EP2461122B1 - Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection - Google Patents

Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection Download PDF

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Publication number
EP2461122B1
EP2461122B1 EP09847791.2A EP09847791A EP2461122B1 EP 2461122 B1 EP2461122 B1 EP 2461122B1 EP 09847791 A EP09847791 A EP 09847791A EP 2461122 B1 EP2461122 B1 EP 2461122B1
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EP
European Patent Office
Prior art keywords
refrigerant
valve
chamber
compression chamber
base plate
Prior art date
Legal status (The legal status 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 status listed.)
Not-in-force
Application number
EP09847791.2A
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German (de)
English (en)
Other versions
EP2461122A4 (fr
EP2461122A1 (fr
Inventor
Masashi MYOGAHARA
Teruhiko Nishiki
Hiroyasu Takahashi
Rei MISAKA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP2461122A1 publication Critical patent/EP2461122A1/fr
Publication of EP2461122A4 publication Critical patent/EP2461122A4/fr
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Publication of EP2461122B1 publication Critical patent/EP2461122B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary 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
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves

Definitions

  • the present invention relates to a heat pump apparatus equipped with an injection circuit and an injectable compressor equipped with an injection mechanism, for example.
  • the present invention also relates to a method of producing a scroll compressor equipped with an injection mechanism.
  • Patent Document 1 JP 2006-112708 A
  • JP 03043691 specifies an injectable compressor comprising a compressing portion forming a compression chamber, and compressing a sucked refrigerant sucked in by the compression chamber from a suction pressure to a discharge pressure, and a refrigerant injecting portion injecting an injection refrigerant into an intermediate pressure portion where the sucked refrigerant has an intermediate pressure, which is higher than the suction pressure and lower than the discharge pressure, in the compression chamber formed by the compressing portion, the refrigerant injecting portion comprising a refrigerant injection port through which the injection refrigerant flows from outside and an on-off valve chamber connected to the refrigerant inlet port and the intermediate pressure portion of the compression chamber, formed with communicating with the refrigerant inlet port and with the port to the compression chamber, and including an on-off valve opening and closing the connection port to the refrigerant inlet port, wherein the on-off valve is placed movably along a predetermined moving direction in the on-off valve chamber.
  • the not fully compressed refrigerant in the compression chamber also flows out to a condenser side in the injection circuit when the pressure of the compression chamber becomes transiently higher than the pressure of an immediate refrigerant having just flown out from the condenser.
  • a heat pump apparatus includes the features of Claim 12.
  • An injectable compressor according to this invention includes the features of Claim 1.
  • a method of producing an injectable scroll compressor according to this invention includes the features of Claim 13.
  • a heat pump apparatus opens and closes a flow channel between an injection pipe and a compression chamber according to the opening of a second expansion valve. This can prevent not fully compressed refrigerant in a compression chamber from flowing out to an injection circuit side when an injection operation is not performed or the like.
  • a term "injection" is defined as to return a liquid refrigerant, a two-phase refrigerant, or a gas refrigerant (of high pressure) discharged from a condenser back to a compression chamber of a compressor to be compressed again.
  • a liquid refrigerant, a two-phase refrigerant, or a gas refrigerant (of high pressure) passed through a condenser is called an injection refrigerant.
  • the refrigerant passed through a condenser may not necessarily be an immediate refrigerant having just passed through a condenser.
  • the refrigerant may be one having just passed a predetermined expansion valve, a predetermined heat exchanger or the like.
  • the condenser may be read as a radiator, a heat exchanger to heat the load side, or a gas cooler.
  • Fig. 1 shows a vertical cross section of a scroll compressor 100 according to a first embodiment.
  • the scroll compressor 100 is an injectable compressor equipped with an injection mechanism, as described later.
  • FIG. 2 to Fig. 4 show enlarged views of the same upper portion of the scroll compressor 100 shown in Fig. 1 .
  • Fig. 2 mainly illustrates a fixed scroll 1
  • Fig. 3 mainly illustrates an orbiting scroll 2
  • Fig. 4 mainly illustrates a compliant frame 3 and a guide frame 4.
  • Broken lines in Fig. 1 to Fig. 4 indicate components that usually cannot be seen.
  • the scroll compressor 100 is formed to include the fixed scroll 1, the orbiting scroll 2, the compliant frame 3, the guide frame 4, an electric motor 5, a sub frame 6, a main shaft 7, and an Oldham mechanism 8, all of which are stored in a hermetically sealed container 10. It is to be noted that the fixed scroll 1 and the orbiting scroll 2 are generically called a compressing portion.
  • the fixed scroll 1 is now described with reference to Fig. 1 and Fig. 2 .
  • the outer surface of the fixed scroll 1 is fixed to the guide frame 4 by bolts to be secured.
  • the Oldham guide grooves 1c are engaged with nails 8b of the Oldham mechanism 8 in such a manner as to enable the nails to slide backwards and forwards.
  • a discharge port 1d is formed through the base plate 1a substantially at a central portion thereof.
  • a refrigerant inlet chamber 1e is formed inside the base plate 1a from a side portion thereof to allow an injection refrigerant to flow in from an injection circuit outside the hermetically concealed container 10 via an injection pipe 41 (a refrigerant inlet port).
  • the injection pipe 41 is mounted at the side portion of the base plate 1a through the hermetically sealed container 10.
  • each of the on-off valve chambers 1f has connection ports on the bottom surface: one is connected to an inlet chamber communication channel 1g (an inlet chamber communication hole, or a first communication hole) communicating with the refrigerant inlet chamber 1e, and the other is connected to a compression chamber communication channel 1h (a compression chamber communication hole, or a second communication hole) communicating with the compression chamber 20.
  • an on-off valve 30 (a check valve) is stored inside each on-off valve chamber 1f.
  • the on-off valve 30 and the backplate 31 will be described later in detail.
  • a mechanism for injecting the injection refrigerant into the compression chamber including such as the refrigerant inlet chamber 1e, the inlet chamber communication channel 1g, the on-off valve chamber 1f, the compression chamber communication channel 1h, the on-off valve 30, and the backplate 31, is called a refrigerant injecting portion.
  • the Oldham guide grooves 2e each have a substantially 90 degree phase difference from one of the Oldham guide grooves 1c of the fixed scroll 1.
  • Each Oldham guide groove 2e is engaged with a nail 8a of the Oldham mechanism 8 in such a manner as to enable the nail to slide backwards and forwards.
  • a cylindrical hollow is formed as a boss portion 2f having an orbiting shaft bearing 2c inside.
  • the orbiting shaft bearing 2c is engaged with an orbiting shaft portion 7b provided at an upper end of the main shaft 7. It is to be noted that a gap between the orbiting shaft bearing 2c and the orbiting shaft portion 7b is called a boss gap 15a.
  • a thrust surface 2d is formed slidably under pressure against a thrust bearing 3a of the compliant frame 3.
  • a gap between the thrust surface 2d of the orbiting scroll 2 and the compliance frame 3 on the outer diameter side of the boss portion 2f is called a boss peripheral gap 15b.
  • a gap between the base plate 2a of the orbiting scroll 2 and the compliant fame 3 on the outer diameter side of the thrust bearing 3a is called a base plate peripheral gap 15c.
  • the base plate peripheral gap 15c is a low pressure space under suction gas environmental pressure (suction pressure).
  • the base plate 2a also has a bleed hole 2j, which is formed through the base plate from the surface of the fixed scroll 1 side (the upper side in Fig. 3 ) to the surface of the compliant frame 3 side (the lower side in Fig. 3 ).
  • the bleed hole 2j is provided on the base plate 2a to allow a space on the side of the compression chamber 20 to be communicated with a space on the side of the thrust surface 2d.
  • the bleed hole 2j is arranged so that the circle trajectory of an opening of the bleed hole 2j on the compliant frame 3 side (a lower opening 2k) during normal operation always stays within the thrust bearing 3a of the compliant frame 3. This arrangement prevents leakage of refrigerant from the bleeding hole 2j to the boss peripheral gap 15b or the base plate peripheral gap 15c.
  • the compliant frame 3 and the guide frame 4 are now described with reference to Fig. 1 and Fig. 4 .
  • the compliant frame 3 is supported by cylindrical surfaces 4a and 4b formed on the inner peripheral surface of the guide frame 4, in the radial direction at two surfaces formed on the outer peripheral surface, upper and lower cylindrical surfaces 3d and 3e.
  • a main shaft bearing 3c and an auxiliary main shaft bearing 3h are formed to support in the radial direction, the main shaft 7 driven by the electric motor 5 for rotation.
  • a gap between the guide frame 4 and the compliant frame 3, which is separated by ring-shaped seal materials 16a and 16b at upper and lower portions, is called a frame gap 15d.
  • the compliant frame 3 is also formed with a communication hole 3s at a position facing the lower opening 2k of the bleeding hole 2j.
  • the communication hole 3s is formed through the compliant frame 3, extending from the thrust bearing 3a side to the frame gap 15d side to allow the bleeding hole 2j to communicate with the frame gap 15d constantly or intermittently.
  • the compliant frame 3 also has an adjustment valve space 3p in which a valve 3t, a valve holder 3y, and an intermediate pressure adjustment spring 3m are stored for adjusting the pressure of the boss peripheral gap 15b.
  • the intermediate pressure adjustment spring 3m is made shorter than its original length when stored in the adjustment valve space 3p. It is to be noted that a gap between the compliant frame 3 and the guide frame 4 on the outer diameter side of the valve 3t is called a valve peripheral gap 15e.
  • the compliant frame 3 also has a reciprocating sliding portion 3x formed on the outer diameter side of the thrust bearing 3a.
  • the reciprocating sliding portion 3x allows an Oldham mechanism annular portion 8c to move slidably backwards and forwards.
  • the reciprocating sliding portion 3x has a communication hole 3n that allows the valve peripheral gap 15e to communicate with the base plate peripheral gap 15c.
  • the guide frame 4 is fixed to the hermetically sealed container 10 by shrink fitting or welding on the outer peripheral surface. However, the guide frame 4 has cuts formed on its outer peripheral surface, so there is a flow channel secured for allowing the refrigerant discharged from the discharge port 1d to flow to the discharge pipe 43.
  • the upper fitting cylindrical surface 4a is formed on the inner peripheral surface of the guide frame 4 on the fixed scroll 1 side (the upper side in Fig. 4 ).
  • the upper fitting cylindrical surface 4a is engaged with the upper fitting cylindrical surface 3d formed on the outer peripheral surface of the compliant frame 3.
  • the lower fitting cylindrical surface 4b is formed on the inner peripheral surface of the guide frame 4 on the electric motor 5 side (the lower side in Fig. 4 ).
  • the lower fitting cylindrical surface 4b is engaged with the lower fitting cylindrical surface 3e formed on the outer peripheral surface of the compliant frame 3.
  • the main shaft 7 is now described with reference to Fig. 1 .
  • the orbiting shaft portion 7b On the orbiting scroll 2 side of the main shaft 7 (the upper side in Fig. 1 ), the orbiting shaft portion 7b is formed so that it is rotatably attached to the orbiting shaft bearing 2c of the orbiting scroll 2. On a lower side of the orbiting shaft portion 7b, a main shaft portion 7c is formed so that it is rotatably attached to the main shaft bearing 3c and the auxiliary main shaft bearing 3h of the compliant frame 3.
  • a sub shaft portion 7d is formed so that it is rotatably attached to a sub shaft bearing 6a of the sub frame 6.
  • a rotor 5a of the electric motor 5 is shrink fitted.
  • the rotor 5a is surrounded by a stator 5b.
  • a high-pressure oil feed hole 7g is formed in the axial direction through the main shaft 7.
  • an oil pipe 7f communicating with the high-pressure oil feed hole 7g is press fitted.
  • a low pressure sucked refrigerant enters, via a suction pipe 42, the compression chamber 20 formed by the spiral teeth 1b of the fixed scroll 1 and the spiral teeth 2b of the orbiting scroll 2.
  • the injection refrigerant flowing in via the injection pipe 41 from outside is also injected into the compression chamber 20 through the refrigerant inlet chamber 1e, the inlet chamber communication channel 1g, the on-off valve chamber 1f, and the compression chamber communication channel 1h. If an injection operation is not performed, the injection refrigerant is not injected into the compression chamber 20.
  • the main shaft 7 is driven by the electric motor 5 to operate the orbiting scroll 2.
  • the orbiting scroll 2 does not rotate itself but orbits (eccentric circling movement) by the Oldham mechanism 8, and performs a compression operation to increasingly reduce the volume of the compression chamber 20.
  • This compression operation allows the sucked refrigerant to have high pressure.
  • the high pressure sucked refrigerant is then discharged into the hermetically sealed container 10 through the discharge port 1d of the fixed scroll 1.
  • the discharged refrigerant is discharged outside the hermetically sealed container 10 through the discharge pipe 43. Therefore, the internal pressure of the hermetically sealed container 10 is increased.
  • the internal pressure of the hermetically sealed container 10 is increased during steady operation.
  • This high pressure causes refrigerant oil 11 accumulated at the bottom of the hermetically sealed container 10 to flow towards the orbiting scroll 2 side (the upper side in Fig. 1 ) through the oil pipe 7f and the high pressure oil feed hole 7g.
  • the high pressure refrigerant oil then flows through the boss gap 15a where the pressure of the refrigerant oil is reduced to an intermediate pressure Pm 1, which is higher than suction pressure and the same or lower than discharge pressure, into the boss peripheral gap 15b.
  • the high pressure oil flowing through the high-pressure oil feed hole 7g is led to the gap between the main shaft bearing 3c and the main shaft portion 7c from a horizontal hole provided on the main shaft 7.
  • the pressure of the refrigerant oil between the main shaft bearing 3c and the main shaft portion 7c is reduced to the intermediate pressure Pm 1, which is higher than the suction pressure and the same or lower than the discharge pressure. Then, the refrigerant oil flows in the boss peripheral gap 15b.
  • the refrigerant oil having the intermediate pressure Pm 1 in the boss peripheral gap 15b generally becomes two-phase of gas refrigerant and refrigerant oil by the foaming of refrigerant dissolved in the refrigerant oil.
  • the refrigerant oil having the intermediate pressure Pm 1 in the boss peripheral gap 15b flows to the valve peripheral gap 15e through the adjustment valve space 3p.
  • the refrigerant oil in the valve peripheral gap 15e is discharged to the inner side of the Oldham mechanism annular portion 8c through the communication hole 3n. More specifically, the refrigerant oil, when passing through the adjustment valve space 3p, pushes up the intermediate pressure adjustment valve 3t against additional pressure applied by the intermediate pressure adjustment spring 3m, and then flows into the valve peripheral gap 15e.
  • the refrigerant oil having the intermediate pressure Pm 1 in the boss peripheral gap 15b is fed to the thrust surface 2d of the orbiting scroll 2 and the sliding portion of the thrust bearing 3a of the compliant frame 3, and then discharged to the inner side of the Oldham mechanism annular portion 8c.
  • the refrigerant oil discharged to the inner side of the Oldham mechanism annular portion 8c is fed to the sliding surface of the Oldham mechanism annular portion 8c and also to the surfaces where the nail 8a and a nail 8b of the Oldham mechanism 8 slide, and then released to the base plate peripheral gap 15c.
  • the lower opening 2k of the bleeding hole 2j communicates constantly or intermittently with an opening provided on the thrust bearing 3a side (an upper opening 3u shown in Fig. 4 ) of the communication hole 3s on the compliant frame 3.
  • This refrigerant gas since it has not been fully compressed, has an intermediate pressure Pm 2, which is higher than the suction pressure and the same or lower than the discharge pressure.
  • a total force (A+B) of force (A) caused by the intermediate pressure Pm 1 of the boss peripheral gap 15b and force (B) caused by pressure from the orbiting scroll 2 via the thrust bearing 3a acts on the compliant frame 3 as a downward force.
  • the total force (C+D) of force (C) caused by the intermediate pressure Pm 2 of the frame gap 15d and force (D) caused by a high pressure acting on a portion exposed to the high-pressure environment on a lower end surface also acts on the compliant frame 3 as an upward force.
  • the upward force (C+D) is set to be larger than the downward force (A+B) during normal operation.
  • the compliant frame 3 is lifted upwards towards the fixed scroll 1 side (the upper side in Fig. 1 ) since the upward force (C+D) is thus set to be larger than the downward force (A+B). More specifically, the compliant frame 3 is thus lifted towards the fixed scroll 1 (the upper side in Fig. 1 ) when the upper fitting cylindrical surface 3d is guided by the upper fitting cylindrical surface 4a of the guide frame 4, and the lower fitting cylindrical surface 3e is guided by the lower fitting cylindrical surface 4b of the guide frame 4. More specifically, the compliant frame 3 is thus lifted towards the fixed scroll 1 (the upper side in Fig. 1 ), and thereby pressed against the orbiting scroll 2 via the thrust bearing 3a.
  • the orbiting scroll 2 is also lifted towards the fixed scroll 1 side (the upper side in Fig. 1 ) like the compliant frame 3, since the compliant frame 3 is pressed against the orbiting scroll 2.
  • the tips of the spiral teeth 2b of the orbiting scroll 2 come in contact with the base of teeth (the base plate 1a) of the fixed scroll 1
  • the tips of the spiral teeth 1b of the fixed scroll 1 come in contact with the base of teeth (the base plate 2a) of the orbiting scroll 2.
  • Fig. 5 shows an example of a circuit configuration of a heat pump apparatus equipped with an injection circuit.
  • Fig. 6 is a Mollier diagram illustrating a state of a refrigerant in the heat pump apparatus shown in Fig. 5 .
  • the horizontal axis indicates specific enthalpy and the vertical axis indicates refrigerant pressure.
  • a four-way valve 58 is set so that a refrigerant flows in a course indicated by solid lines. It is to be noted that the heating operation here includes air heating for air conditioning and water heating for heating water to produce hot water.
  • the high-temperature high-pressure gas refrigerant (point 1 in Fig. 6 ) at a compressor 51 is discharged through a discharge pipe 43 of the compressor 51.
  • the high-temperature high-pressure gas refrigerant then enters a heat exchanger 52, as a condenser or a radiator, where heat is exchanged, and liquefies (point 2 in Fig. 6 ).
  • heat absorbed from the refrigerant heats air or water to be used for air conditioning or water heating.
  • the liquid refrigerant from the heat exchanger 52 passes through a first expansion valve 53 (a pressure reducing mechanism) where pressure is reduced to an intermediate pressure, and thereby turns into two-phase gas-liquid (point 3 in Fig. 6 ).
  • the two-phase gas-liquid refrigerant from the first expansion valve 53 enters a receiver 59 where heat is exchanged with a refrigerant to be sucked in by the compressor 51, and is thereby cooled and liquefied (point 4 in Fig. 6 ).
  • the flow of the liquid refrigerant from the receiver 59 is divided into a flow (mainstream) to the side including an inner heat exchanger 54 and a third expansion valve 55 and another flow (branch stream or injection circuit) to the side including a second expansion valve 56.
  • the liquid refrigerant in the mainstream passes through the inner heat exchanger 54 where heat is exchanged with the two-phase gas-liquid refrigerant in the branch stream as a result of pressure reduction through the second expansion valve 56, and is thereby further cooled (point 5 in Fig. 6 ).
  • the liquid refrigerant as a result of cooling by the inner heat exchanger 54 passes through the third expansion valve 55 (a pressure reducing mechanism) where pressure is reduced, and thereby turns into two-phase gas-liquid (point 6 in Fig. 6 ).
  • the two-phase gas-liquid refrigerant from the third expansion valve 55 enters a heat exchanger 57 as an evaporator, where heat is exchanged, and is thereby heated (point 7 in Fig. 6 ).
  • the heated refrigerant from the heat exchanger 57 then passes through the receiver 59 to further absorb heat (point 8 in Fig. 6 ), and is then sucked in by the compressor 51 through the suction pipe 42.
  • the refrigerant flowing in the branch stream passes through the second expansion valve 56 (a pressure reducing mechanism) where pressure is reduced (point 9 in Fig. 6 ), and then enters the inner heat exchanger 54 where heat is exchanged (point 10 in Fig. 6 ), as described earlier.
  • the two-phase gas-liquid refrigerant (an injection refrigerant) as a result of heat exchange at the inner heat exchanger 54 flows as two-phase gas-liquid in the refrigeration inlet chamber 1e of the fixed scroll 1 via the injection pipe 41 of the compressor 51.
  • the mainstream refrigerant sucked in through the suction pipe 42 (point 8 in Fig. 6 ) is compressed up to the intermediate pressure and thereby heated (point 11 in Fig. 6 ).
  • the compressed and heated refrigerant having the intermediate pressure joins the injection refrigerant (point 8 in Fig. 6 ) to reduce the temperature (point 12 in Fig. 6 ).
  • the cooled refrigerant (point 12 in Fig. 6 ) is then further compressed and heated to increase its temperature and pressure (point 1 in Fig. 6 ), and then discharged (point 1 in Fig. 6 ).
  • a compressing operation performed in the compressor 51 will be described further in detail later.
  • the opening of the second expansion valve 56 is closed when the injection operation is not performed. More specifically, during injection operation, the opening of the second expansion valve 56 is increased from a predetermined opening. When the injection operation is not performed, the opening of the second expansion valve 56 is reduced from the predetermined opening. This prevents the injection refrigerant from flowing into the refrigerant inlet chamber 1e of the compressor 51. In other words, all the amount of refrigerant passing through the heat exchanger 52, the first expansion valve 53, and the receiver 59 is sucked in by the compressor 51 via the suction pipe 42.
  • the opening of the second expansion valve 56 may be electronically controlled, for example.
  • the four-way valve 58 is set so that a refrigerant flows in a course indicated by broken lines during cooling operation.
  • the high-temperature high-pressure gas refrigerant (point 1 in Fig. 6 ) from the compressor 51 (the scroll compressor 100) is discharged through the discharge pipe 43 of the compressor 51.
  • the high-temperature high-pressure gas refrigerant then enters the heat exchanger 57 as a condenser, where heat is exchanged, and liquefies (point 2 in Fig. 6 ).
  • the liquid refrigerant from the heat exchanger 57 then passes through the third expansion valve 55 where pressure is reduced to the intermediate pressure, and thereby turns into two-phase gas-liquid (point 3 in Fig. 6 ).
  • the two-phase gas-liquid refrigerant from the third expansion valve 55 then enters the inner heat exchanger 54 where heat is exchanged, and is thereby cooled and liquefied (point 4 in Fig. 6 ).
  • heat is exchanged between the two-phase gas-liquid refrigerant from the third expansion valve 55 and the two-phase gas-liquid refrigerant from the second expansion valve 56 (point 9 in Fig. 6 ) where the pressure of the liquid refrigerant from the inner heat exchanger 54 is reduced.
  • the flow of the liquid refrigerant through the inner heat exchanger 54 (point 4 in Fig. 6 ) is divided into the receiver 59 side (the mainstream) and the inner heat exchanger 54 side (the branch stream, or the injection circuit).
  • the mainstream liquid refrigerant enters the receiver 59 where heat is exchanged with the refrigerant to be sucked in by the compressor 51, and is thereby further cooled (point 5 in Fig. 6 ).
  • the cooled liquid refrigerant from the receiver 59 passes through the first expansion valve 53 where pressure is reduced, and thereby turns into two-phase gas-liquid (point 6 in Fig. 6 ).
  • the two-phase gas-liquid refrigerant from the first expansion valve 53 enters the heat exchanger 52 as an evaporator where heat is exchanged, and is thereby heated (point 7 in Fig. 6 ).
  • This heat absorption by refrigerant causes air, water, etc. to cool for such as air conditioning, water chilling and icing, and freezing.
  • the heated refrigerant from the heat exchanger 57 enters the receiver 59 to be further heated (point 8 in Fig. 6 ), and then sucked in by the compressor 51 via the suction pipe 42.
  • the refrigerant flowing in the branch stream passes through the second expansion valve 56 where pressure is reduced (point 9 in Fig. 6 ), and enters the inner heat exchanger 54 where heat is exchanged (point 10 in Fig. 6 ), as described earlier.
  • the two-phase gas-liquid refrigerant (the injection refrigerant) from the inner heat exchanger 54 flows as two-phase gas-liquid into the refrigerant inlet chamber 1e of the fixed scroll 1 via the injection pipe 41 of the compressor 51.
  • the compression operation in the compressor 51 is performed in the same manner as that performed during heating operation.
  • the opening of the second expansion valve 56 is closed to stop the injection refrigerant from flowing into the refrigerant inlet chamber 1e of the compressor 51, in the same manner as that performed during heating operation.
  • the injection operation is usually performed during heating operation. Therefore, the injection operation is not usually performed during cooling operation. More specifically, the injection operation is not always performed during heating operation. Heating capacity may be enhanced if the injection operation is performed exclusively when the outside temperature is the same or below a predetermined temperature (e.g., 2 °C) or when the rotation frequency of the compressor is the same or higher than a predetermined frequency (e.g., 60 Hz), for example. This can result in achieving a heat pump apparatus having an efficient performance in heating air and water. When the injection operation is not necessary, the injection operation is not performed, even during heating operation, by closing the second expansion valve 56.
  • a predetermined temperature e.g. 2 °C
  • a predetermined frequency e.g. 60 Hz
  • the above standard may not necessarily be used to decide whether to carry out the injection operation.
  • the injection operation may be performed during cooling operation, for example.
  • the heat exchanger 52 may be of a type that exchanges heat between a high-temperature high-pressure gas refrigerant or a low-temperature low-pressure liquid refrigerant and liquid such as water.
  • a heat exchanger that exchanges heat between a high-temperature high-pressure gas refrigerant or a low-temperature low-pressure liquid refrigerant and a gas such as air may be employed instead.
  • the heat pump apparatus illustrated in Fig. 5 and Fig. 6 may alternatively be an air conditioner, a water heater, a freezer, or a refrigerator.
  • Fig. 7 shows relative positions of an orbiting scroll 2 with respect to a fixed scroll 1 at every 90 degrees when suction is completed at 0 degree.
  • the spiral teeth 1b of the fixed scroll 1 and the spiral teeth 2b of the orbiting scroll 2 are engaged with each other to form a pair of compression chambers 20a and 20b.
  • the compression chambers 20a and 20b are generically called the compression chamber 20.
  • the compression chamber 20 moves towards the center while gradually reducing its volume as the orbiting scroll 2 orbits according to the rotation of the main shaft 7. More specifically, a refrigerant sucked in by the compression chamber 20 is gradually compressed to increase its pressure, and moves towards the center as the orbiting scroll 2 orbiting according to the rotation of the main shaft 7. Then, when the compression chamber 20 communicates with the discharge port 1d at a central portion, the compressed refrigerant is discharged into the hermetically sealed container 10 through the discharge port 1d.
  • the suction of the refrigerant is completed, as earlier mentioned. More specifically, at 0 degree, the refrigerant has been sucked in by the compression chamber 20 through the suction pipe 42, and the compression chamber 20 is hermetically sealed.
  • the main shaft 7 rotates 90 degrees from 0 degree (a refrigerant suction completion point)
  • the volume of the compression chamber 20 is slightly reduced, and the compression chamber 20 has moved slightly towards the central portion.
  • the compression chamber 20 communicates with the compression chamber communication channel 1h. This allows the injection refrigerant to flow in the compression chamber communication channel 1h while the injection operation is performed.
  • the injection refrigerant is injected to an intermediate pressure portion where the sucked refrigerant sucked in by the compression chamber 20 through the suction pipe 42 has an intermediate pressure, which is higher than the suction pressure (low pressure) at the point when the refrigerant is sucked, and lower than the discharge pressure (high pressure) at the point when the refrigerant is discharged through the discharge port 1d.
  • the main shaft 7 rotates 180 degrees, 270 degrees and 360 degrees from the refrigerant suction completion point.
  • the compression chamber 20 communicates with the compression chamber communication channel 1h. Therefore, during the rotation while the injection refrigerant continues to flow in the compression chamber 20 through the compression chamber communication channel 1h, the refrigerant in the compressing chamber 20 is increasingly compressed and moves gradually towards the central portion.
  • the compression chamber 20 terminates the communication with the compression communication channel 1h. Thereafter, the refrigerant in the compression chamber 20 is continued to be compressed with no additional refrigerant flowing in from outside, until the compression chamber 20 communicates with the discharge port 1d.
  • the compression chamber 20 communicates with the discharge port 1d, and then compressed refrigerant is discharged into the hermetically sealed container 10 through the discharge port 1d.
  • the refrigerant When the main shaft 7 rotates 360 degrees from the refrigeration suction completion point, the refrigerant has been sucked in by the outermost compression chamber 20. When the main shaft 7 rotates 450 degrees from the refrigeration suction completion point, the outermost compression chamber 20 begins to communicate with the compression chamber communication channel 1h. In such a manner, the refrigerant is compressed repeatedly in the scroll compressor 100.
  • the compression chambers 20a and 20b are arranged so that each of the compression chambers communicates with one of the compression chamber communication channels 1h communicating with the respective on-off valve chambers 1f. More specifically, the base plate 1a of the fixed scroll 1 is formed with the two on-off valve chambers 1f, as mentioned above.
  • the compression chamber 20a is arranged to communicate with one of the two on-off valve chambers 1f, and the compression chamber 20b is arranged to communicate with the other on-off valve chamber 1f.
  • Fig. 8 is an exploded perspective view illustrating a configuration of the on-off valve chamber 1f. Referring to Fig. 8 , broken lines indicate components that are usually invisible.
  • the two on-off valve chambers 1f are formed by covering two cylindrical recesses, which are formed on the opposite side to the side where spiral teeth 1b of the base plate 1a are formed in the fixed scroll 1, with the backplate 31, and fastening the backplate 31 with bolts 34 to seal the recesses.
  • one piece of the backplate 31 is used to cover both the openings of the two recesses.
  • a separate piece of the backplate 31 may be used to cover each recess.
  • a connection port to the inlet chamber communication channel 1g and a connection port to the compression chamber communication channel 1h are formed on the bottom surface of each recess.
  • the inlet chamber communication channel 1g communicates with the refrigerant inlet chamber 1e formed by extending inwards from a side portion of the base plate 1a.
  • the compression chamber communication channel 1h communicates with a surface on the spiral teeth 1b side. More specifically, the compression chamber communication channel 1h communicates with the compression chamber 20.
  • a connection port to the refrigerant inlet chamber 1e and a connection port to the compression chamber 20 are formed on the bottom surface of each recess.
  • Each of the on-off valve chambers 1f is provided with the on-off valve 30 that is formed like a circular plate whose diameter is almost the same or slightly smaller than the bore diameter of the recess.
  • the on-off valve 30 is formed with a passage hole 30a and a guide hole 30b.
  • the on-off valve 30 is placed so that the passage hole 30a overlaps with the connection port of the compression chamber communication channel 1h.
  • the on-off valve 30 is placed in the on-off valve chamber 1f with a guide projection 31a (a guide rod), which is formed on the backplate 31, inserted through the guide hole 30b.
  • the guide projection 31a is a projection extending like a stick perpendicularly (an up-down direction in Fig. 1 , a vertical direction) to the surface where the inlet chamber communication channel 1g and the compression chamber communication channel 1h are formed.
  • the guide hole 30b is formed like a keyhole, and the guide projection 31a is formed like a key in a corresponding manner. Therefore, the on-off valve 30 is allowed to move in the vertical direction to the direction of the surface of the fixed base plate (the up-down direction in Fig. 1 ) in the on-off valve chamber 1f. However, the on-off valve 30 is not allowed to rotate around the guide projection 31a since the guide hole 30b and the guide projection 31a are engaged with each other. This prevents the passage hole 30a, which is arranged to communicate with the compression chamber communication channel 1h, from moving.
  • the on-off valve 30 may be shaped in a circle whose diameter is almost the same as the bore diameter of the recess, or the guide hole 30b may be formed substantially the same in size and shape as the circumference and outer periphery of the guide projection 31a. In this case, the on-off valve 30 is prevented from moving in a horizontal direction. If the on-off valve 30 is shaped in a circle whose diameter is almost the same as the bore diameter of the recess, however, burr may be caused if the outer surface of the on-off valve 30 and the inner wall of the recess rub against each other.
  • the on-off valve 30 is shaped in a circle whose diameter is slightly smaller than the bore diameter of the recess, and also the guide hole 30b is formed substantially the same in size and shape as the circumference and outer periphery of the guide projection 31a.
  • the guide holes 30b and the guide projections 31a are intentionally designed in shape not to allow the on-off valve 30 to rotate.
  • the recesses may be formed into a shape of a prism and the on-off valves 30 may be formed into a polygonal shape to prevent the on-off valves 30 from rotating.
  • Fig. 9 shows a vicinity of one of the on-off valve chambers 1f when the injecting operation is performed.
  • the two-phase gas-liquid injection refrigerant flows in the refrigerant inlet chamber 1e, which is formed inside the base plate 1a of the fixed scroll 1, through the injection pipe 41.
  • the injection refrigerant in the refrigerant inlet chamber 1e flows in the two inlet chamber communication channels 1g.
  • the pressure of the injection refrigerant in the refrigerant inlet chamber 1e is higher than the pressure of the refrigerant in the compression chamber 20 (especially at the position where the compression chamber 20 communicates with the compression chamber communication channel 1h, i.e., the intermediate pressure portion).
  • the injection refrigerant in the inlet chamber communication channel 1g flows in the on-off valve chamber 1f.
  • the compression chamber 20 communicates with the compression chamber communication channel 1h the injection refrigerant of the on-off chamber 1f flows into the compression chamber 20 through the compression chamber communication channel 1h.
  • Fig. 10 shows a vicinity of one of the on-off valve chambers 1f when the injecting operation is not performed.
  • the second expansion valve 56 in the heat pump apparatus is closed when the injection operation is not performed. Therefore, the injection refrigerant does not enter the refrigerant inlet chamber 1e.
  • the internal pressure of the compression chamber 20 (especially in the position where the compression chamber 20 communicates with the compression chamber communication channel, i.e., the intermediate pressure portion) is higher than the pressure of the refrigerant between the refrigerant inlet chamber 1e and the on-off valve chamber 1f. This causes the refrigerant in the compression chamber 20 to flow back to the on-off valve chamber 1f via the compression chamber communication channel 1h when the compression chamber 20 communicates with the compression chamber communication channel 1h.
  • the refrigerant flows in the on-off valve chamber 1f through the passage hole 30a on the on-off valve 30.
  • the internal pressure of the compression chamber 20 is higher than the internal pressure of the refrigerant inlet chamber 1e. Therefore, the refrigerant entering the on-off valve chamber 1f from the compression chamber 20 presses the on-off valve 30 against the inlet chamber communication channel 1g (the lower side in Fig. 10 ). This causes the on-off valve 30 to block the inlet chamber communication channel 1g. Accordingly, the refrigerant in the on-off valve chamber 1f is not allowed to flow out to the refrigerant inlet chamber 1e through the inlet chamber communication channel 1g.
  • the on-off valve 30 is pushed towards the backplate 31 side, and therefore the on-off valve 30 opens. Consequently, the injection refrigerant flows in the on-off valve chamber 1f through the inlet chamber communication channel 1g, and then flows in the compression chamber 20 through the compression chamber communication channel 1h.
  • the on-off valve 30 is pressed against the inlet chamber communication channel side 1g, and therefore the on-off valve 30 closes. As a result, the refrigerant flowing back from the compression chamber 20 into the on-off valve chamber 1f is not allowed to flow in the refrigerant inlet chamber 1e through the inlet chamber communication channel 1g.
  • the on-off valve 30 opens and closes according to a difference in pressure between the refrigerant on the refrigerant inlet chamber 1e side (the inlet chamber communication channel 1g) and the refrigerant in the compression chamber 20 (the compression chamber communication channel 1h).
  • the on-off valve 30 If the on-off valve 30 is not provided, the refrigerant in the compression chamber 20 flows back to the injection circuit. As a result, a volume between the compression chamber communication channel 1h and the second expansion valve 56 becomes dead volume in compression, which causes a considerable reduction in efficiency. That is to say that the use of the on-off valve 30 contributes largely to a reduction in the dead volume, improving compression efficiency.
  • the pressure of the refrigerant in the compression chamber 20 may transiently become higher than the pressure of the refrigerant in the refrigerant inlet chamber 1e even during injection operation. Even in such a case, the refrigerant is not allowed to flow out to the injection circuit by the on-off valve 30, like the case when the injection operation is not performed.
  • the internal pressure of the refrigerant inlet chamber 1e is increasingly reduced.
  • the on-off valve 30 pushed up towards the backplate 31 side (the upper side in Figs. 9 and 10 ) is pulled down by gravity towards the inlet chamber communication channel 1g (the lower side in Figs. 9 and 10 ).
  • the on-off valve 30 is pressed towards the inlet chamber communication channel 1g (the lower side in Figs. 9 and 10 ) by the refrigerant flowing into the on-off valve chamber 1f from the compression chamber 20 through the passage hole 30.
  • the on-off valve 30 operates according only to the pressure difference and gravity.
  • the on-off valve 30 operates without spring force of such as coil spring. This contributes to an increase in reliability and a reduction in production cost.
  • connection port to the inlet chamber communication channel 1g and the connection port to the compression chamber communication channel 1h are formed on the bottom surface of the on-off valve chamber 1f. This allows the on-off valve 30 to descend easily towards the inlet chamber communication channel 1g (the lower side in Figs. 9 and 10 ) according to not only pressure differences but also gravity in the transition from the state where the injection operation is being carried out to the state where the injection operation is not performed, as mentioned earlier.
  • the connection port to the inlet chamber communication channel 1g and the connection port to the compression chamber communication channel 1h may also be provided on a side surface or an upper surface of the on-off valve chamber 1f.
  • the on-off valve 30 moves according to a pressure difference alone in a transition to the state where the injection operation is not performed.
  • the movement of the on-off valve 30, however, may further be assisted by the use of coil spring or the like. More specifically, coil spring, or the like is used so that the on-off valve 30 is pressed towards the inlet chamber communication channel 1g when the internal pressure of the compression chamber 20 and the internal pressure of the refrigerant inlet chamber 1e are almost the same. This allow the on-off valve 30 to move towards the inlet chamber communication channel 1g easily in the transition from where the injection operation is being carried out to where the injection operation is not performed.
  • Coil spring or the like is also applicable between the on-off valve 30 and the backplate 31 to assist the descending movement of the on-off valve 30 towards the inlet chamber communication channel 1g (the lower side in Figs. 9 and 10 ) even when the connection port to the inlet chamber communication channel 1g and the connection port to the compression chamber communication channel 1h are formed on the bottom surface of the on-off valve chamber 1f.
  • the inlet chamber communication channel 1g which communicates with the refrigerant inlet chamber 1e
  • the compression chamber communication channel 1h which communicates with the compression chamber 20
  • That surface is therefore allowed to be made flat, and thus the on-off valve 30 is allowed to have a simple structure.
  • the fixed scroll 1, the orbiting scroll 2, and so forth are formed into the shapes described above.
  • machining is used to form the spiral teeth 1b, a hole as the refrigeration inlet chamber 1e, the two recesses, holes as the inlet chamber connection chambers 1g, and holes as compression chamber communication channels 1h on the base plate 1a. Then, the on-off valves 30 are placed in the machined recesses, and the backplate 31 is mounted.
  • the hole as the refrigeration inlet chamber 1e, the two recesses, the holes as the inlet chamber connection chambers 1g, and the holes as compression chamber communication channels 1h may be formed on the base plate 1a of the fixed scroll 1 by machine cutting in a linear fashion.
  • the order of machining of the spiral teeth 1b, the holes as the refrigerant inlet chamber 1e, the two recesses, the holes as the inlet chamber communication channels 1g, and the holes as the compression chamber communication holes 1h does not matter.
  • the sub frame 6, the electric motor 5, the main shaft 7, the guide frame 4, the compliant frame 3, and the Oldham mechanism 8 are arranged in the lower container 10a of the hermetically sealed container 10.
  • the orbiting scroll 2 is also arranged so that it engages with the main shaft 7.
  • the fixed scroll 1 is also arranged so that the compression chamber 20 is formed between the orbiting scroll 2 and the fixed scroll 1.
  • the injection pipe 41 is mounted on the lower container 10a so that the injection pipe 41 is connected to the refrigerant inlet chamber 1e.
  • the suction pipe 42 is mounted on the lower container 10a so that the suction pipe 42 is connected to the suction opening of the compression chamber 20.
  • the discharge pipe 43 is mounted on the lower container 10a.
  • the upper container 10b is also mounted on the lower container 10a to seal the container.
  • the scroll compressor 100 is thus produced.
  • the scroll compressor 100 can thus prevent not fully compressed refrigerant from flowing back to the injection circuit, and also prevent the dead volume from increasing in the compression process.
  • connection ports that connect the inlet chamber communication channel 1g and the compression chamber communication channel 1h to the on-off valve chamber 1f are thus formed on the same surface of the on-off valve chamber 1f.
  • the on-off valve 30 thus opens and closes according to the difference in pressure between the inlet chamber communication channel 1g side and the compressor chamber communication channel 1h side. This can thus allow the on-off valve 30 to move and open/close smoothly, thereby improving reliability. This can also make the on-off valve chamber 1f compact.
  • the scroll compressor 100 can thus control the opening and closing according to the pressure difference between the internal pressure of the compression chamber 20 and the pressure of the refrigerant inlet chamber 1e without using coil spring. This can contribute to a reduction in the number of components required, compared to an on-off valve using coil spring.
  • the scroll compressor 100 the refrigerant inlet chamber 1e, the two recesses, the inlet chamber communication channels 1g, and the compression chamber communication channels 1h are formed simply in a linear arrangement with respect to the base plate 1g of the fixed scroll 1.
  • the on-off valve chambers 1f are formed to include the on-off valves 30 placed therein, and covered with the backplate 31 as a lid.
  • all that is needed to form the scroll compressor 100 is to form linear holes and arrange the on-off valves 30 and the backplate 31. Therefore, complicated work such as to cut a groove as a refrigerant channel on the valve seat of an on-off valve is not required. This can result in a reduction in the number of machining processes required.
  • the refrigerant inlet chamber 1e is formed from the side portion towards the inside of the base plate 1a of the fixed scroll 1. Therefore, the injection pipe 41 is only to be mounted on the side portion of the base plate 1a of the fixed scroll 1. This allows the injection pipe 41 to be mounted on the lower container 10a. In other words, there is no need to mount the injection pipe 41 on the upper container 10b. Therefore, it is very easy to fix the upper container 10b to the lower container 10a.
  • the injection pipe 41 can be mounted on the side portion of the hermetically sealed container 10 since the injection pipe 41 only needs to be mounted on the side portion of the base plate 1a of the fixed scroll 1. This allows pipes to be connected to the injection pipe 41 to be installed on a side portion of the hermetically sealed container 10. The pipes do not need to be installed above the hermetically sealed container 10. If a heat pump apparatus equipped with a compressor is reduced in size, an outdoor unit would not generally allow extra space above and below the hermetically sealed container 10.
  • the scroll compressor 100 is, however, space saving with respect to space above the hermetically sealed container 10, compared to a compressor requiring pipes connected to the injection pie 41 above the hermetically sealed container 10. The scroll compressor 100 can thus allow a heat pump apparatus to be reduced effectively in size.
  • the scroll compressor 100 described in a second embodiment employs on-off valves 32 made from plate springs.
  • Fig. 11 is a vertical cross section of the scroll compressor 100 according to the second embodiment.
  • the scroll compressor 100 shown in Fig. 11 of the second embodiment modifies the scroll compressor 100 shown in Fig. 1 of the first embodiment by replacing the on-off valve by one having a different configuration.
  • the scroll compressor 100 of the second embodiment employs the on-off valves 32 made from plate springs as mentioned above.
  • the on-off valves 32 are placed to cover the openings of the inlet chamber communication channels 1g.
  • the on-off valves 32 are pushed up towards a backplate 33 and bent. Then, the injection refrigerant flows in the on-off valve chamber 1f through the inlet chamber communication channel 1g, and then flows into the compression chamber 20 through the compression chamber communication channel 1h.
  • the on-off valve 32 When the pressure on the refrigerant inlet chamber 1e side is lower than the internal pressure of the compression chamber 20 such as when the injection operation is not performed, the on-off valve 32 is pressed against the inlet chamber communication channel 1g side. This prevents the refrigerant returning from the compression chamber 20 into the on-off valve chamber 1f from flowing out to the refrigerant inlet chamber 1e through the inlet chamber communication channels 1g.
  • the backplate 33 does not need to have a guide projection such as the guide projection 31a of the back plate 31 described in the first embodiment if the on-off valves 32 of plate springs are used. This can allow the back plate 33 to have a simple structure, as shown in Fig. 11 .
  • the scroll compressor 100 equipped with the on-off valves 32 made from plate springs of the second embodiment can also achieve the same effect as that according to the scroll compressor 100 of the first embodiment.
  • the scroll compressor described in the above embodiments is characterized as follows:
  • the fixed scroll and the orbiting scroll are engaged with each other in the hermetically sealed container.
  • the orbiting scroll orbits around the fixed scroll without rotating itself.
  • the refrigerant compressed in the compression chamber is thereby discharged to the discharge space at the back surface of the fixed scroll through the discharge port provided at the central portion of the fixed scroll.
  • the compression chamber is formed with the plate spiral teeth of both the fixed scroll and the orbiting scroll.
  • the scroll compressor allows the refrigerant having the intermediate pressure to be injected into the intermediate portion of the compression process.
  • the intermediate pressure is the pressure between the pressure of the refrigerant flowing into the compression chamber and the pressure of the discharged refrigerant from the compression chamber.
  • the scroll compressor comprises the two on-off valves and the on-off valve chambers storing the two on-off valves in the refrigerant inlet chamber.
  • the refrigerant inlet chamber is formed from the side portion towards the inside of the fixed scroll to allow the refrigerant to flow into the compression chamber through the compression chamber communication channels.
  • the scroll compressor also comprises the back plate to seal the on-off valve chambers.
  • the scroll compressor 100 is used as an example of the injectable compressor.
  • a different type of compressor equipped with an injection mechanism such as a rotary compressor, can be used instead as the injectable compressor.
  • such as the refrigerant inlet chamber 1e and the on-off valve chambers 1f are provided on the base plate 1a of the fixed scroll 1 of the scroll compressor 100, as an example.
  • such as the refrigerant inlet chamber 1e and the on-off valve chambers 1f may be provided separately from the base plate 1a of the fixed scroll 1.

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Claims (13)

  1. Compresseur à injection (100) comprenant :
    une partie de compression formant une chambre de compression (20), et comprimant un réfrigérant aspiré, aspiré par la chambre de compression d'une pression d'aspiration à une pression de décharge, et
    une partie d'injection de réfrigérant injectant un réfrigérant d'injection dans une partie de pression intermédiaire dans laquelle le réfrigérant aspiré a une pression intermédiaire, qui est supérieure à la pression d'aspiration et inférieure à la pression de décharge, dans la chambre de compression formée par la partie de compression,
    la partie d'injection de réfrigérant comprenant :
    une chambre d'entrée de réfrigérant (1e) dans laquelle le réfrigérant d'injection s'écoule depuis l'extérieur ; et
    une chambre de valve de marche / arrêt (1f) raccordée à la chambre d'entrée de réfrigérant (1e) et la partie de pression intermédiaire de la chambre de compression, formée avec un orifice de raccordement à la chambre d'entrée de réfrigérant (1e) et un orifice de raccordement à la chambre de compression, qui sont formés sur une même surface dans la chambre de valve de marche / arrêt (1f),
    et comprenant :
    une valve de marche / arrêt (30, 32) ouvrant et fermant l'orifice de raccordement à la chambre d'entrée de réfrigérant (1e) sur la base d'une différence de pression entre un réfrigérant du côté de la chambre d'entrée de réfrigérant et un réfrigérant du côté de la chambre de compression ;
    dans lequel la valve de marche / arrêt (30, 32) est placée, de manière mobile, le long d'une direction de déplacement prédéterminée dans la chambre de valve de marche / arrêt (1f), et est formée avec un trou (30a) dans une position chevauchant l'orifice de raccordement à la partie à pression intermédiaire lorsque l'orifice de raccordement à la chambre d'entrée de réfrigérant (1e) est fermé.
  2. Compresseur à injection selon la revendication 1, dans lequel la valve de marche / arrêt (30, 32) est un élément de plaque.
  3. Compresseur à injection selon la revendication 2, dans lequel la valve de marche / arrêt (30, 32) est formée avec un trou de guidage (30b) à travers lequel une tige de guidage (31a) s'étend dans la direction de déplacement dans la chambre de valve de marche / arrêt (1f).
  4. Compresseur à injection selon la revendication 3, dans lequel la chambre de valve de marche / arrêt (1f) est formée selon une forme cylindrique avec une surface inférieure où l'orifice de raccordement à la chambre d'entrée de réfrigérant (1e) et l'orifice de raccordement à la partie à pression intermédiaire sont formés, et
    dans lequel la valve de marche marche / arrêt (30, 32) est un élément de plaque circulaire formé avec le trou de guidage, le trou de guidage étant mis en prise avec la tige de guidage pour empêcher la rotation de la valve de marche / arrêt (30, 32) autour de la tige de guidage.
  5. Compresseur à injection selon la revendication 3, dans lequel la chambre de valve de marche / arrêt (1f) est formée selon une forme cylindrique avec une surface inférieure où l'orifice de raccordement à la chambre d'entrée de réfrigérant (1e) et la partie de raccordement à la partie à pression intermédiaire sont formés, et
    dans lequel la valve de marche / arrêt (30, 32) est formée selon la forme d'un cercle dont le diamètre est inférieur à un diamètre de la surface inférieure de la chambre de valve de marche / arrêt (1f),
    la valve de marche / arrêt étant formée avec le trou de guidage qui a une taille sensiblement identique à la circonférence de la tige de guidage et une forme sensiblement identique à une forme périphérique de la tige de guidage.
  6. Compresseur à injection selon la revendication 1, dans lequel la valve de marche / arrêt est un ressort à lames.
  7. Compresseur à injection selon la revendication 1, dans lequel la partie de compression comprend :
    une spirale orbitale (2b) comprenant des dents de spirale orbitale (2b) formées du côté de la surface supérieure d'une plaque de base orbitale (2a) ; et
    une spirale fixe (1) comprenant des dents de spirale fixe (1b) formées du côté de la surface inférieure de la plaque de base fixe (1a), les dents de spirale fixe étant mises en prise avec les dents de spirale orbitale de la spirale orbitale (2) afin de former la chambre de compression,
    dans lequel la chambre d'entrée de réfrigérant (1e) est une chambre formée à l'intérieur de la plaque de base fixe (1a), s'étendant à partir d'une partie latérale de la plaque de base fixe (1a), et
    dans lequel la chambre de valve de marche / arrêt (1f) est une chambre formée du côté de la surface supérieure de la plaque de base fixe (1a).
  8. Compresseur à injection selon la revendication 7, dans lequel la chambre de valve de marche / arrêt (1f) est une chambre formée en recouvrant un évidement formé du côté de la surface supérieure de la plaque de base fixe (1a) avec une plaque arrière (31).
  9. Compresseur à injection selon la revendication 7, dans lequel la partie de compression comprend une paire de dents de spirale orbitale de la spirale orbitale (2) et les dents de spirale fixe de la spirale fixe mises en prise entre elles afin de former une chambre de compression en paire, et
    dans lequel la chambre de valve de marche / arrêt (1f) est prévue pour chaque chambre de compression de la chambre de compression en paire.
  10. Compresseur à injection selon la revendication 4, comprenant en outre :
    un récipient hermétiquement fermé (10) stockant la partie de compression et la partie d'injection de réfrigérant, et
    un tuyau d'injection (41) monté à travers une surface latérale du récipient hermétiquement fermé pour permettre au réfrigérant d'injection de s'écouler dans la chambre d'entrée de réfrigérant (1e) depuis l'extérieur.
  11. Compresseur à injection selon la revendication 10, dans lequel le récipient hermétiquement fermé comprend :
    un récipient inférieur (10a) ; et
    un récipient supérieur (10b) combiné avec un récipient inférieur afin de créer un espace hermétiquement fermé à l'intérieur du récipient hermétiquement fermé,
    dans lequel le tuyau d'injection est monté à travers une surface latérale du récipient inférieur.
  12. Appareil de pompe à chaleur comprenant :
    un circuit de réfrigération principal comprenant le compresseur à injection (100) selon l'une quelconque des revendications 1 à 11, un radiateur (52), une première valve d'expansion (53) et un évaporateur (57) raccordés en série ; et
    un circuit d'injection raccordant une partie entre le radiateur et la première valve d'expansion dans le circuit de réfrigération principal et la partie d'injection de réfrigérant, le circuit d'injection comprenant une seconde valve d'expansion (56).
  13. Procédé pour produire un compresseur à spirales à injection (100), comprenant les étapes consistant à :
    former des dents de spirale orbitale (2b) sur une surface d'un côté d'une plaque de base orbitale (2a) ;
    former des dents de spirale fixe (1b) sur une surface d'un côté de la plaque de base fixe (1a) ;
    former un trou latéral sur une partie latérale de la plaque de base fixe (1a) ;
    former un évidement sur une surface d'un autre côté de la plaque de base fixe (1a) ;
    former, sur la plaque de base fixe (1a), un premier trou de communication (1g) qui raccorde une surface inférieure de l'évidement et le trou latéral, et un second trou de communication (1h) qui raccorde la surface inférieure de l'évidement (1f) et la surface du premier côté de la plaque de base fixe (1a) ;
    placer une valve de marche / arrêt (30, 32) dans l'évidement (1f) formé sur la plaque de base fixe (1a),
    la valve de marche / arrêt ouvrant et fermant le premier trou de communication (1g) ;
    monter une plaque arrière (31) sur la plaque de base fixe (1a) de sorte que la plaque arrière recouvre une ouverture de l'évidement (1f) dans lequel la valve de marche / arrêt (30, 32) est placée ;
    placer dans un récipient hermétiquement fermé, (10), la plaque de base orbitale (2a) formée avec les dents de spirale orbitale ;
    placer dans le récipient hermétiquement fermé la plaque de base fixe (1a) formée avec les dents en spirale fixes de sorte que les dents de spirale fixe sont mises en prise avec les dents de spirale orbitale afin de former une chambre de compression (20) ;
    raccorder un tuyau d'aspiration (42) à une ouverture d'aspiration de la chambre de compression, le tuyau d'aspiration permettant à un réfrigérant aspiré de s'écouler dans la chambre de compression depuis l'extérieur du récipient hermétiquement fermé ; et
    raccorder un tuyau d'injection (41) au tuyau latéral, le tuyau d'injection permettant à un réfrigérant d'injection de s'écouler dans le trou latéral depuis l'extérieur du récipient hermétiquement fermé.
EP09847791.2A 2009-07-28 2009-07-28 Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection Not-in-force EP2461122B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/063412 WO2011013199A1 (fr) 2009-07-28 2009-07-28 Dispositif de pompe à chaleur, compresseur avec mécanisme d'injection et procédé de fabrication d'un compresseur à spirale avec mécanisme d'injection

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EP2461122A1 EP2461122A1 (fr) 2012-06-06
EP2461122A4 EP2461122A4 (fr) 2016-04-13
EP2461122B1 true EP2461122B1 (fr) 2018-12-19

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EP (1) EP2461122B1 (fr)
JP (1) JP5389173B2 (fr)
KR (1) KR101312762B1 (fr)
CN (1) CN102472528B (fr)
WO (1) WO2011013199A1 (fr)

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JP2012172581A (ja) * 2011-02-21 2012-09-10 Mitsubishi Electric Corp スクロール圧縮機及びヒートポンプ装置
JP5656691B2 (ja) * 2011-03-04 2015-01-21 三菱電機株式会社 冷凍装置
JP5777571B2 (ja) * 2012-06-11 2015-09-09 三菱電機株式会社 スクロール圧縮機
CN102953992A (zh) * 2012-11-27 2013-03-06 大连三洋压缩机有限公司 具有喷射通道的涡旋式压缩机
JP6355453B2 (ja) * 2014-06-27 2018-07-11 三菱電機株式会社 スクロール圧縮機
JP6541804B2 (ja) * 2016-01-29 2019-07-10 三菱電機株式会社 スクロール圧縮機およびヒートポンプ装置
JP6689300B2 (ja) * 2016-02-16 2020-04-28 三菱電機株式会社 スクロール圧縮機
CN105952638A (zh) * 2016-06-21 2016-09-21 广东美的暖通设备有限公司 涡旋压缩机和空调器
CN106122010A (zh) * 2016-08-22 2016-11-16 广东美的暖通设备有限公司 涡旋压缩机和制冷设备
EP3546756B1 (fr) * 2016-11-24 2022-01-19 Panasonic Intellectual Property Management Co., Ltd. Compresseur à spirales ayant une fonction d'injection
DE102016125400A1 (de) * 2016-12-22 2018-06-28 OET GmbH Verfahren zur Herstellung eines Scrollkompressors
WO2019069441A1 (fr) * 2017-10-06 2019-04-11 三菱電機株式会社 Dispositif à cycle frigorifique
JP6865861B2 (ja) * 2018-01-30 2021-04-28 三菱電機株式会社 スクロール圧縮機
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JP7345550B2 (ja) * 2019-07-16 2023-09-15 三菱電機株式会社 スクロール圧縮機
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ES2960489T3 (es) 2019-10-21 2024-03-05 Emerson Climate Tech Gmbh Refrigeración de compresor con fluido de succión
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Also Published As

Publication number Publication date
EP2461122A4 (fr) 2016-04-13
CN102472528B (zh) 2014-07-02
EP2461122A1 (fr) 2012-06-06
CN102472528A (zh) 2012-05-23
JPWO2011013199A1 (ja) 2013-01-07
KR101312762B1 (ko) 2013-09-27
JP5389173B2 (ja) 2014-01-15
KR20120024858A (ko) 2012-03-14
WO2011013199A1 (fr) 2011-02-03

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