automotive Components Corporation Scroll compressor
US20220372975A1 (en) * 2019-11-04 2022-11-24 Danfoss Commercial Compressors Scroll compressor including a first and a second axial stabilizing arrangement
DE102021118962A1 (de) 2021-07-22 2023-01-26 Hanon Systems Steuerstromregelventil für Spiralverdichter
WO2023033400A1 (en) * 2021-09-06 2023-03-09 Hanon Systems Back pressure valve for scroll compressors
DE112017003912B4 (de) 2016-08-04 2023-08-31 Sanden Corporation Spiralverdichter
DE102023117639A1 (de) 2022-08-18 2024-02-29 Hanon Systems Steuerstromgegendruckdüse für Spiralverdichter sowie ein Verfahren zur Partikelentfernung aus Kältemittel-Öl-Gemischen in einer Steuerstromgegendruckdüse von Spiralverdichtern

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JP5418425B2 (ja) 2010-07-01 2014-02-19 コベルコ建機株式会社 キャビンのドア
KR101827829B1 (ko) * 2011-01-07 2018-02-12 삼성전자주식회사 스크롤 압축기
CN103174648B (zh) * 2011-12-20 2016-08-24 华域三电汽车空调有限公司 涡旋压缩机
KR101467024B1 (ko) * 2012-02-16 2014-12-01 한라비스테온공조 주식회사 스크롤 압축기
KR101509290B1 (ko) * 2012-09-17 2015-04-07 한라비스테온공조 주식회사 스크롤 압축기
KR101642178B1 (ko) * 2013-07-02 2016-07-25 한온시스템 주식회사 스크롤 압축기
JP6058723B2 (ja) * 2015-03-23 2017-01-11 三機工業株式会社 水噴霧加湿装置
JP2017115762A (ja) * 2015-12-25 2017-06-29 サンデンホールディングス株式会社 スクロール型圧縮機
KR102486465B1 (ko) * 2016-04-26 2023-01-10 학교법인 두원학원 스크롤 압축기의 배압제어 수단
JP6875201B2 (ja) * 2017-06-02 2021-05-19 サンデンホールディングス株式会社 背圧制御弁及びスクロール型圧縮機
CN112682307B (zh) * 2020-12-29 2022-05-10 罗伯特·博世有限公司 涡旋式压缩机

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US6905318B2 (en) * 2000-07-26 2005-06-14 Hitachi, Ltd. Compressor including tapered discharged valve and valve seat
US20020102172A1 (en) * 2001-02-01 2002-08-01 Hiroyuki Gennami Scroll compressor and method for controlling back pressure for the same
US20050217288A1 (en) * 2004-03-31 2005-10-06 Denso Corporation & Nippon Soken, Inc. System utilizing waste heat of internal combustion engine

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7967551B2 (en) * 2003-03-26 2011-06-28 Ishikawajima-Harima Heavy Industries Co., Ltd. Suction filter, turbocompressor, and method for compact assembling of the same
US20090320283A1 (en) * 2003-03-26 2009-12-31 Ishikawajima-Harima Heavy Industries Co., Ltd. Suction filter, turbo compressor, and method for compact assembling of the same
US10036386B2 (en) 2013-07-31 2018-07-31 Trane International Inc. Structure for stabilizing an orbiting scroll in a scroll compressor
EP3377766B1 (de) * 2015-11-20 2024-07-03 OET GmbH Verdrängermaschine nach dem spiralprinzip, verfahren zum betreiben einer verdrängermaschine, fahrzeugklimaanlage und fahrzeug
DE102015120151A1 (de) * 2015-11-20 2017-05-24 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug
US11448218B2 (en) * 2015-11-20 2022-09-20 OET GmbH Displacement machine according to the spiral principle, method to regulate pressure in the counter-pressure chamber by using a pressure difference and characteristic curve
US20190072094A1 (en) * 2015-11-20 2019-03-07 OET GmbH Displacement machine according to the spiral principle, method for operating a displacement machine, vehicle air-conditioning system, and vehicle
DE102016218396B4 (de) 2015-12-23 2019-02-07 OET GmbH Kältemittelverdichter
DE102016105302A1 (de) 2016-03-22 2017-09-28 Hanon Systems Steuerstromregelventil, insbesondere für Scrollverdichter in Fahrzeugklimaanlagen oder Wärmepumpen
DE102016105302B4 (de) 2016-03-22 2018-06-14 Hanon Systems Steuerstromregelventil, insbesondere für Spiralverdichter in Fahrzeugklimaanlagen oder Wärmepumpen
EP3971454A1 (en) 2016-03-22 2022-03-23 Hanon Systems Control flowrate regulating valve specifically for scroll compressor inside vehicle air conditioner or heat pump
US11047383B2 (en) 2016-03-22 2021-06-29 Hanon Systems Control flowrate regulating valve specifically for scroll compressor inside vehicle air conditioner or heat pump
WO2017164628A1 (ko) * 2016-03-22 2017-09-28 한온시스템 주식회사 특히 차량 에어컨 또는 열 펌프 내 스크롤 압축기를 위한 제어 유량 조정 밸브
US10738777B2 (en) 2016-06-02 2020-08-11 Trane International Inc. Scroll compressor with partial load capacity
US20190128579A1 (en) * 2016-07-15 2019-05-02 Hanon Systems Compression device and control mass flow separation method
US11262113B2 (en) * 2016-07-15 2022-03-01 Hanon Systems Compression device and control mass flow separation method
DE112017003912B4 (de) 2016-08-04 2023-08-31 Sanden Corporation Spiralverdichter
US20180258933A1 (en) * 2017-03-10 2018-09-13 OET GmbH Positive-displacement machine according to the spiral principle, method for operating a positive-displacement machine, positive-displacement spiral, vehicle air-conditioning system and vehicle
US10801496B2 (en) * 2017-03-10 2020-10-13 OET GmbH Positive-displacement machine according to the spiral principle, method for operating a positive-displacement machine, positive-displacement spiral, vehicle air-conditioning system and vehicle
CN108571447A (zh) * 2017-03-10 2018-09-25 Oet股份有限公司 根据螺旋原理的容积式机器、操作容积式机器的方法、容积式螺旋件、车辆空调系统和车辆
US11131306B2 (en) 2017-05-19 2021-09-28 OET GmbH Displacement machine including only one displacement spiral passage and gas connection line in communication with a counter pressure chamber
US20220170461A1 (en) * 2019-03-20 2022-06-02 Sanden Automotive Components Corporation Scroll compressor
US11933297B2 (en) * 2019-03-20 2024-03-19 Sanden Corporation Scroll compressor
US20220372975A1 (en) * 2019-11-04 2022-11-24 Danfoss Commercial Compressors Scroll compressor including a first and a second axial stabilizing arrangement
US11841013B2 (en) * 2019-11-04 2023-12-12 Danfoss Commercial Compressors Scroll compressor including a first and a second axial stabilizing arrangement
DE102021118962A1 (de) 2021-07-22 2023-01-26 Hanon Systems Steuerstromregelventil für Spiralverdichter
WO2023033400A1 (en) * 2021-09-06 2023-03-09 Hanon Systems Back pressure valve for scroll compressors
DE102023117639A1 (de) 2022-08-18 2024-02-29 Hanon Systems Steuerstromgegendruckdüse für Spiralverdichter sowie ein Verfahren zur Partikelentfernung aus Kältemittel-Öl-Gemischen in einer Steuerstromgegendruckdüse von Spiralverdichtern

Also Published As

Publication number Publication date
EP2206926A2 (en) 2010-07-14
KR20100075369A (ko) 2010-07-02
KR101128756B1 (ko) 2012-03-23
CN101761478A (zh) 2010-06-30
JP2010150967A (ja) 2010-07-08

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