EP1004773A1 - Spiralverdichter mit mehrstufigem mengenregler - Google Patents

Spiralverdichter mit mehrstufigem mengenregler Download PDF

Info

Publication number
EP1004773A1
EP1004773A1 EP99922489A EP99922489A EP1004773A1 EP 1004773 A1 EP1004773 A1 EP 1004773A1 EP 99922489 A EP99922489 A EP 99922489A EP 99922489 A EP99922489 A EP 99922489A EP 1004773 A1 EP1004773 A1 EP 1004773A1
Authority
EP
European Patent Office
Prior art keywords
opening
compressor
scroll
capacity
scroll compressor
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.)
Granted
Application number
EP99922489A
Other languages
English (en)
French (fr)
Other versions
EP1004773B1 (de
EP1004773A4 (de
Inventor
Kenji-Rinkai-kojo Daikin Industries Ltd. MATSUBA
Shigeki-Rinkai-kojo Daikin Industries L HAGIWARA
Yoshitaka-Rinkai-kojo Daikin Industrie SHIBAMOTO
Hiroyuki-Rinkai-kojo Daikin Industries L KUROIWA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP1004773A1 publication Critical patent/EP1004773A1/de
Publication of EP1004773A4 publication Critical patent/EP1004773A4/de
Application granted granted Critical
Publication of EP1004773B1 publication Critical patent/EP1004773B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/16—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
    • 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
    • F04C18/02—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

Definitions

  • the present invention relates to a multi-stage capacity-controlled scroll compressor which enables partial load operation in lower capacity regions.
  • Fig. 8 and Fig. 9 which is a sectional view taken along the line X - X of Fig. 8 (Japanese Patent Laid-Open Publication HEI 9-170573).
  • This scroll compressor is an asymmetrical spiral-type scroll compressor in which a scrolling end of a first scroll 1 is ⁇ (rad) longer in involute angle than a scrolling end of a second scroll 2.
  • a first fluid working chamber A defined by an inner surface of the first scroll 1 and an outer surface of the second scroll 2 and a second fluid working chamber B defined by an outer surface of the first scroll 1 and an inner surface of the second scroll 2 are alternately opened and closed to a single low-pressure port 3.
  • a common bypass hole 4 common to the first fluid working chamber A and the second fluid working chamber B is provided at a point j which is a point about one-scroll inwardly unwound from an outermost side contact point E of the second scroll 2 with the first scroll 1.
  • a valve hole 5 communicating with the common bypass hole 4 is formed in the first scroll 1, and a bypass passage 6 communicating with the low-pressure port 3 is formed in a side portion of the valve hole 5.
  • a stepped cylindrical bypass valve 7 for opening and closing the common bypass hole 4 is internally fitted so as to be slidable.
  • a coil spring 8 is engaged with the stepped portion of the bypass valve 7, and an upper portion of the bypass valve 7 is closed by a lid member 9 and thereby partitioned from a discharge dome 10 to define an operating-pressure chamber 11.
  • an operating-pressure line 15 communicated selectively with a low-pressure line 13 or a high-pressure line 14 by a solenoid valve 12 is connected to the operating-pressure chamber 11 via a joint tube 16.
  • Reference numeral 17 denotes a capillary tube for preventing shortcircuit between the high-pressure line 14 and the low-pressure line 13
  • numeral 18 denotes a casing
  • numeral 19 denotes a high-pressure port.
  • the common bypass hole 4 is formed at the point j, which is a point about one-round inwardly unwound from the outermost side contact point E of the second scroll 2 with the first scroll 1. Therefore, when high-pressure gas is supplied to the operating-pressure chamber 11 of the bypass valve 7 by closing the solenoid valve 12 and then the bypass valve 7 is closed, discharge capacity becomes the full capacity (100%). On the other hand, when low-pressure gas is supplied to the operating-pressure chamber 11 of the bypass valve 7 by opening the solenoid valve 12 and then the bypass valve 7 is opened, the discharge capacity becomes about 60% of the full capacity because the position of the common bypass hole 4 serves as a compression start point. In this way, the discharge capacity of the scroll compressor is switched between 100% and 60%.
  • the above multi-stage capacity-controlled scroll compressor of the prior art has the following problems. First, because its volume ratio Vr considerably lowers during a 50% or lower partial load operation, there is a problem that the operational range is limited.
  • increasing the intrinsic volume ratio Vr causes the critical partial load ratio to lower so that a 50% or lower partial load operation is enabled, but the efficiency at the full load would be lowered in that case, conversely, so that increasing the intrinsic volume ratio Vr could not be adopted.
  • an object of the present invention is to provide a multi-stage capacity-controlled scroll compressor which is capable of changing 50% or lower partial load operation in multiple stages and which is low in price and high in reliability.
  • a multi-stage capacity-controlled scroll compressor comprising:
  • the second opening/closing means opens and closes the second bypass passage, by which the load of the compressor can be switched between 100% and a first specified %.
  • the first opening/closing means opens and closes the first bypass passage, by which the discharge capacity of the compressor can be switched between 100% and a second specified %. Accordingly, in combinations of the opening and closing operations of the first opening/closing means and the opening and closing operations of the second opening/closing means, effective load of the compressor can be changed over in four stages. In this case, the discharge capacity of the compressor can be changed over only to the second specified % by the first opening/closing means.
  • the volume ratio for the compressor and the second specified % are so set that the volume ratio at which the discharge capacity of the compressor becomes the second specified % becomes 1 or more, then the volume ratio can be maintained 1 or more even when the effective load of the compressor becomes a minimum, so that high-reliability multi-stage load control can be achieved.
  • a first scroll and a second scroll of which the compression chamber is formed show asymmetrical spiral shapes, respectively, that a spiral end of one scroll is 180 degree longer in involute angle than a spiral end of the other scroll.
  • the first fluid working chamber defined by the inner surface of the first scroll and the outer surface of the second scroll and the second fluid working chamber defined by the outer surface of the first scroll and the inner surface of the second scroll are formed alternately at positions on the same first bypass passage. Accordingly, the high-pressure gas in the fluid working chambers is returned from the only one first bypass passage to the suction port.
  • the second bypass passage is provided outside a body of the compressor.
  • the second bypass passage and the second opening/closing means do not need to be formed within the compressor body, and may be formed between discharge line and suction line. Accordingly, the multi-stage capacity-controlled scroll compressor is produced with low price.
  • the second bypass passage and the second opening/closing means are provided each in a plural number.
  • the second bypass passage and the second opening/closing means are provided in pluralities. Accordingly, in combinations of the opening and closing operations of the second opening/closing means and the opening and closing operations of the first opening/closing means, 8 or more stages of multi-stage load control is achieved.
  • the second opening/closing means for opening and closing the second bypass passage is a motor-operated valve which is controllable to any arbitrary degree of openness.
  • the second opening/closing means operates on a differential pressure between a pilot pressure and a pressure on the suction side or a pressure on the discharge side.
  • control system for the second opening/closing means can be implemented with simplicity, so that the multi-stage capacity-controlled scroll compressor is produced with low price.
  • the multi-stage capacity-controlled scroll compressor further comprises a liquid injection tube for cooling a low-pressure chamber communicating with the suction port.
  • the low-pressure chamber and the driving motor are cooled by cooling liquid injected from the liquid injection tube.
  • temperature increase of the low-pressure chamber due to the return of the high-pressure gas in the compression chamber to the suction port is prevented, making it possible to lower the temperature of the discharged gas and the motor.
  • the first opening/closing means and the second opening/closing means operate on a pilot pressure
  • a pilot port of the first opening/closing means and a pilot port of the second opening/closing means are connected to their corresponding pilot lines, respectively, via one joint fitting provided at an upper center of the compressor body.
  • the joint fitting that connects the pilot ports of the first and second opening/closing means and their respective pilot lines to each other need to be provided only one in number at an upper center of the compressor, so that the port and line connection can be taken out from one place, the casing top center. Therefore, as compared with the case where the port and line connection is taken out from two decentered places of the casing top, in which case elliptical welding with the operating tube needs to be provided at two places, the welding work between the casing top and the operating tube can be achieved with simplicity, so that the man-hours for assembly is reduced, thus allowing a further cost reduction.
  • a multi-stage capacity-controlled scroll compressor comprises:
  • a twin multi-stage capacity-controlled scroll compressor is made up of a multi-stage capacity-controlled scroll compressor and a standard scroll compressor. Accordingly, in a combination of switching to two load states of unload and full load with the standard scroll compressor and n-stage load switching with the multi-stage capacity-controlled scroll compressor, load can be changed over in 2 ⁇ n stages. Thus, load control can be achieved in even further multiple stages.
  • the first opening/closing means operates on a pilot pressure
  • a pilot port of the first opening/closing means and joint fittings for connecting a pilot line to the pilot port are connected to each other by screws.
  • FIG. 1 is a partial sectional view of a multi-stage capacity-controlled scroll compressor of a first embodiment.
  • a first scroll 21, a second scroll 22, a low-pressure port 23, a common bypass hole 24, a valve hole 25, a bypass passage 26, a bypass valve 27, a coil spring 28, a lid member 29, a discharge dome 30, an operating-pressure chamber 31, a solenoid valve 32, a low-pressure line 33, a high-pressure line 34, an operating-pressure line 35, a joint tube 36, a capillary tube 37, a casing 38 and a high-pressure port 39 have the same constitution and operate in the same manner, respectively, as the first scroll 1, the second scroll 2, the low-pressure port 3, the common bypass hole 4, the valve hole 5, the bypass passage 6, the bypass valve 7, the coil spring 8, the lid member 9, the discharge dome 10, the operating-pressure chamber 11, the solenoid valve 12, the low-pressure line 13, the high-pressure line 14, the operating-pressure line 15,
  • the end plate of the first scroll 21 is provided a second bypass valve 40 which makes a through hole 45 selectively communicate with a suction side communicating with the low-pressure port 23 or a discharge side in the discharge dome 30.
  • the bypass valve 27 is referred to as a first bypass valve and the bypass valve 40 is referred to as a second bypass valve.
  • the second bypass valve 40 roughly comprises a cylindrical-shaped cylinder part 42 provided so as to be protrusive on the surface on the high pressure side of an end plate 41 of the first scroll 21, a valve body 43 which has a ball at its end and slides within the cylinder 42, and a spring 44 fitted and shrunk between the valve body 43 and the cylinder 42.
  • a fitting portion 42a which has a shaft hole communicating with inside of the cylinder 42 and has a fitting screw provided on its outer circumferential face. Also, in the end plate 41, the through hole 45 is bored through this end plate 41, and a fitting hole 45a into which the fitting portion 42a of the cylinder 42 is screwed is formed at an upper end portion of the through hole 45.
  • an upper portion of the cylinder 42 is partitioned from the discharge dome 30 to define an operating-pressure chamber 46.
  • an operating-pressure line 48 which is communicated selectively with the low-pressure line 33 or the high-pressure line 34 by a second solenoid valve 47 is connected to the operating-pressure chamber 46 via a joint tube 49.
  • the solenoid valve 32 is referred to as a first solenoid valve, and the solenoid valve 47 is referred to as a second solenoid valve.
  • reference numeral 50 denotes a capillary tube for preventing shortcircuit between the high-pressure line 34 and the low-pressure line 33.
  • a stepped portion which is made smaller in diameter on its low-pressure side, is formed in the outer circumferential surface of the valve body 43, and a spring 44 is fitted to this smaller-diameter portion.
  • a through hole 51 which radially communicates inside and outside of the cylinder 42 with each other.
  • the larger-diameter portion of the valve body 43 closes the through hole 51 so that the load of the compressor is set to 100% (hereinafter, the load set in this way will be referred to as set load).
  • the through hole 51 of the valve body 43 is opened so that the set load of the compressor becomes 50%. That is, in this embodiment, the second bypass passage is implemented by the through hole 45, while the second opening/closing means is implemented by the second bypass valve 40.
  • the multi-stage capacity-controlled scroll compressor having the above constitution is enabled to perform multi-stage load control, as shown below, by controlling the first bypass valve 27 and the second bypass valve 40.
  • closing the second solenoid valve 47 causes the second bypass valve 40 to be closed, so that the set load of the compressor becomes 100%.
  • the first bypass valve 27 that communicates with the low-pressure port 23 to yield a discharge capacity of 60% is provided at the point J (see Fig. 9) which is about one-round inwardly unwound from the outermost side contact point E of the second scroll 22 with the first scroll 21.
  • the second bypass valve 40 that makes the suction side and the discharge side selectively communicated with each other to yield a 50% set load of the compressor is provided outside the scroll of the first scroll 21.
  • the first bypass valve 27 and the second bypass valve 40 are opened and closed depending on a differential pressure between the pressure of the low-pressure line 33 or the high-pressure line 34 and the pressure on the suction side. Therefore, closing both the second bypass valve 40 and the first bypass valve 27 allows the effective load of the compressor to be 100%. Also, closing the second bypass valve 40 and concurrently opening the first bypass valve 27 allows the effective load of the compressor to be 60%. Also, opening both the second bypass valve 40 and the first bypass valve 27 allows the effective load of the compressor to be 30%.
  • 50% or lower partial load operation with high reliability can be achieved by setting the volume ratio Vr during the minimum capacity operation to a value of "1" or more.
  • the multi-stage capacity-controlled scroll compressor having the above constitution can be implemented simply by boring the through hole 45 through the end plate 41 outside the scroll of the first scroll 21 in the conventional asymmetrical spiral-type multi-stage capacity-controlled scroll compressor having the first bypass valve 27, and by screwing the fitting portion 42a of the cylinder 42 to an upper end portion of the through hole 45.
  • the second bypass valve 40 to be provided outside the scroll does not require such precision as demanded for the first bypass valve 27 provided within the scroll. Accordingly, the multi-stage capacity-controlled scroll compressor can be provided with a smaller number of parts and at low price.
  • Fig. 3 is a partial sectional view showing a modification example of the multi-stage capacity-controlled scroll compressor shown in Fig. 1.
  • the operating-pressure lines 67, 72 are connected to the first bypass valve 63 and the second bypass valve 69 via one joint tube 74 fitted to a top center of a casing 73.
  • the operating-pressure line 67 is connected to the first hole 74a by a first bolt joint 75
  • the operating-pressure line 72 is connected to the second hole 74b by a second bolt joint 76.
  • an operating-pressure chamber 78 of the first bypass valve 63 is connected to the first hole 74a by a first piping 77
  • an operating-pressure chamber 80 of the second bypass valve 69 is connected to the second hole 74b by a second piping 79.
  • Fig. 4 is a partial sectional view showing a multi-stage capacity-controlled scroll compressor according to a second embodiment.
  • a first scroll 81, a second scroll 82, a low-pressure port 83, a bypass valve 84, a first solenoid valve 85, a low-pressure line 86, a high-pressure line 87, an operating-pressure line 88, a joint tube 89 and a high-pressure port 90 have the same constitution and operate in the same manner, respectively, as the first scroll 21, the second scroll 22, the low-pressure port 23, the first bypass valve 27, the first solenoid valve 32, the low-pressure line 33, the high-pressure line 34, the operating-pressure line 35, the joint tube 36 and the high-pressure port 39 of the multi-stage capacity-controlled scroll compressor shown in Fig. 1.
  • the second bypass valve 40 which is provided in an upper portion of the through hole 45 bored in the end plate 41 of the first scroll 21, is opened and closed so that the second bypass valve 40 makes the low-pressure inner side of the end plate 41 selectively communicate with the suction side or the discharge side, by which the set load of the compressor is switched between 100% and 50%.
  • the selective communication between the suction side and the discharge side can be achieved in another way.
  • the low-pressure line 86 and the high-pressure line 87 are connected to each other by a bypass passage 93 on which a second solenoid valve 91 and a capillary tube 92 are provided interveniently, by which the selective communication between the suction side and the discharge side is enabled.
  • the capillary tube 92 prevents shortcircuit between the high-pressure line 87 and the low-pressure line 86.
  • multi-stage load control is performed in the following manner.
  • closing the first solenoid valve 85 causes the first bypass valve 84 to be closed so that the discharge capacity becomes 100%. Accordingly, the effective load of the compressor in this case is 100%.
  • opening the first solenoid valve 85 causes the first bypass valve 84 to be opened so that the discharge capacity becomes 60%. Accordingly, the effective load of the compressor in this case is 60%.
  • the set load of the compressor becomes 50%.
  • opening the first solenoid valve 85 causes the discharge capacity to be 60%. Accordingly, the effective load of the compressor in this case is 30%. In this way, as in the case of the first embodiment, 50% or lower partial load operation with high reliability can be achieved by setting the volume ratio Vr during the minimum capacity operation to "1" or more.
  • the selective communication between the suction side and the discharge side is enabled by a very simple means of connecting the low-pressure line 86 and the high-pressure line 87 to each other by the bypass passage 93 on which the second solenoid valve 91 is interveniently provided. Therefore, it is no longer necessary to provide the second bypass valve 40 within the compressor body, unlike the first embodiment, so that a further cost reduction can be achieved.
  • the set load of the compressor can be changed in multiple stages arbitrarily. Therefore, in that case, in combination with the opening/closing operations of the first solenoid valve 85, 50% or lower arbitrary multi-stage load control with high reliability can be achieved.
  • Fig. 5 is a partial sectional view showing a modification example of the multi-stage capacity-controlled scroll compressor shown in Fig. 4.
  • the low-pressure line 106 and the high-pressure line 107 are connected to each other by a bypass passage 113 on which a second solenoid valve 111 that sets the set load of the compressor in the opened state to 75% is provided interveniently, and by a bypass passage 114 on which a third solenoid valve 112 that sets the set load of the compressor in the opened state to 65% is provided interveniently. Then, by controlling the opening and closing operations of the first solenoid valve 105, the second solenoid valve 111 and the third solenoid valve 112, multi-stage load control is performed in the following manner.
  • the set load of the compressor becomes 100%.
  • closing the first solenoid valve 105 causes the first bypass valve 104 to be closed so that the discharge capacity becomes 100%. Accordingly, the effective load of the compressor in this case is 100%.
  • opening the first solenoid valve 105 causes the first bypass valve 104 to be opened so that the discharge capacity becomes 50%. Accordingly, the effective load of the compressor in this case is 50%.
  • closing the third solenoid valve 112 and concurrently opening the second solenoid valve 111 the set load of the compressor becomes 75%. In this state, closing the first solenoid valve 105 causes the discharge capacity to be 100%.
  • the effective load of the compressor in this case is 75%.
  • opening the first solenoid valve 105 causes the discharge capacity to be 50%.
  • 50% or lower multi-stage load control with high reliability can be achieved by setting the volume ratio Vr during the minimum capacity operation to "1" or more.
  • up to 8-stage load control can be implemented.
  • Fig. 6 is an arrangement view of a multi-stage capacity-controlled scroll compressor according to a third embodiment.
  • a multi-stage capacity-controlled scroll compressor having any one of the constitutions of the foregoing embodiments (hereinafter, referred to as capacity-controlled compressor) and a standard-structure (non capacity-controlled) scroll compressor (hereinafter, referred to as standard compressor), 50% or lower high-multi-stage load control is performed.
  • the standard compressor 121 is a non-capacity-controlled type scroll compressor having a maximum discharge capacity one half the maximum capacity required by a system to which high-pressure gas is supplied (hereinafter, the maximum capacity required will be referred to simply as necessary maximum capacity).
  • the capacity-controlled compressor 122 is, for example, a multi-stage capacity-controlled scroll compressor shown in Fig. 5, which has a maximum discharge capacity one half the necessary maximum capacity of the system. In the capacity-controlled compressor 122, discharge capacity is switched between 100% and 50% by controlling the opening and closing operations of the bypass valve (see Fig.
  • a liquid injection tube 126 having a nozzle is provided, for example, outside the scroll of the first scroll in the capacity-controlled compressor 122, and a liquid line 127 from the system side is connected to this liquid injection tube 126.
  • the multi-stage capacity-controlled scroll compressor of the above constitution operates in the following manner.
  • the standard compressor 121 is put into an unload state.
  • the capacity-controlled compressor 122 is set to an effective load of 24% as described above.
  • setting the effective load of the capacity-controlled compressor 122 to 75% causes the effective discharge capacity to the system to be 37.5% of the necessary maximum capacity.
  • Setting the effective load of the capacity-controlled compressor 122 to 100% causes the effective discharge capacity to the system to be 50% of the necessary maximum capacity.
  • the standard compressor 121 is put into a full-load (100%) state.
  • the capacity-controlled compressor 122 is set to an effective load of 24% in the way as described above.
  • setting the effective load of the capacity-controlled compressor 122 to 50% causes the effective discharge capacity to the system to be 75% of the necessary maximum capacity.
  • setting the effective load of the capacity-controlled compressor 122 to 75% causes the effective discharge capacity to the system to be 87.5% of the necessary maximum capacity.
  • Setting the effective load of the capacity-controlled compressor 122 to 100% causes the effective discharge capacity to the system to be 100% of the necessary maximum capacity.
  • a liquid injection tube 126 is provided in the capacity-controlled compressor 122 so that a liquid coolant is injected from the system side. Accordingly, the injected liquid coolant flows down from the compressor section comprising the first scroll and the second scroll toward the motor that drives the second scroll into rotation, by which the compressor section and the motor are cooled. In this way, the discharge gas and the motor are lowered in temperature, so that the operable range is enlarged.
  • the provision of the liquid injection tube in the capacity-controlled compressor may be applied to the multi-stage capacity-controlled scroll compressors of the first and second embodiments.
  • a twin multi-stage capacity-controlled scroll compressor is made up of the standard compressor 121 having a maximum discharge capacity which is one half of the maximum capacity required for the system, and the capacity-controlled compressor 122 having a maximum discharge capacity which is one half of the maximum capacity required for the system. Therefore, by changing over the effective load of the capacity-controlled compressor 122 to 24%, 50%, 75% and 100% simultaneously when the standard compressor 121 is switched between the unload state and the full load state, the effective discharge capacity from the twin multi-stage capacity-controlled scroll compressor to the system can be changed over to 8 stages of 12%, 25%, 37.5%, 50%, 62%, 75%, 87.5% and 100% of the necessary maximum capacity of the system.
  • the effective discharge capacity from the twin multi-stage capacity-controlled scroll compressor to the system can be changed over in 16 stages.
  • the maximum discharge capacity may be set as appropriate, depending on required effective discharge capacity, without being limited to the above case.
  • the joint tube 36 to be connected to the operating-pressure chamber 31 of the first bypass valve 27 in the foregoing embodiments is fitted with its end being inserted into a hole bored in the lid member 29, and further sealed by an O-ring 52.
  • a fitting structure is weak to vibrations of the joint tube 36, which may lead to occurrence of leakage depending on conditions of use. Further, there is a problem of thermal resistance.
  • a fitting structure as shown in Figs. 7A and 7B are adopted in the fourth embodiment.
  • a male screw 132 is provided at a taper portion of an end of a joint tube 131, while a female screw 134 is provided at a taper hole of a lid member 133. Then, the taper portion of the end of the joint tube 131 is screwed into the taper hole of the lid member 133, by which the joint tube 131 is fitted to the lid member 133.
  • a fitting structure of the joint tube 131 which is strong to vibrations and high in leakage resistance and thermal resistance can be obtained.
  • a joint tube body 135 and a tube body 136 are separated from each other, and the tube body 136 and a lid member 137 are formed integrally.
  • an end of the tube body 136 is protruded through a hole 139 of a casing 138, and fixed by welding at the place of the hole 139.
  • the taper hole of the joint tube body 135 is screwed to the taper portion of the end of the tube body 136.
  • the above embodiments have been described, taking as an example a so-called asymmetrical spiral-type scroll compressor in which, as shown in Fig. 9, the spiral end of the first scroll 21, 61, 81, 101 is ⁇ (rad) longer in involute angle than the spiral end of the second scroll 22, 62, 82, 102, and in which the outermost side contact point E of the second scroll 22, 62, 82, 102 with the first scroll 21, 61, 81, 101 is the aforementioned spiral end.
  • the present invention is not limited to this, and can be applied to so-called symmetrical spiral-type scroll compressors in which spiral ends of a symmetrical pair of scrolls are shifted from each other by ⁇ (rad) in involute angle.
  • the first fluid working chamber A defined by the inner surface of the first scroll and the outer surface of the second scroll, and the second fluid working chamber B defined by the outer surface of the first scroll and the inner surface of the second scroll are not formed at the same position but formed so as to be opposed to each other, in which case therefore the first bypass valve for changing the discharge capacity of the compressor needs to be provided two in number, one for the first fluid working chamber A and the other for the second fluid working chamber B, at positions opposed to each other.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP99922489A 1998-06-12 1999-05-26 Spiralverdichter mit mehrstufigem mengenregler Expired - Lifetime EP1004773B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP10165022A JP2974009B1 (ja) 1998-06-12 1998-06-12 多段階容量制御スクロール圧縮機
JP16502298 1998-06-12
PCT/JP1999/002761 WO1999064744A1 (fr) 1998-06-12 1999-05-26 Compresseur a volute de type a commande de capacite en plusieurs etapes

Publications (3)

Publication Number Publication Date
EP1004773A1 true EP1004773A1 (de) 2000-05-31
EP1004773A4 EP1004773A4 (de) 2004-05-12
EP1004773B1 EP1004773B1 (de) 2010-12-08

Family

ID=15804366

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99922489A Expired - Lifetime EP1004773B1 (de) 1998-06-12 1999-05-26 Spiralverdichter mit mehrstufigem mengenregler

Country Status (7)

Country Link
EP (1) EP1004773B1 (de)
JP (1) JP2974009B1 (de)
KR (1) KR100601270B1 (de)
CN (1) CN1094566C (de)
DE (1) DE69943017D1 (de)
ES (1) ES2356224T3 (de)
WO (1) WO1999064744A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2025939A2 (de) 2007-08-03 2009-02-18 Scroll Technologies Abgestufter Spiralverdichter mit Kapazitätsmodulation
EP2213879A1 (de) * 2009-01-22 2010-08-04 Danfoss Scroll Technologies Spiralverdichter mit dreistufiger Leistungssteuerung
US10316843B2 (en) 2016-05-30 2019-06-11 Lg Electronics Inc. Scroll compressor that includes a non-orbiting scroll having a bypass hole
US10428818B2 (en) 2016-02-24 2019-10-01 Lg Electronics Inc. Scroll compressor
US10428819B2 (en) 2016-05-25 2019-10-01 Lg Electronics Inc. Scroll compressor that includes a non-orbiting scroll having a bypass hole

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6478550B2 (en) 1998-06-12 2002-11-12 Daikin Industries, Ltd. Multi-stage capacity-controlled scroll compressor
CN100343527C (zh) * 2002-12-25 2007-10-17 乐金电子(天津)电器有限公司 具有防真空能力的涡轮压缩机
KR100547322B1 (ko) 2003-07-26 2006-01-26 엘지전자 주식회사 용량 조절식 스크롤 압축기
KR100557056B1 (ko) 2003-07-26 2006-03-03 엘지전자 주식회사 용량 조절식 스크롤 압축기
KR100695822B1 (ko) * 2004-12-23 2007-03-20 엘지전자 주식회사 스크롤 압축기의 계단형 용량 가변장치
KR100585811B1 (ko) 2004-12-31 2006-06-07 엘지전자 주식회사 용량 가변형 스크롤 압축기
JP5040907B2 (ja) * 2008-09-30 2012-10-03 ダイキン工業株式会社 冷凍装置
JP5489142B2 (ja) * 2011-02-22 2014-05-14 株式会社日立製作所 スクロール圧縮機
CN106286292B (zh) * 2015-05-27 2018-12-04 珠海格力节能环保制冷技术研究中心有限公司 压缩组件、变容量涡旋压缩机及空调器
CN105275804B (zh) * 2015-10-15 2017-10-10 珠海格力节能环保制冷技术研究中心有限公司 涡旋压缩机的变容机构及涡旋压缩机
US10563891B2 (en) * 2017-01-26 2020-02-18 Trane International Inc. Variable displacement scroll compressor
JP6489166B2 (ja) * 2017-07-05 2019-03-27 ダイキン工業株式会社 スクロール圧縮機
CN211343341U (zh) * 2018-09-19 2020-08-25 艾默生环境优化技术(苏州)有限公司 涡旋压缩机

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3985472A (en) * 1975-04-23 1976-10-12 International Harvester Company Combined fixed and variable displacement pump system
US4886425A (en) * 1987-03-26 1989-12-12 Mitsubishi Jukogyo Kabushiki Kaisha Capacity control device of scroll-type fluid compressor
US4904164A (en) * 1987-06-30 1990-02-27 Sanden Corporation Scroll type compressor with variable displacement mechanism
US5112201A (en) * 1989-08-02 1992-05-12 Hitachi, Ltd. Scroll compressor apparatus with separate oil reservoir vessel
US5336058A (en) * 1992-02-18 1994-08-09 Sanden Corporation Scroll-type compressor with variable displacement mechanism
US5577897A (en) * 1992-04-01 1996-11-26 Nippondenso Co., Ltd. Scroll-type variable-capacity compressor having two control valves
US5678985A (en) * 1995-12-19 1997-10-21 Copeland Corporation Scroll machine with capacity modulation

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3132888B2 (ja) * 1992-04-01 2001-02-05 株式会社日本自動車部品総合研究所 スクロール型可変容量圧縮機
JPH0979152A (ja) * 1995-09-11 1997-03-25 Sanyo Electric Co Ltd スクロール圧縮機
JP3591101B2 (ja) * 1995-12-19 2004-11-17 ダイキン工業株式会社 スクロール形流体機械

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3985472A (en) * 1975-04-23 1976-10-12 International Harvester Company Combined fixed and variable displacement pump system
US4886425A (en) * 1987-03-26 1989-12-12 Mitsubishi Jukogyo Kabushiki Kaisha Capacity control device of scroll-type fluid compressor
US4904164A (en) * 1987-06-30 1990-02-27 Sanden Corporation Scroll type compressor with variable displacement mechanism
US5112201A (en) * 1989-08-02 1992-05-12 Hitachi, Ltd. Scroll compressor apparatus with separate oil reservoir vessel
US5336058A (en) * 1992-02-18 1994-08-09 Sanden Corporation Scroll-type compressor with variable displacement mechanism
US5577897A (en) * 1992-04-01 1996-11-26 Nippondenso Co., Ltd. Scroll-type variable-capacity compressor having two control valves
US5678985A (en) * 1995-12-19 1997-10-21 Copeland Corporation Scroll machine with capacity modulation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO9964744A1 *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2025939A2 (de) 2007-08-03 2009-02-18 Scroll Technologies Abgestufter Spiralverdichter mit Kapazitätsmodulation
EP2025939A3 (de) * 2007-08-03 2010-08-11 Scroll Technologies Abgestufter Spiralverdichter mit Kapazitätsmodulation
EP2213879A1 (de) * 2009-01-22 2010-08-04 Danfoss Scroll Technologies Spiralverdichter mit dreistufiger Leistungssteuerung
US8328531B2 (en) 2009-01-22 2012-12-11 Danfoss Scroll Technologies, Llc Scroll compressor with three-step capacity control
US10428818B2 (en) 2016-02-24 2019-10-01 Lg Electronics Inc. Scroll compressor
US10428819B2 (en) 2016-05-25 2019-10-01 Lg Electronics Inc. Scroll compressor that includes a non-orbiting scroll having a bypass hole
US11204035B2 (en) 2016-05-25 2021-12-21 Lg Electronics Inc. Scroll compressor having a valve assembly controlling the opening/closing valve to open and close communication passage and bypass holes on fixed scroll
US10316843B2 (en) 2016-05-30 2019-06-11 Lg Electronics Inc. Scroll compressor that includes a non-orbiting scroll having a bypass hole
US11215181B2 (en) 2016-05-30 2022-01-04 Lg Electronics Inc. Scroll compressor that includes a non-orbiting scroll member having a connection passage portion connected first valve assembly and second valve assembly

Also Published As

Publication number Publication date
KR20010022824A (ko) 2001-03-26
KR100601270B1 (ko) 2006-07-13
CN1272906A (zh) 2000-11-08
EP1004773B1 (de) 2010-12-08
ES2356224T3 (es) 2011-04-06
JPH11351167A (ja) 1999-12-21
WO1999064744A1 (fr) 1999-12-16
JP2974009B1 (ja) 1999-11-08
EP1004773A4 (de) 2004-05-12
CN1094566C (zh) 2002-11-20
DE69943017D1 (de) 2011-01-20

Similar Documents

Publication Publication Date Title
US6478550B2 (en) Multi-stage capacity-controlled scroll compressor
EP1004773B1 (de) Spiralverdichter mit mehrstufigem mengenregler
EP3810934B1 (de) Spiralverdichter mit einer axialen druckkammer
AU768192B2 (en) Compressor pulse width modulation
US9360011B2 (en) System including high-side and low-side compressors
AU2004202610B2 (en) Plural compressors
EP1253323B1 (de) Hermetische Verdichter
EP0144169B1 (de) Verdichter mit spiralförmigem Förderraum und einstellbarer Förderleistung
US6202428B1 (en) Air conditioner
US10982674B2 (en) Scroll compressor with back pressure chamber and back pressure passages
KR100725893B1 (ko) 스크롤형 유체기계
CN108361195A (zh) 可变排量涡旋压缩机
CN111502987B (zh) 容量调节和喷气增焓一体式涡旋压缩机及其系统
CN217999879U (zh) 压缩机构及涡旋压缩机
EP4039980A1 (de) Spiralverdichter mit abgasvorwärmereinspritzung
US12092379B2 (en) Compressor and refrigeration cycle device having the same
CN117365954A (zh) 定涡旋组件、涡旋压缩机及加工定涡旋组件的方法
AU2003252946B2 (en) Compressor pulse width modulation
JP2002250287A (ja) スクロール圧縮機

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): BE DE ES FR GB IT

17P Request for examination filed

Effective date: 20000505

A4 Supplementary search report drawn up and despatched

Effective date: 20040325

RIC1 Information provided on ipc code assigned before grant

Ipc: 7F 04C 29/10 B

Ipc: 7F 04C 18/02 A

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 29/12 20060101ALI20100527BHEP

Ipc: F04C 18/02 20060101AFI20100527BHEP

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KUROIWA, HIROYUKI

Inventor name: SHIBAMOTO, YOSHITAKA

Inventor name: HAGIWARA, SHIGEKI

Inventor name: MATSUBA, KENJI

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): BE DE ES FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 69943017

Country of ref document: DE

Date of ref document: 20110120

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2356224

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20110406

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20101208

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20110520

Year of fee payment: 13

Ref country code: FR

Payment date: 20110523

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20110525

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20110518

Year of fee payment: 13

Ref country code: IT

Payment date: 20110523

Year of fee payment: 13

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20110909

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 69943017

Country of ref document: DE

Effective date: 20110909

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20120526

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120526

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20130131

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 69943017

Country of ref document: DE

Effective date: 20121201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120531

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120526

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20121201

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20130820

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120527