CN101344089A - Compression system, multi-cylinder rotary compressor - Google Patents

Compression system, multi-cylinder rotary compressor Download PDF

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Publication number
CN101344089A
CN101344089A CNA2008101340490A CN200810134049A CN101344089A CN 101344089 A CN101344089 A CN 101344089A CN A2008101340490 A CNA2008101340490 A CN A2008101340490A CN 200810134049 A CN200810134049 A CN 200810134049A CN 101344089 A CN101344089 A CN 101344089A
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China
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refrigerant
blade
pressure
cylinder
mentioned
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CNA2008101340490A
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CN101344089B (en
Inventor
西川刚弘
小笠原弘丞
須田章博
�原正之
泽边浩幸
吉田浩之
桥本彰
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Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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Priority claimed from JP2004201915A external-priority patent/JP4404708B2/en
Priority claimed from JP2004203001A external-priority patent/JP2006022766A/en
Priority claimed from JP2004202994A external-priority patent/JP4726444B2/en
Priority claimed from JP2004235419A external-priority patent/JP2006052693A/en
Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd
Publication of CN101344089A publication Critical patent/CN101344089A/en
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    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/001—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 of similar working principle
    • 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

Abstract

The object of the present invention is to prevent the second blade of a compression system with a muti-cylinder rotary compressor from generating conflicting sound. The compression system comprises a multicylinder rotary compressor being configured to be used by switching of a first operation mode in which both rotary compression elements (32,34) perform a compression work and a the second operation mode in which the only first rotary compression element (32) substantially performs the compression work. When the second operation mode is switched to the first operation mode, discharge-side pressures of both the rotary compression elements (32,34) are applied as a back pressure of the second vane (52), and thereafter an intermediate pressure is applied which is between suction-side and discharge-side pressures of both the rotary compression elements. When the first operation mode is switched to the second operation mode, a valve device (106) interrupts flowing of a refrigerant into a second cylinder (40), and thereafter suction-side pressures of both the rotary compression elements (32,34) are applied as the back pressure of the second vane (52).

Description

Compression system, multi-cylinder rotary compressor
The application's denomination of invention that to be Sanyo Electric Co., Ltd proposed on 06 07th, 2005 is dividing an application of 200510076423.2 application for " compression system, compression system, multi-cylinder rotary compressor and the refrigerating plant that uses it ", application number.
Technical field
The refrigerating plant that the present invention relates to compression system and constitute its compression system, multi-cylinder rotary compressor and use it.
Technical background
In the past, this compression system was that control gear etc. by the running of compression system, multi-cylinder rotary compressor and this compression system, multi-cylinder rotary compressor of control constitutes.This compression system, multi-cylinder rotary compressor, two cylinder rotary compressors that for example have the first and second rotation compressing member are to take in driving element and rotate compressing member by the rotation of this driving element shaft-driven first and second to form in seal container.This first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is entrenched in the eccentric part that is formed on the running shaft, eccentric respectively rotation in each cylinder, this first and second blade contacts with this first and second cylinder, will be divided into low pressure chamber side and hyperbaric chamber side in each cylinder respectively.In addition, first and second blade is always suppressed to first and second roller respectively by spring members.
Like this, if be driven by above-mentioned control gear driving element, then the refrigerant gas of low pressure is inhaled into the first and second low pressure chamber side of rotating each cylinder of compressing member from sucking path, action by each roller and each blade is compressed respectively, become the refrigerant gas of High Temperature High Pressure, from the hyperbaric chamber side of each cylinder by exhaust port be discharged to discharge the anechoic chamber after, be discharged in the seal container, be discharged to the outside and constitute (for example, opening flat 5-99172 communique) with reference to the spy.
In compression system with such compression system, multi-cylinder rotary compressor, little ability zone when light hours or low speed rotation etc., undertaken under the situation of compression operation by first and second liang of cylinder, because must suck the refrigerant gas of the eliminating cubical content of two cylinders compresses, so should amount pass through control gear, the revolution that reduces driving element turns round.But excessive if revolution reduces, the efficient that has then produced driving element reduces, the while leakage loss increases, the significantly reduced problem of running efficiency.
Therefore, in view of this problem, developing can be according to ability, to the compression system that a cylinder turns round and two cylinder is changed.Promptly, eliminate spring members with any one party of first and second blade in the spring members that first and second roller suppresses of compression system, multi-cylinder rotary compressor, for example eliminate the spring members that second blade is suppressed to second roller, pass through control gear, when two cylinder turns round, as the back pressure of second blade, become the compression system of the refrigerant pressure of the discharge side that applies two rotation compressing members.In view of the above, second blade is suppressed to the second roller side, finishes the compression work done.
On the other hand, when being converted to cylinder running from above-mentioned two cylinder,,, become the compression system of the refrigerant pressure of the suction side that applies two rotation compressing members as the back pressure of second blade by control gear.Because this suction pressure is a low pressure, so second blade can not be suppressed to the second roller side.Therefore, in the second rotation compressing member, not compressing work done in fact, only is the compression work done of carrying out refrigerant in the first rotation compressing member.
Like this, by the cylinder running in little ability zone, owing to can reduce the amount of compressed refrigerant gas, this amount can make revolution rise.In view of the above, the running efficiency of driving element can be improved, and also leakage loss can be reduced.
Here, as mentioned above, when two cylinder turns round, be not provided with in the second rotation compressing member of spring members, the discharge side pressure pressure oscillation of two rotation compressing members of suppressing second roller is big, because this pressure oscillation, the tracing ability of blade worsens, because between second roller and second blade, produce the conflict sound,, apply the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure so the claimant has attempted the back pressure as second roller.
But, in back pressure, applied under the situation of above-mentioned intermediate pressure as second blade, produced following problems, that is, when being converted to the two cylinder running from a cylinder, make second blade follow spended time on second roller, betwixt, second blade conflicts with second roller, has produced the conflict sound.
On the other hand, also there is following problems, promptly, when a cylinder turns round, because the back pressure of the pressure in second cylinder and second blade is applied identical suction side pressure, so when turning round from two cylinder to cylinder running conversion, second blade is difficult to be introduced in second cylinder 40, betwixt, conflict, still produce the conflict sound with second roller.
In addition, though during the running by compression system, multi-cylinder rotary compressor with the snap action of blade to roller, back pressure side (side opposite with roller) at blade produces pressure pulse, but, still have following problems, promptly, second blade that spring members is not set is because this pressure pulse, the tracing ability of second blade worsens, and conflicts with second roller, produces the conflict sound.
Have, the discharge side pressure pressure oscillation of the two rotation compressing members that apply as the back pressure of second blade is big again, and even so, the tracing ability that second blade of spring members is not set worsens, and produces the conflict sound between second roller and second blade.
Also have, though when a cylinder turns round, in the second rotation compressing member, second roller becomes idling conditions, but, still have following problems, promptly, because this moment, back pressure to the pressure in second cylinder and second blade has applied identical suction side pressure, because the change of the balance in two spaces, second blade is outstanding in second cylinder, conflict with second roller, still produce the conflict sound.
Summary of the invention
The present invention is exactly the invention that produces for the problem that solves the conventional art, be in having the compression system of compression system, multi-cylinder rotary compressor, with the conflict sound of avoiding producing during operation mode in conversion second blade is purpose, this compression system, multi-cylinder rotary compressor only suppresses first blade by spring members to first roller, can change and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact.
Compression system of the present invention has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compressor only suppresses first blade by spring members to first roller, can change and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact, from second operation mode when first operation mode is changed, in back pressure as second blade, after having applied the discharge side pressure of two rotation compressing members, apply the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure.
In addition, compression system of the present invention has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compressor only suppresses first blade by spring members to first roller, can change and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact, be provided for controlling control valve unit to the refrigerant circulation of second cylinder, from first operation mode when second operation mode is changed, cutting off by control valve unit after the refrigerant of second cylinder flows into,, apply the suction side pressure of two rotation compressing members as the back pressure of second blade.
In addition, compression system of the present invention has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compressor only suppresses first blade by spring members to first roller, can change and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact, be provided for controlling control valve unit to the refrigerant circulation of second cylinder, in first operation mode, pass through control valve unit, make refrigerant flow into second cylinder, and back pressure as second blade, apply the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure, in second operation mode, pass through control valve unit, prevention flows into refrigerant to second cylinder, and, back pressure as second blade, apply the suction side pressure of two rotation compressing members, simultaneously, from second operation mode when first operation mode is changed, in back pressure as second blade, applied the discharge side pressure of two rotation compressing members after, apply the suction side pressure of two rotation compressing members and discharge intermediate pressure between the side pressure, from first operation mode when second operation mode is changed, cutting off by control valve unit after the refrigerant of second cylinder flows into,, apply the suction side pressure of two rotation compressing members as the back pressure of second blade.
In addition, in compression system of the present invention, when carrying out mode switch in above-mentioned each invention, make the driving element low speed rotation of compression system, multi-cylinder rotary compressor, making the compression ratio of the first rotation compressing member or two rotation compressing members is smaller or equal to 3.0.
According to this invention, from second operation mode during to the conversion of above-mentioned first operation mode, because in back pressure as second blade, after having applied the discharge side pressure of two rotation compressing members, apply the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure, so can make second blade in early days to the second roller side shifting by the discharge side pressure of two rotation compressing members.In view of the above, can improve, improve running efficiency, and can avoid producing the conflict sound of second blade from the tracing ability of second blade of second operation mode when first operation mode is changed.
In addition, in the discharge side pressure that second blade is applied two rotation compressing members, after second blade has been followed second roller, rotate the suction side pressure of compressing members and the intermediate pressure between the discharge side pressure by applying two, the situations that applied the discharge side pressure of two rotation compressing members with back pressure at second blade are compared, because pressure oscillation significantly reduces, so improved the tracing ability of second blade of the compression system, multi-cylinder rotary compressor behind the conversion operation mode, improved the compression efficiency of the second rotation compressing member, and, in first operation mode, can possibly avoid producing the conflict sound of second roller and second blade.
In addition, from first operation mode when second operation mode is changed, because cutting off by control valve unit after the inflow of the refrigerant of second cylinder, back pressure as second blade, apply the suction side pressure of two rotation compressing members, so can make the interior pressure of second cylinder be higher than the back pressure of second blade.In view of the above, second blade pass of compression system, multi-cylinder rotary compressor is crossed the pressure in second cylinder, is pushed to a side opposite with second roller, owing to can not come out in second cylinder, so can possibly avoid conflicting with second roller, produces the such problem of conflict sound.
Like this, by the above-mentioned performance and the reliability that can improve compression system, multi-cylinder rotary compressor, as compression system, can seek to improve significantly performance, this compression system, multi-cylinder rotary compressor can be changed and be used first operation mode and second operation mode, and at above-mentioned first operation mode, the first and second rotation compressing member compresses work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact.
Particularly when translative mode,, make the first rotation compressing member or two compression ratios that rotate compressing members smaller or equal to 3.0, the pressure oscillation in the time of then can being suppressed at the operation mode conversion if make the driving element low speed rotation of compression system, multi-cylinder rotary compressor.
In addition, refrigerating plant of the present invention is to use the compression system of above-mentioned each invention, constitutes cryogen circuit.
According to this invention, because the cryogen circuit of refrigerating plant is to use the compression system of above-mentioned each invention to constitute, so also can seek the improvement of the running efficiency of refrigerating plant integral body.
In addition, the present invention only has by spring members first blade in the compression system of the compression system, multi-cylinder rotary compressor that first roller suppresses, and is purpose with the conflict sound of avoiding producing when the starting second blade.
Promptly, the compression system of this invention has compression system, multi-cylinder rotary compressor, this compressor is in seal container, taking in driving element and rotating compressing member by the rotation shaft-driven first and second of this driving element, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compressor only suppresses first blade by spring members to first roller, when the starting compression system, multi-cylinder rotary compressor, in back pressure as second blade, apply the state starting down of the suction side pressure of two rotation compressing members, simultaneously after starting, back pressure as second blade, apply the discharge side pressure of two rotation compressing members, then, make the back pressure of second blade become the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure.
In addition, in compression system of the present invention, in foregoing invention, compression system, multi-cylinder rotary compressor can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact.
According to this invention, when the starting compression system, multi-cylinder rotary compressor, be in back pressure as second blade, two states that rotate the suction side pressure of compressing members that apply start down, in the second rotation compressing member, do not finish the compression work done in fact.
In addition, after starting,, apply the discharge side pressure of two rotation compressing members, second blade is suppressed to second roller, the compression work done of beginning in the second rotation compressing member as the back pressure of second blade.
Have again, in back pressure as second blade, after having applied the discharge side pressure of two rotation compressing members, become the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure by the back pressure that makes second blade, the situations that applied the discharge side pressure of two rotation compressing members with back pressure at second blade are compared, because pressure oscillation significantly reduces, so tracing ability of second blade of the compression system, multi-cylinder rotary compressor when having improved the common running after starting, improve the compression efficiency of the second rotation compressing member, can possibly avoid producing the conflict sound of second roller and second blade.
Particularly can improve the performance and the reliability of compression system, multi-cylinder rotary compressor, as compression system, can seek to improve significantly performance, this compression system, multi-cylinder rotary compressor can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member to compress work done in fact.
In addition, refrigerating plant of the present invention is to use the compression system of above-mentioned each invention, constitutes cryogen circuit.
According to this invention, the cryogen circuit of refrigerating plant is to use the compression system of above-mentioned each invention to constitute, and also can seek the improvement of the running efficiency of refrigerating plant integral body.
In addition, the present invention be by spring members only with first blade to compression system, multi-cylinder rotary compressor that first roller suppresses and have in the compression system of this compression system, multi-cylinder rotary compressor, to improve the tracing ability of second blade, the conflict sound of avoiding producing second blade is a purpose.
Promptly, the compression system, multi-cylinder rotary compressor of this invention is in seal container, taking in driving element and rotating compressing member by the rotation shaft-driven first and second of this driving element, this first and second rotation compressing member is made of respectively first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compression system, multi-cylinder rotary compressor only suppresses first blade by spring members to first roller, has back pressure chamber, this back pressure chamber is used for second blade is applied back pressure, and it is suppressed to second roller, and this back pressure chamber is as the baffler chamber with regulation spatial volume.
In this invention, be with the baffler chamber of back pressure chamber as spatial volume with regulation, by this spatial volume, reduced the pressure pulse that produces because of snap action to second blade, and, also can reduce the pressure oscillation of the discharge side pressure of the two rotation compressing members that are applied in as the back pressure of second blade.
In view of the above, can improve the tracing ability of second blade, improve the compression efficiency of the second rotation compressing member, and, can do one's utmost to avoid producing the conflict sound of second roller and second blade.
Like this, by above-mentioned performance and the reliability that can seek to improve compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member compresses work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact.
In addition, compression system, multi-cylinder rotary compressor of the present invention is in seal container, taking in driving element and rotating compressing member by the rotation shaft-driven first and second of this driving element, this first and second rotation compressing member is made of respectively first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compression system, multi-cylinder rotary compressor only suppresses first blade by spring members to first roller, have the back pressure path that is used for second blade is applied back pressure, make this back pressure with the cross-section area of path mean value more than or equal to the surface area that exposes second blade in second cylinder.
In this invention, by making back pressure with the cross-section area of path mean value more than or equal to the surface area that exposes second blade in second cylinder, can guarantee this back pressure path fully, reduce the pressure pulse that produces because of snap action to second blade, and, also can reduce as the back pressure of second blade and the pressure oscillation of the refrigerant that is applied in.
In view of the above, can improve the tracing ability of second blade, improve the compression efficiency of the second rotation compressing member, and, can do one's utmost to avoid producing the conflict sound of second roller and second blade.
By above-mentioned, can seek to improve the performance and the reliability of compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor only suppresses first blade by spring members to first roller.
In addition, compression system, multi-cylinder rotary compressor of the present invention is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compression system, multi-cylinder rotary compressor suppresses first blade by spring members to first roller, can change and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at second operation mode, have only the first rotation compressing member to compress work done in fact, be provided with second blade is suppressed mechanism to what second roller suppressed, make this elastic force pressure that suppresses mechanism smaller or equal to two rotation compressing members, or the suction side pressure of the first rotation compressing member apply the elastic force pressure under the situation as the back pressure of second blade.
In addition, in compression system, multi-cylinder rotary compressor of the present invention, in foregoing invention, be provided for controlling control valve unit to the refrigerant circulation of second cylinder, in first operation mode, by control valve unit, make refrigerant flow into second cylinder, and as the back pressure of second blade, apply the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure, or apply the two discharge side pressure of rotating compressing members, in second operation mode, pass through control valve unit, cut-out flows into refrigerant to second cylinder, and,, apply the suction side pressure of two rotation compressing members as the back pressure of second blade.
In addition, compression system of the present invention has compression system, multi-cylinder rotary compressor, this compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compressor only suppresses first blade by spring members to first roller, can change and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact, be provided for controlling control valve unit to the refrigerant circulation of second cylinder, with second blade is suppressed mechanism to what second roller suppressed, make this elastic force pressure that suppresses mechanism smaller or equal to two rotation compressing members, or the suction side pressure of the first rotation compressing member applies the elastic force pressure under the situation as the back pressure of second blade, simultaneously, in first operation mode, pass through control valve unit, make refrigerant flow into second cylinder, and back pressure as second blade, apply the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure, or apply the two discharge side pressure of rotating compressing members, in second operation mode, pass through control valve unit, cut-out flows into refrigerant to second cylinder, and,, apply the suction side pressure of two rotation compressing members as the back pressure of second blade.
In addition, compression system, multi-cylinder rotary compressor of the present invention is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on running shaft, eccentric rotation in each cylinder respectively; This first and second blade contacts with this first and second roller, low pressure chamber side and hyperbaric chamber side will be divided into respectively in each cylinder, simultaneously, this compression system, multi-cylinder rotary compressor suppresses first blade by spring members to first roller, can change and be used first operation mode and second operation mode, at above-mentioned first operation mode, two rotation compressing members compress work done, at above-mentioned second operation mode, have only the first rotation compressing member to compress work done in fact, opposite side in the second roller side of second blade, the weak spring that tensile load is used is set, the tensile force that makes this weak spring is smaller or equal to two rotation compressing members, or the suction side pressure of the first rotation compressing member applies the elastic force pressure under the situation as the back pressure of second blade.
According to this invention, for example,, can improve the tracing ability of second blade in first operation mode by the mechanism of suppressing that constitutes by weak spring etc.Particularly, under first operation mode, passing through control valve unit, make refrigerant flow into second cylinder, and, as the back pressure of second blade, the suction side pressure of two rotation compressing members and the intermediate pressure between the discharge side pressure have been applied, or when having applied the discharge side pressure of two rotation compressing members, can suppress mechanism by this, possibly avoid because this intermediate pressure or the tracing ability of discharging second blade that the pressure pulse of side pressure causes worsen such problem.
In addition, by making the elastic force pressure that suppresses mechanism smaller or equal to two rotation compressing members, or the suction side pressure of the first rotation compressing member applies the elastic force pressure under the situation as the back pressure of second blade, in second operation mode, pass through control valve unit, cut-out flows into refrigerant to second cylinder, and, back pressure as second blade, apply the suction side pressure of two rotation compressing members, can be by the pressure in second cylinder, make elastic force pressure that second blade is suppressed to the back pressure side greater than the suction side pressure that second blade is suppressed to second roller with suppress the elastic force pressure of mechanism.
In view of the above, even be provided with second blade under the situation of suppressing mechanism that second roller suppresses, in second operation mode, even be provided with under the situation of suppressing parts, because the pressure in second cylinder, second blade of compression system, multi-cylinder rotary compressor can not come out in second cylinder yet, so can possibly avoid conflicting with second roller, produces the problem of conflict sound.
Like this, by above-mentioned, can improve the performance and the reliability of compression system, multi-cylinder rotary compressor, as compression system, seek to improve significantly performance, this compression system, multi-cylinder rotary compressor can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member to compress work done in fact.
In addition, because the weak spring that tension load is used, in second operation mode, owing to pass through the tensile force of this weak spring, second blade can not come out in second cylinder, so can possibly avoid conflicting with second roller, produces the problem of conflict sound.
Description of drawings
Fig. 1 is the vertical profile side view of compression system, multi-cylinder rotary compressor of the compression system of embodiments of the invention.
Fig. 2 is another vertical profile side view of the compression system, multi-cylinder rotary compressor of Fig. 1.
Fig. 3 has been to use the figure of cryogen circuit of air conditioner of the compression system of embodiments of the invention.
Fig. 4 is switching motion is carried out in expression to first operation mode from second operation mode of the compression system, multi-cylinder rotary compressor of Fig. 1 figure.
Fig. 5 is the vertical profile side view of compression system, multi-cylinder rotary compressor of the compression system of embodiments of the invention 2.
Fig. 6 is switching motion is carried out in expression to second operation mode from first operation mode of the compression system, multi-cylinder rotary compressor of Fig. 5 figure.
Fig. 7 is switching motion is carried out in expression to first operation mode from second operation mode of the compression system, multi-cylinder rotary compressor of Fig. 5 figure.
Fig. 8 is the vertical profile side view of compression system, multi-cylinder rotary compressor of the compression system of embodiments of the invention 3.
Fig. 9 is the figure that is illustrated in the action of each solenoid valve in second operation mode of compression system, multi-cylinder rotary compressor of compression system of embodiments of the invention 5.
Figure 10 is the vertical profile side view of the compression system, multi-cylinder rotary compressor of embodiments of the invention 7.
Figure 11 is the embodiment's 8 of compression system, multi-cylinder rotary compressor the vertical view cutaway drawing of second cylinder.
Figure 12 is the vertical view cutaway drawing that the embodiment's 11 of compression system, multi-cylinder rotary compressor of the present invention second second roller that rotates compressing member is positioned at second cylinder of top dead center situation.
Figure 13 is the vertical view cutaway drawing that the embodiment's 11 of compression system, multi-cylinder rotary compressor of the present invention second second roller that rotates compressing member is positioned at second cylinder of lower dead center situation.
Figure 14 is the vertical profile side view of the compression system, multi-cylinder rotary compressor of embodiments of the invention 14.
Figure 15 is another vertical profile side view of the compression system, multi-cylinder rotary compressor of Figure 14.
Figure 16 is the vertical view cutaway drawing of second cylinder of the second rotation compressing member of the compression system, multi-cylinder rotary compressor of Figure 14.
Figure 17 has been to use the figure of cryogen circuit of air conditioner of the compression system of embodiments of the invention 14.
Figure 18 is the figure that flows that is illustrated in the refrigerant in embodiment 14 first operation mode of compression system, multi-cylinder rotary compressor.
Figure 19 is the figure that flows that is illustrated in the refrigerant in embodiment 14 second operation mode of compression system, multi-cylinder rotary compressor.
Figure 20 is the figure that flows that is illustrated in the refrigerant in other embodiment's first operation mode of compression system, multi-cylinder rotary compressor.
Figure 21 is the vertical profile side view of the compression system, multi-cylinder rotary compressor of embodiments of the invention 15.
Figure 22 is another vertical profile side view of the compression system, multi-cylinder rotary compressor of Figure 21.
Figure 23 is the enlarged view of weak spring of the second rotation compressing member of the compression system, multi-cylinder rotary compressor of Figure 21.
Figure 24 is other embodiment's the enlarged view of weak spring of the second rotation compressing member of the compression system, multi-cylinder rotary compressor of Figure 23.
Figure 25 is another other embodiment's the enlarged view of weak spring of the second rotation compressing member of the compression system, multi-cylinder rotary compressor of Figure 23.
Embodiment
Below, with reference to the accompanying drawings, be described in detail embodiments of the present invention.
(embodiment 1)
Being respectively Fig. 1 is the embodiment of expression as the compression system, multi-cylinder rotary compressor of compression system CS of the present invention, have the vertical profile side view of rotary compressor 10 of the internal high pressure type of the first and second rotation compressing member, Fig. 2 is the vertical profile side view (representing the section different with Fig. 1) of the rotary compressor 10 of presentation graphs 1.In addition, the compression system CS of present embodiment is a part that constitutes as to the cryogen circuit of the air conditioner of the indoor refrigerating plant that carries out air conditioning.
In each figure, embodiment's rotary compressor 10 is rotary compressors of internal high pressure type, in the longitudinal type that constitutes by steel plate seal container 12 cylindraceous, taking in electric element 14 and rotary compressor structure portion 18, this electric element 14 is the driving elements as the upside of the inner space that is configured in sealing container 12, this rotary compressor structure portion 18 is made of the first and second rotation compressing member 32,34, this first and second rotation compressing member 32,34 is configured in the downside of this electric element 14, and the running shaft 16 by electric element 14 is driven.
Seal container 12 with the bottom as the machine oil groove, by the container body 12A that is taking in electric element 14 and rotary compressor structure portion 18, constitute with roughly bowl-shape end cap (lid) 12B of the upper opening that seals this container body 12A, and, on this end cap 12B, form circular mounting hole 12D, on this mounting hole 12D, the wiring terminal (omission distribution) 20 that is used for to electric element 14 supply capabilities is installed.
In addition, refrigerant discharge tube 96 described later is installed on end cap 12B, an end of this refrigerant ingress pipe 96 and 12 interior connections of seal container.And, installation pedestal 11 is set in the bottom of seal container 12.
Electric element 14 is by the inner peripheral surface along the upper space of seal container 12, the fixing stator 22 of welding and in the inboard of this stator 22 annularly is provided with some intervals and inserts that the rotor 24 that is provided with constitutes, this rotor 24 is fixed on the center of passing, vertically on the running shaft 16 of Yan Shening.
Said stator 22 have lamination 26 that the electromagnetic steel plate lamination with ring-type forms and by string around (winding with one heart) mode, be wrapped in the stator coil 28 of the tooth portion of this lamination 26.In addition, rotor 24 is also same with stator 22, is that the lamination 30 by electromagnetic steel plate forms.
Between the above-mentioned first rotation compressing member 32 and the second rotation compressing member 34, intermediate clapboard 36 in clamping.Promptly, first the rotation compressing member 32 and second the rotation compressing member 34 constitute by intermediate clapboard 36, first and second cylinder 38,40, first and second roller 46,48, first and second blade 50,52, upper support member 54 and lower support member 56, this first and second cylinder 38,40 be configured in this intermediate clapboard 36 about; This first and second roller 46,48 has the phase difference of 180 degree in this first and second cylinder 38,40, be entrenched on the eccentric part up and down 42,44 that is arranged on the running shaft 16 eccentric respectively rotation in each cylinder 38,40; This first and second blade 50,52 contacts with this first and second roller 46,48, will be divided into low pressure chamber side and hyperbaric chamber side respectively in each cylinder 38,40; The upside opening surface of this upper support member 54 and lower support member 56 sealings first cylinder 38 and the open lower side face of second cylinder 40 are as the supporting part of the bearing that is also used as running shaft 16.
On above-mentioned first and second cylinder 38,40, the suction path 58,60 with these first and second cylinder, 38,40 internal communication is set respectively, suck on path 58,60 at this, connecting refrigerant ingress pipe 92,94 described later respectively.
In addition, be provided with at the upside of upper support member 54 and discharge anechoic chamber 62, be discharged to this discharge anechoic chamber 62 by the refrigerant gas of the first rotation compressing member, 32 compressions.This discharge anechoic chamber 62 is formed in the roughly bowl-shape cap assembly 63, the hole that the upper support member 54 that is used for running shaft 16 and is also used as the bearing of running shaft 16 of this cap assembly 63 having at the center runs through covers electric element 14 sides (upside) of upper support member 54.Then, above cap assembly 63, leave the interval of regulation, electric element 14 is set with cap assembly 63.
On lower support member 56, be provided with and discharge anechoic chamber 64, this discharges anechoic chamber 64 is by being used as the lid of wall, seals the depressed part of the downside that is formed on this lower support member 56 and forms.That is, discharging anechoic chamber 64 is closed by dividing the lower cover 68 of discharging anechoic chamber 64.
On above-mentioned first cylinder 38, form the steering channel 70 of taking in above-mentioned first blade 50, in the outside of this steering channel 70, that is,, form the container 70A that takes in as the spring 74 of spring members in the back side of first blade 50.This spring 74 contacts with the back side end of first blade 50, always first blade 50 is suppressed to first roller, 46 sides.In addition, on the 70A of container, for example also import the discharge side pressure described later (high pressure) in the seal container 12, be applied in as the back pressure of first blade 50.Like this, this container 70A is at steering channel 70 sides and seal container 12 (container body 12A) side opening, and seal container 12 sides at the spring 74 that is accommodated in container 70A are provided with metal embolism 137, to reach the effect that prevents that spring 74 from coming off.
In addition, on above-mentioned second cylinder 40, form the steering channel 72 of taking in second blade 52,, that is,, form back pressure chamber 72A in the back side of second blade 52 in the outside of this steering channel 72.This back pressure chamber 72A is connecting pipe arrangement 75 described later at steering channel 72 sides and seal container 12 side openings on the opening of sealing container 12 sides, sealed in seal container 12.
In the side of the container body 12A of seal container 12, with suction path 58, the 60 corresponding positions of first cylinder 38 and second cylinder 40 on, sliding sleeve 141 and 142 are being fixed in welding respectively.These sliding sleeves 141 and 142 are adjacency up and down.
Like this, in sliding sleeve 141, insert the end that connection is used for refrigerant gas is imported the refrigerant ingress pipe 92 of first cylinder 38, an end of this refrigerant ingress pipe 92 is communicated with the suction path 58 of upper cylinder half 38.The other end of this refrigerant ingress pipe 92 is at accumulator 146 inner openings.
In sliding sleeve 142, insert the end that connection is used for refrigerant gas is imported the refrigerant ingress pipe 94 of second cylinder 40, an end of this refrigerant ingress pipe 94 is communicated with the suction path 60 of second cylinder 40.The other end of this refrigerant ingress pipe 94 is identical with above-mentioned refrigerant ingress pipe 92, at accumulator 146 inner openings.
Above-mentioned accumulator 146 is the jars that the refrigerant that sucks carried out gas-liquid separation, by carriage 147, is installed in the upper side of the container body 12A of seal container 12.Like this, on accumulator 146, be inserted with refrigerant ingress pipe 92 and refrigerant ingress pipe 94 from the bottom, in this accumulator 146 above, the opening of the other end is in place respectively.In addition, an end of refrigerant pipe arrangement 100 inserts the top in the accumulator 146.
In addition, discharge anechoic chamber 64 and discharge anechoic chamber 62 by access 120 connections, this access 120 connects the supporting part 54,56 and first and second cylinder 38,40 and the intermediate clapboard 36 up and down at axis direction (above-below direction).Like this, by 34 compressions of the second rotation compressing member, the refrigerant gas that is discharged to the High Temperature High Pressure of discharging anechoic chamber 64 is discharged to by this access 120 discharges anechoic chamber 62, with the refrigerant gas interflow of the High Temperature High Pressure of being compressed by the first rotation compressing member 32.
In addition, the not shown hole that goes out of discharging in anechoic chamber 62 and the seal container 12 by connecting cap assembly 63 is communicated with, by the first rotation compressing member 32 and 34 compressions of the second rotation compressing member, the refrigerant gas that is discharged to the high pressure of discharging anechoic chamber 62 is discharged in the seal container 12 from this hole.
, at the middle part of above-mentioned refrigerant pipe arrangement 100, be connected with refrigerant pipe arrangement 101 here, this pipe arrangement is by solenoid valve 105, is connected with above-mentioned pipe arrangement 75.In addition,, also be connected with refrigerant pipe arrangement 102 at the middle part of above-mentioned refrigerant discharge tube 96, same with above-mentioned refrigerant pipe arrangement 101, by solenoid valve 106, be connected with above-mentioned pipe arrangement 75.In addition, by controller 210 described later, control the switching of these solenoid valves 105,106 respectively.That is, if by controller 210 control valve unit 105 is left, control valve unit 106 closes, and then refrigerant pipe arrangement 101 and pipe arrangement 75 are communicated with.In view of the above, flow in refrigerant pipe arrangement 100, two parts of rotating the suction side refrigerant of compressing members 32,34 that flow into to accumulator 146 enter refrigerant pipe arrangement 101, flow into back pressure chamber 72A from pipe arrangement 75.In view of the above, as the back pressure of second blade 52, apply the suction side pressure of two rotation compressing members 32,34.
In addition, if by controller 210 control valve unit 105 is closed, control valve unit 106 leaves, and then refrigerant discharge tube 96 and pipe arrangement 75 are communicated with.In view of the above, be discharged from, rotate the part process refrigerant pipe arrangement 102 of the discharge side refrigerant of compressing members 32,34 from seal container 12, flow into back pressure chamber 72A from pipe arrangement 75 by two of refrigerant discharge tube 96.In view of the above, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
Here, above-mentioned controller 210 is the parts that constitute the part of compression system CS of the present invention, the revolution of the electric element 14 of control rotary compressor 10.In addition, as mentioned above, control the switching of solenoid valve 106 of solenoid valve 105, the refrigerant pipe arrangement 102 of above-mentioned refrigerant pipe arrangement 101.
Then, Fig. 3 is that expression is used compression system CS and the figure of the cryogen circuit of the above-mentioned air conditioner that constitutes.That is, embodiment's compression system CS constitutes the part of the cryogen circuit of air conditioner shown in Figure 3, is to be made of above-mentioned rotary compressor 10 and controller 210 etc.The refrigerant discharge tube 96 of rotary compressor 10 is connected with the inlet of outdoor heat exchanger 152.Above-mentioned controller 210 and rotary compressor 10, outdoor heat exchanger 152 are arranged on the not shown outdoor unit that goes out of air conditioner.The pipe arrangement that is connected the outlet of this outdoor heat exchanger 152 is connected with expansion valve 154 as the mechanism of decompressor, and the pipe arrangement that comes out from expansion valve 154 is connected with indoor side heat exchanger 156.These expansion valves 154 and indoor side heat exchanger 156 are arranged on the not shown indoor set that goes out of air conditioner.In addition, the above-mentioned refrigerant pipe arrangement 100 that is connecting rotary compressor 10 at the outlet side of indoor side heat exchanger 156.
In addition,, use the refrigerant of HFC or HC class,, use for example existing machine oil such as mineral oil (oil), alkymer, ether oil, ester oil as the machine oil of lubricant oil as refrigerant.
With above-mentioned formation, the action of rotary compressor 10 is described then.
(1) first operation mode (load or the running during high load usually)
At first, first operation mode that compresses work done with regard to two rotation compressing members 32,34 describes.According to the above-mentioned running instruction input that is arranged on the controller of the not shown indoor pusher side that goes out on the indoor set, the revolution of the electric element 14 of controller 210 control rotary compressors 10, simultaneously indoor be usually under the situation of load or higher load condition, controller 210 implementations first operation mode.Under this first operation mode, controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101 and the solenoid valve 106 of refrigerant pipe arrangement 102.
Like this, if by wiring terminal 20 and the not shown distribution that goes out, to stator coil 28 energisings of electric element 14, then electric element 14 startings, rotor 24 rotations.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.As mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 100 is closed, thus can not flow into pipe arrangement 75 by the refrigerant of refrigerant pipe arrangement 100, but all flow in the accumulator 146.
Like this, having flow into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in each refrigerant discharge tube 92,94 of this accumulator 146 inner openings.The refrigerant gas process that has entered the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.
On the other hand, the refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 94 sucks path 60, is inhaled into the low pressure chamber side of second cylinder 40 of the second rotation compressing member 34.The action of refrigerant gas by second roller 48 and second blade 52 that is inhaled into the low pressure chamber side of second cylinder 40 is compressed.
At this moment, as mentioned above, because solenoid valve 105 and solenoid valve 106 are closed, so be seal space in the pipe arrangement 75 that is communicated with the back pressure chamber 72A of second blade 52.Have again, because the refrigerant in a lot of second cylinders 40 flows into the back pressure chamber 72A between second blade 52 and container 70A, so the pressure in the back pressure chamber 72A of second blade 52 becomes the suction side pressure of two rotation compressing members 32,34 and discharges intermediate pressure between the side pressure, this intermediate pressure becomes the state that is applied in as the back pressure of second blade 52.Because this intermediate pressure does not use spring members, second blade 52 can be suppressed fully to second roller 48.
In addition, in the past, though, applied high pressure as the discharge side pressure of two rotation compressing members 32,34 as the back pressure of second blade 52, but in this case, there is following problems, that is, because the pulse of discharge side pressure is big, and there is not a spring members, so because this pulse causes the tracing ability of second blade 52 to worsen, compression efficiency reduces, and between second blade 52 and second roller 48, produce the conflict sound.
But, as the back pressure of second blade 52, rotate the suction side pressure of compressing members 32,34 and the intermediate pressure between the discharge side pressure by applying two, to compare with having applied the situation of discharging side pressure as mentioned above, pressure pulse significantly reduces.Particularly in the present embodiment, close solenoid valve 105,106 because be, rotate the suction side refrigerant of compressing members 32,34 and discharge the state that side refrigerant flows into from pipe arrangement 75 as cutting off two, so can suppress the pulse of the back pressure of second blade 52 better.In view of the above, improve the tracing ability of second blade 52 in first operation mode, also improved the compression efficiency of the second rotation compressing member 34.
In addition, be compacted into the refrigerant gas of High Temperature High Pressure, by in the not shown exhaust port that goes out, be discharged to and discharge in the anechoic chamber 64 from the hyperbaric chamber side of second cylinder 40 by the action of second roller 48 and second blade 52.The refrigerant gas that is discharged to discharge anechoic chamber 64 is discharged to and discharges in the anechoic chamber 62 via above-mentioned access 120, with the refrigerant gas interflow of being compressed by the above-mentioned first rotation compressing member 32.Like this, the refrigerant gas at interflow is discharged in the seal container 12 by connecting the not shown hole that goes out of cap assembly 63.
Then, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flow in the outdoor heat exchanger 152.Refrigerant gas heat release here after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.Here, the refrigerant evaporation at this moment, by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
(2) second operation modes (runnings of light hours)
Then, describe with regard to second operation mode.Controller 210 indoor be under the situation of light load state, be transformed into second operation mode.This second operation mode comes down to have only the first rotation compressing member 32 to compress the pattern of work done, is to be light load indoor, and in above-mentioned first operation mode, the operation mode of electric element 14 for carrying out under the situation of low speed rotation.Little ability zone at compression system CS, by having only the first rotation compressing member 32 to compress work done in fact, compare with the situation of compressing work done by first and second liang of cylinder 38,40, owing to can reduce the amount of the refrigerant gas of compression, so should measure also in the light hours, the revolution of electric element 14 is risen, improved the running efficiency of electric element 14, and also make the leakage loss that reduces refrigerant become possibility.
In this case, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101, closes the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 75 are communicated with, and the suction side refrigerant of the first rotation compressing member 32 flows among the back pressure chamber 72A, and as the back pressure of second blade 52, the suction side pressure of the first rotation compressing member 32 is applied in.
On the other hand, controller 210 to stator coil 28 energisings of electric element 14, makes rotor 24 rotations of electric element 14 by aforesaid wiring terminal 20 and the not shown distribution that goes out.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.At this moment, as mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 101 is opened, so the part of the refrigerant of the suction side of the first rotation compressing member 32 by refrigerant pipe arrangement 100 flows into the back pressure chamber 72A through pipe arrangements 75 from refrigerant pipe arrangement 101.In view of the above, back pressure chamber 72A becomes the suction side pressure of the first rotation compressing member 32, and as the back pressure of second blade 52, the suction side pressure of this first rotation compressing member 32 is applied in.
Here because as second the rotation compressing member 34 back pressure and be applied in two the rotation compressing members 32,34 suction side pressures be low pressure, so second blade 52 can not be suppressed to second roller 48.Therefore, in the second rotation compressing member 34, not compressing work done in fact, only is to be provided with first of spring 74 to rotate the compression work done that compressing member 32 is finished refrigerant.
On the other hand, flowing into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in the refrigerant discharge tube 92 of this accumulator 146 inner openings.The refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.At this moment, because in this second operation mode, discharge anechoic chamber 62 and bring into play function, discharge anechoic chamber 64 and bring into play function, so can be reduced in the pressure pulse of compressed refrigerant in the first rotation compressing member 32 more as the anechoic chamber of sympathetic response type as the anechoic chamber of intumescent.In view of the above, substantially have only the first rotation compressing member 32 to compress in second operation mode of work done, can improve erasure effect more.
Be discharged to the refrigerant gas of discharging anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.Then, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Refrigerant gas heat release here after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.By this indoor side heat exchanger 156 refrigerant evaporation,, bring into play cooling action, to indoor refrigeration by from the air of indoor circulation, absorbing heat.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
(3) from of the conversion of second operation mode to first operation mode
On the other hand, become common load or higher load condition as if indoor from above-mentioned light load state, then controller 210 is changed to first operation mode from second operation mode.For from the switching motion of second operation mode, use Fig. 4 to describe here, to first operation mode.In this case, controller 210 is controlled, and makes electric element 14 low speed rotation (revolution is smaller or equal to 50Hz), and the compression ratio that makes two rotation compressing members 32,34 is smaller or equal to 3.0.In addition, controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101, opens the solenoid valve 106 (Fig. 4 (2)) of refrigerant pipe arrangement 102.
In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 75 are communicated with, and the discharge side refrigerant of two rotation compressing members 32,34 flows among the back pressure chamber 72A, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
Back pressure as second blade 52, by applying the discharge side pressure of two rotation compressing members 32,34, owing to compare in the back pressure chamber 72A of second blade 52 and second cylinder 40, become significant high pressure, so second blade 52 is by this high pressure of back pressure chamber 72A, be pushed to second roller, 48 sides, follow.
As the back pressure of second blade 52,, second blade 52 can be released fully second roller, 48 sides during conversion here, by applying the discharge side pressure of two rotation compressing members.Promptly, from second operation mode when first operation mode is changed, back pressure as second blade 52, during as the common running of the first above-mentioned operation mode, under the situation of the intermediate pressure between suction side pressure that applies two rotation compressing members 32,34 and the discharge side pressure, in this intermediate pressure, because the pressure difference with back pressure chamber 72A in second cylinder 40 is few, so follow very spended time of second roller 48 until second blade 52, second blade 52 and 48 conflicts of second roller have produced the such problem of sound that clashes betwixt.
But, in the present invention, from second operation mode when first operation mode is changed, back pressure as second blade 52, by applying the discharge side pressure of two rotation compressing members 32,34, can discharge side pressure by this, second blade 52 is suppressed fully to second roller, 48 sides, second roller 48 is followed in early days.
In view of the above, improve, improve running efficiency, and can avoid the generation of the conflict sound of second blade 52 from the tracing ability of second blade 52 of second operation mode when the conversion of first operation mode.
In addition, when conversion, controller 210 is controlled, and makes electric element 14 low speed rotation (revolution is smaller or equal to 50Hz), and the compression ratio that makes two rotation compressing members 32,34 is smaller or equal to 3.0.In view of the above, because can suppress pressure oscillation,, also be difficult to be subjected to the influence of this pressure oscillation so, applied under the situation of discharge side pressure of two rotation compressing members 32,34 even in back pressure as the second rotation compressing member 34.
In addition, controller 210 is in the discharge side pressure that second blade 52 is applied two rotation compressing members 32,34, after making second blade 52 follow second roller 48, apply the suction side pressure of two rotation compressing members 32,34 and the intermediate pressure (Fig. 4 (3)) between the discharge side pressure.In view of the above, because as mentioned above, comparing with the situation of the discharge side pressure that on the back pressure of second blade 52, has applied two rotation compressing members 32,34, can reduce pressure oscillation significantly, so can improve the tracing ability of second blade 52 of the rotary compressor 10 after the conversion in operation mode, improve the compression efficiency of the second rotation compressing member 34, and, in first operation mode, can possibly avoid producing the conflict sound of second roller 48 and second blade 52.
As above detailed description, according to the present invention, can seek to improve performance and the reliability of the compression system CS with rotary compressor 10, this rotary compressor 10 can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member 32,34 compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member 32 to compress work done in fact.
In view of the above,, constitute the cryogen circuit of air conditioner, can improve the running efficiency and the performance of this air conditioner, also can seek to reduce consumption electric power by using this compression system CS.
(embodiment 2)
Then, other embodiments with regard to compression system CS of the present invention describe.Fig. 5 be expression as the compression system, multi-cylinder rotary compressor of the compression system CS under this situation, have the vertical profile side view of rotary compressor 110 of the internal high pressure type of the first and second rotation compressing member.In addition, in Fig. 5, the parts of having given the symbol identical with Fig. 1 to Fig. 4 are the parts that can produce identical or similar effect.
In Fig. 5, the 200th, control valve unit at the outlet side of accumulator 146, is arranged on the middle part of refrigerant ingress pipe 94 of the inlet side of seal container 12.This solenoid valve 200 is to be used to control the control valve unit that refrigerant flows into to second cylinder 40, by above-mentioned controller 210 controls as control gear.
In addition, same as the previously described embodiments as refrigerant in the present embodiment, the refrigerant of use HFC or HC class as the machine oil of lubricant oil, uses for example existing machine oil such as mineral oil (oil), alkymer, ether oil, ester oil.
With above-mentioned formation, the action of rotary compressor 110 is described then.
(1) first operation mode (load or the running during high load usually)
At first, first operation mode that compresses work done with regard to two rotation compressing members 32,34 describes.According to the above-mentioned running instruction input that is arranged on the controller of the not shown indoor pusher side that goes out on the indoor set, the revolution of the electric element 14 of controller 210 control rotary compressors 110, simultaneously, indoor be usually that controller 210 is carried out first operation mode under the situation of load or higher load condition.Under this first operation mode, controller 210 is opened the solenoid valve 200 of refrigerant ingress pipe 94, closes the solenoid valve 105 of refrigerant pipe arrangement 101 and the solenoid valve 106 of refrigerant pipe arrangement 102.
Like this, if by wiring terminal 20 and the not shown distribution that goes out, to stator coil 28 energisings of electric element 14, then electric element 14 startings, rotor 24 rotations.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 110.As mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 101 is closed, thus can not flow into pipe arrangement 75 by the refrigerant of refrigerant pipe arrangement 100, but all flow in the accumulator 146.
Like this, having flow into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in each refrigerant discharge tube 92,94 of this accumulator 146 inner openings.The refrigerant gas process that has entered the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.
On the other hand, the refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 94 sucks path 60, is inhaled into the low pressure chamber side of second cylinder 40 of the second rotation compressing member 34.The action of refrigerant gas by second roller 48 and second blade 52 that is inhaled into the low pressure chamber side of second cylinder 40 is compressed.
At this moment, as mentioned above, because solenoid valve 105 and solenoid valve 106 are closed, so be seal space in the pipe arrangement 75 that is communicated with the back pressure chamber 72A of second blade 52.Have again, because the refrigerant in many second cylinders 40 flows into the back pressure chamber 72A between second blade 52 and container 70A, so the pressure in the back pressure chamber 72A of second blade 52 becomes the suction side pressure of two rotation compressing members 32,34 and discharges intermediate pressure between the side pressure, this intermediate pressure becomes the state that is applied in as the back pressure of second blade 52.Because this intermediate pressure does not use spring members, promptly second blade 52 can be suppressed fully to second roller 48.
In view of the above, same as the previously described embodiments, improved the tracing ability of second blade 52 in first operation mode, also can seek to improve the compression efficiency of the second rotation compressing member 34.
In addition, be compacted into the refrigerant gas of High Temperature High Pressure, by in the not shown exhaust port that goes out, be discharged to and discharge in the anechoic chamber 64 from the hyperbaric chamber side of second cylinder 40 by the action of second roller 48 and second blade 52.The refrigerant gas that is discharged to discharge anechoic chamber 64 is discharged to and discharges in the anechoic chamber 62 via above-mentioned access 120, with the refrigerant gas interflow of being compressed by the above-mentioned first rotation compressing member 32.Like this, the refrigerant gas at interflow is discharged in the seal container 12 by connecting the not shown hole that goes out of cap assembly 63.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Here, the refrigerant gas heat release after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.By this indoor side heat exchanger 156, the refrigerant evaporation by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 110.
(2) from of the conversion of first operation mode to second operation mode
Then, become the light load state as if indoor from above-mentioned common load or higher load condition, then controller 210 is changed to second operation mode from first operation mode.
For from the switching motion of first operation mode, use Fig. 6 to describe here, to second operation mode.In addition, when mode switch, controller 210 is controlled, and makes electric element 14 by low speed rotation, for example, makes revolution smaller or equal to 50Hz, and the compression ratio that makes two rotation compressing members 32 is smaller or equal to 3.0.
At first, controller 210 is closed above-mentioned solenoid valve 200, cuts off the inflow (Fig. 6 (2)) to the refrigerant of second cylinder 40.In view of the above, in the second rotation compressing member 34, do not finish the compression work done.If the inflow to the refrigerant of second cylinder 40 is prevented from, then in second cylinder 40, become the pressure higher slightly (because second roller, 48 rotations than the suction side pressure of above-mentioned two rotation compressing members 32,34, and, high pressure in the seal container 12 is from the inflows slightly such as gap of second cylinder 40, so in second cylinder 40, be the pressure higher slightly) than suction side pressure.
In addition, because under above-mentioned first operation mode, pressure in the aforesaid back pressure chamber 72A becomes the suction side pressure of two rotation compressing members 32,34 and the intermediate pressure between the discharge side pressure, so the pressure in the back pressure chamber 72A of the pressure in second cylinder 40 and second blade 52 is roughly the same pressure.
Then, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101.In addition, the solenoid valve 106 of refrigerant pipe arrangement 102 is a closing state (Fig. 6 (3)) like this.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 75 are communicated with, and the suction side refrigerant of the first rotation compressing member 32 flows among the back pressure chamber 72A, as the back pressure of second blade 52, apply the suction side pressure of the first rotation compressing member 32.
In view of the above, the part of the suction side refrigerant of the first rotation compressing member 32 by refrigerant pipe arrangement 100 flows into the back pressure chamber 72A through pipe arrangements 75 from refrigerant pipe arrangement 101.In view of the above, back pressure chamber 72A becomes the suction side pressure of the first rotation compressing member 32, as the back pressure of second blade 52, applies the suction side pressure of this first rotation compressing member 32.
Because aforesaid second cylinder 40 becomes the high pressure of suction side pressure than the first rotation compressing member 32, so back pressure as second blade 52, by applying the suction side pressure of the first rotation compressing member 32, can make the pressure of second cylinder 40 be higher than the back pressure chamber 72A of second blade 52.Therefore, second blade 52 is because the pressure in second cylinder 40, is pushed to the back pressure chamber 72A side that becomes with the opposite side of second roller 48, is incorporated in the steering channel 72.In view of the above, because when second operation mode change, second blade 52 can be introduced in second cylinder 40 in early days, it is housed in the steering channel 72, so can possibly avoid conflicting of second blade 52 and second roller 48, the generation such problem of sound of conflicting.
(3) second operation modes
Then, just the action of the rotary compressor in second operation mode 110 describes.After flowing into low-pressure refrigerants in the accumulator 146 and carry out gas-liquid separation here from the refrigerant pipe arrangement 100 of rotary compressor 110, only be that refrigerant gas enters in the refrigerant discharge tube 92 of this accumulator 146 inner openings.The refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.Be discharged to the refrigerant gas of discharging anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Here, the refrigerant gas heat release after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.Here, the refrigerant evaporation at this moment, by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out refrigerant is discharged, is drawn into from indoor side heat exchanger 156 circulation of rotary compressor 110 repeatedly.
In addition, in this second operation mode, controller 210 is by closing above-mentioned solenoid valve 200, with the state running of prevention to the inflow of the refrigerant of second cylinder 40, in second operation mode, the pressure in second cylinder 40 is maintained at the state higher than the back pressure of second blade 52 like this.Therefore, second blade 52 can not come out in second cylinder 40 because the pressure in second cylinder 40 is pushed to the back pressure chamber 72A side that becomes with second roller, 48 opposite sides.In view of the above, in the running of second operation mode, can possibly avoid second blade 52 in second cylinder 40, to come out, conflict, produce the such problem of conflict sound with second roller 48.
(4) from of the conversion of second operation mode to first operation mode
On the other hand, become common load or higher load condition as if indoor from above-mentioned light load state, then controller 210 is changed to first operation mode from second operation mode.For from the switching motion of second operation mode, use Fig. 7 to describe here, to first operation mode.In this case, controller 210 is opened solenoid valve 200, makes refrigerant flow into second cylinder 40, simultaneously, closes the solenoid valve 105 of refrigerant pipe arrangement 101, opens the solenoid valve 106 (Fig. 7 (2)) of refrigerant pipe arrangement 102.
In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 75 are communicated with, and the discharge side refrigerant of two rotation compressing members 32,34 flows among the back pressure chamber 72A, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
Back pressure as second blade 52, by applying the discharge side pressure of two rotation compressing members 32,34, owing to be in a ratio of significant high pressure in the back pressure chamber of second blade 52 and second cylinder 40, second blade 52 is by this high pressure of back pressure chamber 72A, be pushed to second roller, 48 sides, follow.
Here, as the back pressure of second blade 52,, second blade 52 can be released fully to the second roller side during conversion by applying the discharge side pressure of two rotation compressing members.Promptly, from second operation mode when first operation mode is changed, back pressure as second blade 52, during as the common running of the first above-mentioned operation mode, under the situation of the intermediate pressure between suction side pressure that applies two rotation compressing members 32,34 and the discharge side pressure, in this intermediate pressure, because the pressure difference with back pressure chamber 72A in second cylinder 40 is few, so follow very spended time of second roller 48 until second blade 52, betwixt, second blade 52 and 48 conflicts of second roller have produced the such problem of sound that clashes.
But, in the present invention, from second operation mode when first operation mode is changed, back pressure as second blade 52, by applying the discharge side pressure of two rotation compressing members 32,34, can discharge side pressure by this, second blade 52 is suppressed fully to second roller, 48 sides, second roller 48 is followed in early days.
In view of the above, improved, improved running efficiency from the tracing ability of second blade 52 of second operation mode when first operation mode is changed, and, the generation of the conflict sound of second blade 52 can be avoided.
In addition, when conversion, controller 210 is controlled, and makes electric element 14 low speed rotation (revolution is smaller or equal to 50Hz), and the compression ratio that makes two rotation compressing members 32,34 is smaller or equal to 3.0.In view of the above, because can suppress pressure oscillation,, also be difficult to be subjected to the influence of this pressure oscillation so, applied under the situation of discharge side pressure of two rotation compressing members 32,34 even in back pressure as the second rotation compressing member 34.
In addition, controller 210 is in the discharge side pressure that second blade 52 is applied two rotation compressing members 32,34, after making second blade 52 follow second roller 48, close solenoid valve 106 (Fig. 7 (3)), apply the suction side pressure of two rotation compressing members 32,34 and the intermediate pressure between the discharge side pressure.In view of the above, because as mentioned above, compare with the situation of the discharge side pressure that has applied two rotation compressing members 32,34 on the back pressure of second blade, pressure oscillation diminishes significantly, so can improve in operation mode, after conversion, the tracing ability of second blade 52 of rotary compressor 110 improves second compression efficiency of rotating compressing member 34, and, in first operation mode, can possibly avoid producing the conflict sound of second roller 48 and second blade 52.
As above describe in detail, even in the present embodiment, also can seek to improve performance and the reliability of the compression system CS with rotary compressor 110, this rotary compressor 110 can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member 32,34 compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member 32 to compress work done in fact.
In view of the above,, constitute the cryogen circuit of air conditioner, can improve the running efficiency and the performance of this air conditioner, also can seek to reduce consumption electric power by using this compression system CS.
(embodiment 3)
In the various embodiments described above,, be to use the refrigerant of HFC or HC class as refrigerant, also can use the big refrigerant of height pressure reduction of carbon dioxide etc., for example, as refrigerant, also can use the refrigerant after carbon dioxide and PAG (polyglycols) combination.In this case, because the refrigerant by each rotation compressing member 32,34 compression is very high high pressure, so if as the various embodiments described above, make discharge anechoic chamber 62 become the shape that covers the upside of upper support member 54 by cap assembly 63, then exist, cause the possibility of cap assembly 63 breakages owing to this high pressure.
Therefore, if make the refrigerant interflow by two rotation compressing members 32,34 compressions upper support member 54 upside the discharge anechoic chamber be shaped as shown in Figure 8 shape, then can guarantee resistance to pressure.That is, the discharge anechoic chamber 162 of Fig. 8 is constructed as follows: at the upside of upper support member 54, form depressed part, utilize the upper cap 66 of depressed part as lid sealed.In view of the above, even under the situation that contains the big refrigerant of height pressure reduction resemble the carbon dioxide, also can use the present invention.
(embodiment 4)
Action when then, starting with regard to compression system CS of the present invention describes.In addition, in the present embodiment, compression system CS, compression system, multi-cylinder rotary compressor and the cryogen circuit of use is identical with the Fig. 1's to Fig. 3 that uses in embodiment 1.Therefore, omit the explanation of these formations.In addition, the refrigerant of use is also identical with the various embodiments described above, uses the refrigerant of HFC or HC class, uses for example existing machine oil such as mineral oil (oil), alkymer, ether oil, ester oil as the machine oil of lubricant oil.
, use Fig. 9 here, the action the when rotary compressor 10 that present embodiment be described starts.According to the above-mentioned running instruction input that is arranged on the controller of the not shown indoor pusher side that goes out on the indoor set, electric element 14 energisings of 210 pairs of rotary compressors 10 of controller.At this moment, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101 in electric element 14 energisings, closes the solenoid valve 106 (Fig. 9 (1)) of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 75 is communicated with, and controller 210 is in the back pressure as second blade 52, applies under the state of suction side pressure of two rotation compressing members 32,34, and the revolution of the electric element 14 of control rotary compressor 10 starts.
Like this, if by wiring terminal 20 and the not shown distribution that goes out, to stator coil 28 energisings of electric element 14, then electric element 14 startings, rotor 24 rotations.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.At this moment, as mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 101 is opened, so the part of the refrigerant of the suction side of two rotation compressing members 32,34 by refrigerant pipe arrangement 100 flows into the back pressure chamber 72A through pipe arrangements 75 from refrigerant pipe arrangement 101.
On the other hand, having flow into refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in the refrigerant ingress pipe 92 of this accumulator 146 inner openings.The refrigerant gas that has entered refrigerant ingress pipe 92 is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32 through sucking path 58.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.Be discharged to the refrigerant gas of discharging anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.
When here, the inherent rotary compressor 10 of cryogen circuit starts is equilibrium pressure.Promptly, because rotary compressor 10 is after last running once stops, balance pressure gradually, if through scheduled time, then become equilibrium pressure in the cryogen circuit,, started under the situation of rotary compressor 10 so in cryogen circuit, become under the situation of equilibrium pressure, after rotary compressor 10 had just started, the pressure of the suction side refrigerant of the two rotation compressing members 32,34 that are applied in as the back pressure of second blade 52 became equilibrium pressure roughly.Equally, the pressure in second cylinder 40 also becomes roughly equilibrium pressure.Therefore, because can not occur second blade 52 is suppressed to second roller 48,, only be to be provided with first of spring 74 to rotate the compression work done that compressing member 32 is finished refrigerant so in the second rotation compressing member 34, do not compress work done in fact.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Here, the refrigerant gas heat release after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.The refrigerant that flow in the indoor side heat exchanger 156 here evaporates, and by from absorbing heat the air of indoor circulation, brings into play cooling action, to indoor refrigeration.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
On the other hand, if rotary compressor 10 startings through scheduled time, then constitute the height pressure difference in cryogen circuit, the state in the cryogen circuit is stable gradually.In addition, at this moment, though the pressure of the suction side refrigerant of the two rotation compressing members 32,34 that are applied in as the back pressure of second blade 52 are low pressure, but under this low pressure, owing to second blade 52 can not be suppressed to second roller, 48 sides, so, have only the first rotation compressing member 32 to finish the compression work done in fact with above-mentioned same.
Here, if rotary compressor 10 startings, through scheduled time, then controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101 shown in Fig. 9 (2), opens the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 102 is communicated with pipe arrangement 75, all flows in the accumulator 146 at the refrigerant of refrigerant pipe arrangement 100 circulation of rotary compressor 10.
In addition, a part that is discharged to the refrigerant of refrigerant discharge tube 96 in seal container 12 is passed through the pipe arrangements 75 inflow back pressure chamber 72A from refrigerant pipe arrangement 102.In view of the above, back pressure chamber 72A is the discharge side pressure of two rotation compressing members 32,34, as the back pressure of second blade 52, applies the discharge side pressure of two rotation compressing members 32,34.
Back pressure as second blade 52, by applying the discharge side pressure of two rotation compressing members 32,34, owing to be in a ratio of significant high pressure in the back pressure chamber of second blade 52 and second cylinder 40, so second blade 52 is by this high pressure of back pressure chamber 72A, suppressed to second roller, 48 sides, follow, in the second rotation compressing member 34, begin to compress work done.
That is, only in accumulator 146, entered in each refrigerant discharge tube 92,94 of this accumulator 146 inner openings by the refrigerant gas of gas-liquid separation.Enter into refrigerant ingress pipe 92 low pressure refrigerant gas as mentioned above, through sucking path 58, be inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.
On the other hand, the refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 94 sucks path 60, is inhaled into the low pressure chamber side of second cylinder 40 of the second rotation compressing member 34.The action of refrigerant gas by second roller 48 and second blade 52 that is inhaled into the low pressure chamber side of second cylinder 40 is compressed.
Here, controller 210 is closed solenoid valve 105, open solenoid valve 106, in back pressure as second blade 52, apply under the state of discharge side pressure of two rotation compressing members 32,34, under the situation of starting rotary compressor 10, because as mentioned above, after just starting, pressure in the cryogen circuit is equilibrium pressure roughly, even so open solenoid valve 106, also be this equilibrium pressure as the back pressure institute applied pressure of second blade 52, discharge side pressure of this two rotations compressing member 32,34 is wanted spended time until becoming high pressure.Therefore, before the discharge side pressure of two rotation compressing members 32,34 rises to a certain degree, can not make second blade 52 follow second roller 48.
In addition, because after just starting, the state labile in the cryogen circuit is so the pulse of the discharge side pressure of two rotation compressing members 32,34 also enlarges markedly.Therefore, under the situation of starting under the state of the discharge side pressure that applies two rotation compressing members 32,34, there is following problems, promptly, because the pulse of the discharge side pressure of two rotation compressing members 32,34 causes the tracing ability of second blade 52 to worsen, second blade 52 conflicts with second roller 48, produces the conflict sound.
But, as the present invention, by opening solenoid valve 105, apply two rotation compressing members 32, the state of 34 suction side pressure is starting down, do not make second blade 52 follow second roller 48, compression work done at the second rotation compressing member 34 is invalid in fact, simultaneously, after starting, in the cryogen circuit under the stable status, apply two rotation compressing members 32,34 discharge side pressure is discharged side pressure by this, second blade 52 is suppressed to second roller, 48 sides, make it follow second roller 38, just can avoid above-mentioned problem, can improve the tracing ability of second blade 52 when starting.
In view of the above, improve the running efficiency of rotary compressor 10, and, can avoid producing the conflict sound of second blade 52.
In addition, by the action compresses of second roller 48 and second blade 52, the refrigerant gas that becomes High Temperature High Pressure, is discharged to and discharges in the anechoic chamber 64 by in the not shown exhaust port that goes out from the hyperbaric chamber side of second cylinder 40.Be discharged to the above-mentioned access 120 of refrigerant gas process of discharging anechoic chamber 64, be discharged to and discharge in the anechoic chamber 62, with the refrigerant gas interflow of being compressed by the above-mentioned first rotation compressing member 32.Then, the refrigerant gas at interflow is discharged in the seal container 12 by connecting the not shown hole that goes out of cap assembly 63.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.In addition, the part of the discharge side refrigerant of two rotation compressing members 32,34 by refrigerant discharge tube 96 since as mentioned above solenoid valve 106 be opened, so from refrigerant pipe arrangement 102 through pipe arrangements 75, flow among the back pressure chamber 72A.In view of the above, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
On the other hand, flow into the refrigerant gas heat release here of outdoor heat exchanger 152, after expansion valve 154 decompressions, flow in the indoor side heat exchanger 156.By this indoor side heat exchanger 156 refrigerant evaporation,, bring into play cooling action, to indoor refrigeration by from the air of indoor circulation, absorbing heat.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
On the other hand, if apply the discharge side pressure of two rotation compressing members 32,34, make second blade 52 follow second roller 48, then controller 210 is closed solenoid valve 106 (Fig. 9 (3)) thereafter.Become enclosed space in view of the above, with in the pipe arrangement 75 that the back pressure chamber 72A of second blade 52 is communicated with.Here, because the refrigerant in many second cylinders 40 flows into the back pressure chamber 72A between second blade 52 and container 70A, so the pressure in the back pressure chamber 72A of second blade 52 becomes the suction side pressure of two rotation compressing members 32,34 and discharges intermediate pressure between the side pressure, become the state that this intermediate pressure is applied in as the back pressure of second blade 52.Because this intermediate pressure so do not use spring members, can suppress second blade 52 to second roller 48 fully.
Here, in back pressure as second blade 52, continue to apply under the situation as the high pressure of the discharge side pressure of two above-mentioned rotation compressing members 32,34, because it is big to discharge the side pressure pulse, and in the second rotation compressing member 34, there is not spring members, so the generation following problems, that is, because this pulse causes the tracing ability of second blade 52 to worsen, compression efficiency reduces, and produces the conflict sound between second blade 52 and second roller 48.
In addition, at starting rotary compressor 10, back pressure as second blade 52, do not apply high pressure as the discharge side pressure of above-mentioned two rotation compressing members 32,34, to make back pressure chamber 72A be the suction side pressure of two rotation compressing members 32,34 and discharge under the situation of the intermediate pressure between the side pressure, there is following problems, promptly, because when this intermediate pressure, pressure difference with back pressure chamber 72A in second cylinder 40 is little, so second blade 52 is wanted spended time until following second roller 48, betwixt, second blade 52 and 48 conflicts of second roller produce the conflict sound.
Therefore, by back pressure as second blade 52, apply the discharge side pressure of two rotation compressing members 32,34, utilize this discharge side pressure, second blade 52 is suppressed to second roller, 48 sides, after making it follow second roller 48, making back pressure chamber 72A is the suction side pressure of two rotation compressing members 32,34 and the intermediate pressure between the discharge side pressure, can improve the tracing ability of second blade 52, improve the compression efficiency of the second rotation compressing member 34, and, can possibly avoid the time producing the conflict sound of second roller 48 and second blade 52 in starting.
In addition, in the present embodiment, though controller 210 is controlled, in to electric element 14 energisings, open solenoid valve 105, close solenoid valve 106, but also can be the switching of carrying out solenoid valve 105,106 at rotary compressor 10 prestarts, for example, controller 210 can be before to electric element 14 energisings, open solenoid valve 105, close solenoid valve 106.
In addition, relevant first operation mode that when common load or high load, carries out and second operation mode that carries out in the light hours, since identical with embodiment's 1 action, the Therefore, omited explanation.
(embodiment 5)
Have again, in compression system CS of the present invention, also can be as the outlet side of above-mentioned embodiment's 2 accumulator shown in Figure 5 146, solenoid valve 200 is arranged on the middle part of refrigerant ingress pipe 94 of the inlet side of seal container 12, this solenoid valve 200 is by controller 210 controls.
Like this, solenoid valve 200 is set on refrigerant ingress pipe 94, when starting, closes solenoid valve, cut off inflow fully to the refrigerant of the second rotation compressing member 34, when opening the solenoid valve 106 of refrigerant pipe arrangement 102, open this solenoid valve 200, also effective so in the present invention.
In addition, in second operation mode, by utilizing controller 210 to close solenoid valve 200, stop and under the state of the inflow of the refrigerant of second cylinder 40, turning round, just can make becomes the high pressure of suction side pressure that rotates compressing member 32 than first in second cylinder 40.
In addition, same as the previously described embodiments as refrigerant in the present embodiment, the refrigerant of use HFC or HC class as the machine oil of lubricant oil, uses for example existing machine oil such as mineral oil (oil), alkymer, ether oil, ester oil.
Action under this situation is described.Controller 210 is closed above-mentioned solenoid valve 200, stops the inflow to the refrigerant of second cylinder 40.In view of the above, in the second rotation compressing member 34, do not finish the compression work done.In addition, if stop inflow to the refrigerant of second cylinder 40, then become the pressure higher (because second roller, 48 rotations in second cylinder 40 than the suction side pressure of two above-mentioned rotation compressing members 32,34, and, high pressure in the seal container 12 is from the inflows such as gap of second cylinder 40, so become the pressure higher than suction side pressure in second cylinder 40).
In addition, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101, closes the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 75 are communicated with, and the suction side refrigerant of the first rotation compressing member 32 flows among the back pressure chamber 72A, as the back pressure of second blade 52, apply the suction side pressure of the first rotation compressing member 32.
Then, the part of the refrigerant of the suction side of first of the refrigerant pipe arrangement 100 by the rotary compressor 110 rotation compressing member 32 flows into the back pressure chamber 72A through pipe arrangements 75 from refrigerant pipe arrangement 101.In view of the above, back pressure chamber 72A becomes the suction side pressure of the first rotation compressing member 32, as the back pressure of second blade 52, applies the suction side pressure of this first rotation compressing member 32.
Here, if close solenoid valve 200, the inflow of the refrigerant of prevention in second cylinder 40, make the high pressure of suction side pressure that becomes in second cylinder 40 than the first rotation compressing member 32, then as the back pressure of second blade 52, by applying the suction side pressure of the first rotation compressing member 32, make the back pressure height of pressure ratio second blade 52 in second cylinder 40.Therefore, second blade 52 is pressed to becoming with the back pressure chamber 72A thruster of second roller, 48 opposite sides by the pressure in second cylinder 40, can not come out in second cylinder 40.In view of the above, can possibly avoid second blade 52 in second cylinder 40, to come out, conflict, produce the such problem of conflict sound with second roller 48.
On the other hand, flowing into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in the refrigerant discharge tube 92 of this accumulator 146 inner openings.The refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.Be discharged to the refrigerant gas of discharging anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Here, the refrigerant gas heat release after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.In this indoor side heat exchanger 156, the refrigerant evaporation by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 110.
Like this, middle part at refrigerant ingress pipe 94 is provided with solenoid valve 200, in second operation mode, close solenoid valve 200 by utilizing controller 210, turn round under the state of the inflow of the refrigerant of second cylinder 40 in prevention, in second operation mode, the pressure in second cylinder 40 is remained on the state higher than the back pressure of second blade 52 like this.Therefore, second blade 52 is by the pressure in second cylinder 40, pressed to becoming with the back pressure chamber 72A thruster of the opposite side of second roller 48, can not come out in second cylinder 40.In view of the above, can possibly avoid in the running of second operation mode, second blade 52 comes out in second cylinder 40, conflicts with second roller 48, produces the such problem of conflict sound.
As above detailed description, according to the present invention, can seek to have performance and the reliability of the compression system CS of rotary compressor 110, this rotary compressor 110 can be changed and be used the 1st operation mode and the 2nd operation mode, at above-mentioned the 1st operation mode, first and the second rotation compressing member 32,34 compresses work done, at above-mentioned the 2nd operation mode, has only the first rotation compressing member 32 to compress work done in fact.
In view of the above,, constitute the cryogen circuit of air conditioner, can improve the running efficiency and the performance of this air conditioner, also can seek to reduce consumption electric power by using this compression system CS.
(embodiment 6)
In addition, in the foregoing description 4 and embodiment 5, as refrigerant, use the refrigerant of HFC or HC class, but also can use the big refrigerant of height pressure reduction of carbon dioxide etc., for example, as refrigerant, also can use the refrigerant after carbon dioxide and PAG (polyglycols) make up.In this case, because the refrigerant by each rotation compressing member 32,34 compression is very high high pressure, so if make discharge anechoic chamber 62 become the shape that covers the upside of upper support member 54 by cap assembly 63 as the various embodiments described above, then exist, cause the possibility of cap assembly 63 breakages owing to this high pressure.
Therefore, if make the refrigerant interflow by two rotation compressing members 32,34 compressions upper support member 54 upside the discharge anechoic chamber be shaped as shape shown in Figure 8, then can guarantee resistance to pressure.That is, the discharge anechoic chamber 162 of Fig. 8 is constructed as follows: the upside in upper support member 54 forms depressed part, utilizes the upper cap 66 of depressed part as lid sealed.In view of the above, even under the situation that contains the big refrigerant of height pressure reduction resemble the carbon dioxide, also can use the present invention.
(embodiment 7)
Then, other the other embodiments with regard to compression system, multi-cylinder rotary compressor of the present invention describe.Figure 10 is the vertical profile side view of the compression system, multi-cylinder rotary compressor of the present invention under this situation.In addition, another vertical profile side view of the compression system, multi-cylinder rotary compressor of present embodiment is identical with Fig. 1 of embodiment 1, and in addition, the cryogen circuit figure also Fig. 3 with embodiment 1 is identical.Therefore, in the present embodiment, only the position to the formation that is different from embodiment 1 describes.In addition, in the present embodiment, the parts of giving the symbol identical with Fig. 1 to Fig. 3 are the parts that can produce identical or similar effects.
This embodiment's back pressure chamber 172A is at steering channel 72 sides and seal container 12 side openings, connecting pipe arrangement 75 described later in the open communication of sealing container 12 sides, and is sealed in the seal container 12.
In addition, back pressure chamber 172A of the present invention becomes the baffler chamber of the spatial volume with regulation.Embodiment's back pressure chamber 172A becomes the shape of the chamber with sagged shape as shown in figure 10, and the chamber of this sagged shape has the spatial volume of regulation on the joint bit position of the above-mentioned pipe arrangement 75 of the upside that becomes lower support member 56 and steering channel 72.Promptly, the back pressure chamber 172A of present embodiment is formed on and seals the top pipe arrangement 75 and the steering channel 72 corresponding positions of lower support member 56 of opening surface of the downside of above-mentioned second cylinder 40, and the following opening portion by this lower support member 56 sealings second cylinder 40 forms depressed part.
Like this, by back pressure chamber 172A being become have the shape of the spatial volume of regulation, by this back pressure chamber 172A, can reduce the pressure pulse that produces because of snap action and the pulse of the pressure that is applied in as the back pressure of second blade 52 to second blade 52.
In addition,, use the refrigerant of HFC or HC class,, use for example existing machine oil such as mineral oil (oil), alkymer, ether oil, ester oil as the machine oil of lubricant oil as refrigerant.
With above-mentioned formation, the action of rotary compressor 10 is described then.
(1) first operation mode when high load (load or) usually
At first, first operation mode that compresses work done with regard to two rotation compressing members 32,34 describes.According to the above-mentioned running instruction input that is arranged on the controller of the not shown indoor pusher side that goes out on the indoor set, the revolution of the electric element 14 of controller 210 control rotary compressors 10, simultaneously, indoor be usually that controller 210 is carried out first operation mode under the situation of load or higher load condition.Under this first operation mode, controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101, opens the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 75 are communicated with, and the suction side refrigerant of two rotation compressing members 32,34 flows among the back pressure chamber 172A, as the back pressure of second blade 52, apply the suction side pressure of two rotation compressing members 32.
Like this, if by wiring terminal 20 and the not shown distribution that goes out, to stator coil 28 energisings of electric element 14, then electric element 14 startings, rotor 24 rotations.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.As mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 100 is closed, thus can not flow into pipe arrangement 75 by the refrigerant of refrigerant pipe arrangement 100, but all flow in the accumulator 146.
Like this, having flow into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in each refrigerant discharge tube 92,94 of this accumulator 146 inner openings.The refrigerant gas process that has entered the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.
On the other hand, the refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 94 sucks path 60, is inhaled into the low pressure chamber side of second cylinder 40 of the second rotation compressing member 34.The action of refrigerant gas by second roller 48 and second blade 52 that is inhaled into the low pressure chamber side of second cylinder 40 is compressed.
At this moment, as mentioned above, because to the snap action of second blade 52 to second roller 48, the back pressure chamber 172A side with the opposite side of second roller 48 of becoming at second blade 52 produces pressure pulse.In this case, produced in the second rotation compressing member 34 that does not have to be provided with spring members in the past, because this pressure pulse, the tracing ability of 52 pairs second rollers of second blade worsens such problem.
Have again, because the discharge side pressure pulse as back pressure applied the two rotation compressing members 32,34 of second blade 52 is big, and there is not a spring members, so there is following problems, that is, because this pulse causes the tracing ability of second blade 52 to worsen, in view of the above, compression efficiency reduces, and, between second blade 52 and second roller 48, produce the conflict sound.
But as the present invention, the baffler chamber that has the spatial volume of regulation by back pressure chamber 172A is become can reduce the pressure pulse that produces owing to the snap action to second blade 52.In addition, by in the process of this back pressure chamber 172A, pressure pulse significantly reduces from the discharge side refrigerant of two rotation compressing members 32,34 of pipe arrangement 75.In view of the above, do not use spring members, second blade 52 can be suppressed fully to second roller 48 yet.
In view of the above, improve the tracing ability of second blade 52 in first operation mode, also improved the compression efficiency of the second rotation compressing member 34.Have again,, can avoid conflicting of above-mentioned and second roller 48 by improving the tracing ability of second blade 52.Therefore, also can do one's utmost to avoid with second roller 48 between produce the such problem of sound of conflicting.
In addition, the action by second roller 48 and second blade 52 is compressed, and becomes the refrigerant gas of High Temperature High Pressure,, is discharged to and discharges in the anechoic chamber 64 by in the not shown exhaust port that goes out from the hyperbaric chamber side of second cylinder 40.Be discharged to the above-mentioned access 120 of refrigerant gas process of discharging in the anechoic chamber 64, be discharged to and discharge in the anechoic chamber 62, with the refrigerant gas interflow of being compressed by the above-mentioned first rotation compressing member 32.Like this, the refrigerant gas at interflow is discharged in the seal container 12 by connecting the not shown hole that goes out of cap assembly 63.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.On the one hand, as mentioned above, because open solenoid valve 106, so the part of the discharge side refrigerant of the two rotation compressing members 32,34 that flow in refrigerant discharge tube 96 flows in the back pressure chamber 172A through pipe arrangement 75 from refrigerant pipe arrangement 102 by controller 210.In view of the above, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
On the other hand, flow into the refrigerant gas heat release here of outdoor heat exchanger 152, after expansion valve 154 decompressions, flow in the indoor side heat exchanger 156.By this indoor side heat exchanger 156, the refrigerant evaporation by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
In addition, in the first above-mentioned operation mode, controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101, open the solenoid valve 106 of refrigerant pipe arrangement 102, refrigerant pipe arrangement 102 and pipe arrangement 75 are communicated with, back pressure as second blade 52, applied discharge side pressure for two rotation compressing members 32,34 of high pressure, but in this first operation mode, as the back pressure of second blade 52, also can apply the suction side pressure of two rotation compressing members 32,34 and the intermediate pressure between the discharge side pressure.In this case, if close the solenoid valve 105 of refrigerant pipe arrangement 101 and the solenoid valve 106 of refrigerant pipe arrangement 102 by controller 210, make in the pipe arrangement 75 that is communicated with the back pressure chamber 172A of second blade 52 and become enclosed space, then because the refrigerant in the second a lot of cylinders 40 flows into the back pressure chamber 172A between second blade 52 and container 70A, so the pressure in the back pressure chamber 172A of second blade 52 becomes two rotation compressing members 32,34 suction side pressure and discharge intermediate pressure between the side pressure, this intermediate pressure is applied in as the back pressure of second blade 52.
Like this, even, also do not use spring members,, second blade 52 can be suppressed fully to second roller 48 by this intermediate pressure as the back pressure of second blade 52 and applied under the situation of intermediate pressure.Have, because compare with the situation of the discharge side pressure that has applied two rotation compressing members 32,34, pressure pulse significantly reduces, so on the basis of the reduction pulsatile effect of bringing because of above-mentioned back pressure chamber 172A, can seek further to reduce pulse again.Particularly, as mentioned above, by closing solenoid valve 105,106, become cut-out from pipe arrangement 75 to the suction side refrigerant of two rotation compressing members 32,34 with discharge the state of the inflow of side refrigerant, can further suppress the pulse of the back pressure of second blade 52.
(2) second operation modes (runnings of light hours)
Then, describe with regard to second operation mode.Controller 210 indoor be under the situation of light load state, be transformed into second operation mode.This second operation mode is to have only the first rotation compressing member 32 to compress the pattern of work done in fact, is to be light load indoor, and in above-mentioned first operation mode, the operation mode of electric element 14 for carrying out under the situation of low speed rotation.In little ability zone, by having only the first rotation compressing member 32 to compress work done in fact, compare with the situation of compressing work done by first and second liang of cylinder 38,40, owing to can reduce the amount of the refrigerant gas of compression, even so should measure in the light hours, the revolution of electric element 14 is risen, improved the running efficiency of electric element 14, and also make the leakage loss that reduces refrigerant become possibility.
In this case, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101, closes the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 75 are communicated with, and the suction side refrigerant of the first rotation compressing member 32 flows among the back pressure chamber 172A, as the back pressure of second blade 52, apply the suction side pressure of the first rotation compressing member 32.
On the other hand, controller 210 to stator coil 28 energisings of electric element 14, makes rotor 24 rotations of electric element 14 by aforesaid wiring terminal 20 and the not shown distribution that goes out.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.At this moment, as mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 100 is opened, so the part of the refrigerant of the suction side of the first rotation compressing member 32 by refrigerant pipe arrangement 100 flows into the back pressure chamber 172A through pipe arrangements 75 from refrigerant pipe arrangement 101.In view of the above, back pressure chamber 172A becomes the suction side pressure of the first rotation compressing member 32, as the back pressure of second blade 52, applies the suction side pressure of this first rotation compressing member 32.
Here because as second the rotation compressing member 34 back pressure and be applied in two the rotation compressing members 32,34 suction side pressures be low pressure, so second blade 52 can not be suppressed to second roller 48.Therefore, in the second rotation compressing member 34, not compressing work done in fact, only is to be provided with first of spring 74 to rotate the compression work done that compressing member 32 is finished refrigerant.
In this case, because the pressure in second cylinder 40 and the back pressure of second blade apply suction side pressure in the same manner, so in the past, the change of the balance by two spaces, second blade appears in second cylinder, conflicts with second roller, still has the problem that produces the conflict sound.But the back pressure chamber 172A of the spatial volume by having regulation of the present invention owing to can reduce change, so can do one's utmost to avoid second blade 52 to appear in second cylinder 40, conflict with second roller 48, produces the such problem of sound of conflicting.
On the other hand, the refrigerant that flow into the low pressure in the accumulator 146 only is that refrigerant gas enters in the refrigerant discharge tube 92 of this accumulator 146 inner openings here by after the gas-liquid separation.The refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.Be discharged to the refrigerant gas of discharging anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Here, the refrigerant gas heat release after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.By this indoor side heat exchanger 156, the refrigerant evaporation by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
As above detailed description, according to the present invention, can seek to improve the performance and the reliability of rotary compressor 10, this rotary compressor 10 can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member 32,34 compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member 32 to compress work done in fact.
In view of the above, by using this rotary compressor 10, constitute the cryogen circuit of air conditioner, can improve the running efficiency and the performance of this air conditioner, also make to seek to reduce to consume electric power and become possibility.
(embodiment 8)
In addition, in embodiment 7, be to make back pressure chamber 172A become the shape of chamber with sagged shape, this chamber has the spatial volume of regulation, but is not limited only to this, as long as back pressure chamber of the present invention has the spatial volume of regulation.For example, become at back pressure chamber under the situation of shape shown in Figure 11, the present invention is also effective.In addition, Figure 11 is the vertical view cutaway drawing of second cylinder of this situation.In Figure 11, giving with the parts of Fig. 1 to Figure 10 same-sign is the parts that can produce identical or similar effect.
In Figure 11,49 is exhaust ports of the second rotation compressing member 34.This back pressure chamber 272A has the enlarged portion of the spatial volume of regulation at the transverse direction of second cylinder 40, as a whole, is roughly cylindric.Like this, become at back pressure chamber 272A under the situation of the such shape of present embodiment, also can pass through this back pressure chamber 272A, reduce this pressure pulse, improve the tracing ability of second blade 52, avoid and the conflicting of second roller 48.
(embodiment 9)
In addition, even under the foregoing description 7 and embodiment's 8 situation, also as shown in Figure 5, outlet side at the accumulator 146 of rotary compressor 10, at the middle part of the refrigerant ingress pipe 94 of the inlet side of seal container 12, the solenoid valve 200 that control flows into to the refrigerant of the second rotation compressing member 34 is set, in second operation mode, close solenoid valve 200, cut-out also is fine to the inflow of the refrigerant of second cylinder 40.
In this case, if cut off inflow to the refrigerant of second cylinder 40, then in second cylinder 40 as mentioned above, become the pressure higher slightly (because second roller, 48 rotations than the suction side pressure of two rotation compressing members 32,34, and, high pressure in the seal container 12 is some from the inflows such as gap of second cylinder 40, so become the pressure higher slightly than suction side pressure in second cylinder 40).
Therefore, second blade 52 is by the pressure in second cylinder 40, presses to becoming with back pressure chamber 172A (or the back pressure chamber 272A) thruster of the opposite side of second roller 48, can not appear in second cylinder 40.In view of the above, on the basis of the effect of above-mentioned back pressure chamber 172A (or back pressure chamber 272A), can more effectively avoid producing second blade 52 such problem of conflicting with second roller 48.
(embodiment 10)
In the foregoing description 7, embodiment 8 and embodiment 9, as refrigerant, be to use the refrigerant of HFC or HC class, but also can use the big refrigerant of height pressure reduction of carbon dioxide etc., for example, as refrigerant, also can use the refrigerant after carbon dioxide and PAG (polyglycols) combination.In this case, because the refrigerant by each rotation compressing member 32,34 compression is very high high pressure, so if make discharge anechoic chamber 62 become the shape that covers the upside of upper support member 54 by cap assembly 63 as the various embodiments described above, then exist, cause the possibility of cap assembly 63 breakages owing to this high pressure.
Therefore, if make the refrigerant interflow by two rotation compressing members 32,34 compressions upper support member 54 upside the discharge anechoic chamber be shaped as shown in Figure 8 shape, then can guarantee resistance to pressure.That is, the discharge anechoic chamber 162 of Fig. 8 is constructed as follows: the upside in upper support member 54 forms depressed part, utilizes the upper cap 66 of depressed part as lid sealed.In view of the above, even under the situation that contains the big refrigerant of height pressure reduction resemble the carbon dioxide, also can use the present invention.
(embodiment 11)
Then, use Figure 12 and Figure 13, describe with regard to other other embodiments of compression system, multi-cylinder rotary compressor of the present invention.Figure 12 is the vertical view cutaway drawing that second roller of the second rotation compressing member of expression compression system, multi-cylinder rotary compressor of the present invention is positioned at second cylinder of top dead center situation, and Figure 13 is the vertical view cutaway drawing that second roller of the expression second rotation compressing member is positioned at second cylinder of lower dead center situation.
In addition, because the vertical profile side view of this embodiment's compression system, multi-cylinder rotary compressor is identical with Fig. 1 and Fig. 2 of embodiment 1, the cryogen circuit figure also Fig. 3 with embodiment 1 is identical, so omit.Therefore, in the present embodiment, only the position to the formation that is different from embodiment 1 describes.In addition, in the present embodiment, giving with the parts of Fig. 1 to Fig. 3 same-sign is the parts that can produce identical or similar effects.
Here, the back side at second blade 52 forms back pressure chamber 72A.Back pressure chamber 72A is at steering channel 72 sides and seal container 12 side openings, connecting as the pipe arrangement 375 (Figure 12 to Figure 13) of back pressure with path from the open communication of sealing container 12 sides, and is sealed in the seal container 12.
Above-mentioned pipe arrangement 375 is the back pressure paths that are used for second blade 52 of the second rotation compressing member 34 is applied back pressure, be respectively by refrigerant pipe arrangement 101 described later, be communicated with the two refrigerant pipe arrangements 100 that rotate the suction side of compressing members 32,34, by refrigerant pipe arrangement 102, be communicated with two refrigerant discharge tube 96 of rotating the discharge side of compressing members 32,34.Like this, the suction side refrigerant of the discharge side refrigerant of two rotation compressing members 32,34 or two rotation compressing members 32,34 flows into the back pressure chamber 72A from pipe arrangement 75, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34 or the suction side pressure of two rotation compressing members 32,34.
In addition, in the present invention, the cross-section area of pipe arrangement 375 is more than or equal to the mean value of the surface area that is exposed to second blade 52 in above-mentioned second cylinder 40.Promptly, calculate at second blade 52 and become the top dead center that least exposes the state in second cylinder 40 from as shown in figure 12 second roller 48 of following in second cylinder 40 eccentric rotation, become between the lower dead center (dotted line of second blade 52 of Figure 13 represents to expose the part in second cylinder 40) of exposing the state in second cylinder 40 most to as shown in figure 13 second blade 52, the mean value that exposes the surface area of second blade 52 in second cylinder 40 is set at mean value more than or equal to this surface area with the cross-section area of above-mentioned pipe arrangement 375.
Like this, the cross-section area by making pipe arrangement 375 is more than or equal to the mean value of the surface area that is exposed to second blade 52 in second cylinder 40, can guarantee the area with the back pressure chamber 72A side of above-mentioned second roller, 48 opposite sides of becoming of second blade 52 fully.
In addition,, be to use the refrigerant of HFC or HC class,, be to use for example existing machine oil such as mineral oil (oil), alkymer, ether oil, ester oil as the machine oil of lubricant oil as refrigerant.
With above-mentioned formation, the action of rotary compressor 10 is described then.
(1) first operation mode when high load (load or) usually
At first, first operation mode that compresses work done with regard to two rotation compressing members 32,34 describes.According to the above-mentioned running instruction input that is arranged on the controller of the not shown indoor pusher side that goes out on the indoor set, the revolution of the electric element 14 of controller 210 control rotary compressors 10, simultaneously, indoor be usually that controller 210 is carried out first operation mode under the situation of load or higher load condition.In this first operation mode, controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101, opens the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 375 are communicated with, and the discharge side refrigerant of two rotation compressing members 32,34 flows among the back pressure chamber 72A, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
Like this, if by wiring terminal 20 and the not shown distribution that goes out, to stator coil 28 energisings of electric element 14, then electric element 14 startings, rotor 24 rotations.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.As mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 100 is closed, thus can not flow in the pipe arrangement 375 by the refrigerant of refrigerant pipe arrangement 100, but all flow in the accumulator 146.
Like this, having flow into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in each refrigerant discharge tube 92,94 of this accumulator 146 inner openings.The refrigerant gas process that has entered the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.
On the other hand, the refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 94 sucks path 60, is inhaled into the low pressure chamber side of second cylinder 40 of the second rotation compressing member 34.The action of refrigerant gas by second roller 48 and second blade 52 that is inhaled into the low pressure chamber side of second cylinder 40 is compressed.
At this moment, as mentioned above, because to the snap action of second blade 52 to second roller 48, the back pressure chamber 72A side with the opposite side of second roller 48 of becoming at second blade 52 produces pressure pulse.In this case, produced in the second rotation compressing member 34 that does not have to be provided with spring members in the past, because this pressure pulse, the tracing ability of 52 pairs second rollers 48 of second blade worsens such problem.
Have again, because the discharge side pressure pulse as back pressure applied the two rotation compressing members 32,34 of second blade 52 is big, and on the second rotation compressing member 34, there is not spring members, so there is following problems, that is, because this pulse causes the tracing ability of second blade 52 to worsen, in view of the above, compression efficiency reduces, and, between second blade 52 and second roller 48, produce the conflict sound.
But, as mentioned above, cross-section area by making pipe arrangement 375 is more than or equal to the mean value of the surface area that is exposed to second blade 52 in second cylinder 40, can guarantee fully that second blade 52 becomes the area with the back pressure chamber 72A side of second roller, 48 opposite sides, can reduce the pressure pulse that the snap action owing to second blade 52 produces.In addition, by in the process of this pipe arrangement 375, pressure pulse significantly reduces from the discharge side refrigerant of two rotation compressing members 32,34 of pipe arrangement 375.In view of the above, do not use spring members, second blade 52 can be suppressed fully to second roller 48.
In view of the above, improve the tracing ability of second blade 52 in first operation mode, also improved the compression efficiency of the second rotation compressing member 34.Have again,, can avoid conflicting of above-mentioned and second roller 48 by improving the tracing ability of second blade 52.Therefore, also can do one's utmost to avoid with second roller 48 between produce the such problem of sound of conflicting.
In addition, be compacted into the refrigerant gas of High Temperature High Pressure, by in the exhaust port 49, be discharged to and discharge in the anechoic chamber 64 from the hyperbaric chamber side of second cylinder 40 by the action of second roller 48 and second blade 52.Be discharged to the above-mentioned access 120 of refrigerant gas process of discharging anechoic chamber 64, be discharged to and discharge anechoic chamber 62, with the refrigerant gas interflow of being compressed by the first rotation compressing member 32.The refrigerant gas at interflow is discharged in the seal container 12 by connecting the not shown hole that goes out of cap assembly 63.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Here, as mentioned above, because the solenoid valve 106 of pipe arrangement 102 is opened, so the parts of the discharge side refrigerant of two rotation compressing members 32,34 by refrigerant discharge tube 96, enter pipe arrangement 375 from refrigerant pipe arrangement 102 as mentioned above, as the back pressure of second blade 52 and be applied in.
On the other hand, flow into the refrigerant gas heat release here of outdoor heat exchanger 152, after expansion valve 154 decompressions, flow in the indoor side heat exchanger 156.In this indoor side heat exchanger 156, the refrigerant evaporation by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
In addition, in the first above-mentioned operation mode, controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101, open the solenoid valve 106 of refrigerant pipe arrangement 102, refrigerant pipe arrangement 102 and pipe arrangement 375 are communicated with, as the back pressure of second blade 52, be applied for the discharge side pressure of two rotation compressing members 32,34 of high pressure, but,, also can apply the suction side pressure of two rotation compressing members 32,34 and the intermediate pressure between the discharge side pressure as the back pressure of second blade 52.In this case, for example if by controller 210, close the solenoid valve 105 of refrigerant pipe arrangement 101 and the solenoid valve 106 of refrigerant pipe arrangement 102, make in the pipe arrangement 375 that is communicated with the back pressure chamber 72A of second blade 52 and become enclosed space, then because the refrigerant in many second cylinders 40 flows into the back pressure chamber 72A between second blade 52 and container 70A, so the pressure in the back pressure chamber 72A of second blade 52 becomes two rotation compressing members 32,34 suction side pressure and discharge intermediate pressure between the side pressure, this intermediate pressure is applied in as the back pressure of second blade 52.
Like this,, applied under the situation of intermediate pressure, do not used spring members,, also second blade 52 can have been suppressed fully to second roller 48 by this intermediate pressure in back pressure as second blade 52.Have, because compare with the situations of the discharge side pressure that has applied two rotation compressing members 32,34, pressure pulse significantly reduces again, so on the basis of the effect of above-mentioned pipe arrangement 375, can seek to reduce further pulse.Particularly, as mentioned above, by closing solenoid valve 105,106, become cut-out from pipe arrangement 375 to the suction side refrigerant of two rotation compressing members 32,34 with discharge the state of the inflow of side refrigerant, can further suppress the pulse of the back pressure of second blade 52.
(2) second operation modes (runnings of light hours)
Then, describe with regard to second operation mode.Controller 210 indoor be under the situation of light load state, be transformed into second operation mode.This second operation mode is to have only the first rotation compressing member 32 to compress the pattern of work done in fact, is to be light load indoor, and in above-mentioned first operation mode, the operation mode of electric element 14 for carrying out under the situation of low speed rotation.Because in little ability zone, by having only the first rotation compressing member 32 to compress work done in fact, compare with the situation of compressing work done at first and second liang of cylinder 38,40, can reduce the amount of the refrigerant gas of compression, so this amount also makes the revolution of electric element 14 rise in the light hours, improve the running efficiency of electric element 14, and also make the leakage loss that reduces refrigerant become possibility.
In this case, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101, closes the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 375 are communicated with, and the suction side refrigerant of the first rotation compressing member 32 flows among the back pressure chamber 72A, as the back pressure of second blade 52, apply the suction side pressure of the first rotation compressing member 32.
On the other hand, controller 210 to stator coil 28 energisings of electric element 14, makes rotor 24 rotations of electric element 14 by aforesaid wiring terminal 20 and the not shown distribution that goes out.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, low-pressure refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.At this moment, as mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 101 is opened, so the part of the refrigerant of the suction side of the first rotation compressing member 32 by refrigerant pipe arrangement 100 flows into the back pressure chamber 72A through pipe arrangements 375 from refrigerant pipe arrangement 101.In view of the above, back pressure chamber 72A becomes the suction side pressure of the first rotation compressing member 32, as the back pressure of second blade 52, applies the suction side pressure of this first rotation compressing member 32.
Here because as second the rotation compressing member 34 back pressure and be applied in two the rotation compressing members 32,34 suction side pressures be low pressure, so second blade 52 can not be suppressed to second roller 48.Therefore, in the second rotation compressing member 34, not compressing work done in fact, only is to be provided with first of spring 74 to rotate the compression work done that compressing member 32 is finished refrigerant.
In this case, because the suction side pressure identical with the back pressure of the pressure in second cylinder 40 and second blade 52 is applied in, so in the past, the change of the balance by two spaces, second blade 52 appears in second cylinder 40, conflict with second roller 48, still have the such problem of conflict sound that produces.But, as the present invention like this, cross-section area by making the pipe arrangement 375 on the back pressure chamber 72A that is connected second blade 52 is more than or equal to the mean value of the surface area that exposes second blade 52 in second cylinder 40, utilize this pipe arrangement 375, owing to can reduce change, so can do one's utmost to avoid second blade 52 to appear in second cylinder 40, conflict with second roller 48, produce the such problem of conflict sound.
On the other hand, the refrigerant that flow into the low pressure in the accumulator 146 only is that refrigerant gas enters in the refrigerant discharge tube 92 of this accumulator 146 inner openings here by after the gas-liquid separation.The refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.Be discharged to the refrigerant gas of discharging anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, flows in the outdoor heat exchanger 152.Here, the refrigerant gas heat release after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.The refrigerant that flow in the indoor side heat exchanger 156 here evaporates, and by from absorbing heat the air of indoor circulation, brings into play cooling action, to indoor refrigeration.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
As above detailed description, according to the present invention, can seek to improve the performance and the reliability of rotary compressor 10, this rotary compressor 10 can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member 32,34 compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member 32 to compress work done in fact.
In view of the above, by using this rotary compressor 10, constitute the cryogen circuit of air conditioner, can improve the running efficiency and the performance of this air conditioner, also make to seek to reduce to consume electric power and become possibility.
(embodiment 12)
In addition, also can be as shown in Figure 5, outlet side at the accumulator 146 of rotary compressor 10, middle part at the refrigerant ingress pipe 94 of the inlet side of seal container 12, the solenoid valve 200 of control to the refrigerant inflow of second cylinder 40 of the second rotation compressing member 34 is set, in second operation mode, close solenoid valve 200, cut off inflow to the refrigerant of second cylinder 40.In addition, in Fig. 5, the parts of giving with Fig. 1 to Figure 13 same-sign are the parts that produce same effect.
In this case, if cut off inflow to the refrigerant of second cylinder 40, then become the pressure higher slightly (because second roller, 48 rotations in second cylinder 40 as mentioned above than the suction side pressure of two rotation compressing members 32,34, and, high pressure in the seal container 12 is some from the inflows such as gap of second cylinder 40, so become the pressure higher slightly than suction side pressure in second cylinder 40).
Therefore, second blade 52 is by the pressure in second cylinder 40, presses to becoming with the back pressure chamber 72A thruster of the opposite side of second roller 48, can not appear in second cylinder 40.In view of the above, on the basis of the effect of above-mentioned pipe arrangement 375, can further avoid producing second blade 52 such problem of conflicting with second roller 48 effectively.
(embodiment 13)
In addition, in the foregoing description 11 and embodiment 12, as refrigerant, be to use the refrigerant of HFC or HC class, but also can use the big refrigerant of height pressure reduction of carbon dioxide etc., for example, as refrigerant, also can use the refrigerant after carbon dioxide and PAG (polyglycols) combination.In this case, because the refrigerant by each rotation compressing member 32,34 compression is very high high pressure, so if make discharge anechoic chamber 62 become the shape that covers the upside of upper support member 54 by cap assembly 63 as the various embodiments described above, then exist, cause the possibility of cap assembly 63 breakages owing to this high pressure.
Therefore, if make the refrigerant interflow by two rotation compressing members 32,34 compressions upper support member 54 upside the discharge anechoic chamber be shaped as above-mentioned shape as shown in Figure 8, then can guarantee resistance to pressure.That is, the discharge anechoic chamber 162 of Fig. 8 is constructed as follows: the upside in upper support member 54 forms depressed part, utilizes the upper cap 66 of depressed part as lid sealed.In view of the above, even under the situation that contains the big refrigerant of height pressure reduction resemble the carbon dioxide, also can use the present invention.
(embodiment 14)
Then, other the embodiment with regard to compression system CS of the present invention describes.Be respectively Figure 14 and be embodiment as the compression system, multi-cylinder rotary compressor of compression system CS of the present invention, expression has the vertical profile side view of rotary compressor 10 of the internal high pressure type of the first and second rotation compressing member, and Figure 15 is the vertical profile side view (representing the section different with Fig. 1) of the rotary compressor 10 of presentation graphs 1.In addition, the compression system CS of present embodiment is a part that constitutes as to the cryogen circuit of the air conditioner of the indoor refrigerating plant that carries out air-conditioning.In addition, in Figure 14 and Figure 15, giving with Fig. 1 to Figure 13 of the various embodiments described above is the parts that can produce identical or similar effect for the parts of same-sign, omits its explanation.
In addition, on above-mentioned second cylinder 40, form the steering channel 72 of taking in second blade 52, in the outside of this steering channel 72, that is, the back side of second blade 52 forms the container 472A that the weak spring 76 of mechanism is suppressed in conduct that takes in as shown in figure 16.This container 472A is communicated with the pipe arrangement 75 described later that continuing at steering channel 72 sides and seal container 12 side openings on the opening of sealing container 12 sides, sealed in the seal container 12.
Above-mentioned weak spring 76 is to be used for second blade 52 is suppressed to second roller 48, and the one end contacts with the back side end of second blade 52, and the other end is fixed on the front end that is communicated with the pipe arrangement 75 that connects from seal container 12 sides of container 472A.In addition, the elastic force pressure of this weak spring 76 is set to smaller or equal to two rotation compressing members 32,34, or the suction side pressure of the first rotation compressing member 32 is applied elastic force pressure under the situation as the back pressure of second blade 52.
In addition, at the outlet side of accumulator 146, solenoid valve 200 is set at the middle part of the refrigerant ingress pipe 94 of the inlet side of seal container 12.This solenoid valve 200 is to be used to control the control valve unit that refrigerant flows into to second cylinder 40, by controller described later 210 controls as control gear.
Here, above-mentioned controller 210 constitutes the part of compression system CS of the present invention, the revolution of the electric element 14 of control rotary compressor 10.In addition, as mentioned above, control the switching of solenoid valve 106 of solenoid valve 105, the refrigerant pipe arrangement 102 of solenoid valve 200, the refrigerant pipe arrangement 101 of above-mentioned refrigerant ingress pipe 94.
Then, Figure 17 is the cryogen circuit figure that the above-mentioned air conditioner that compression system CS constituted is used in expression.That is, embodiment's compression system CS constitutes the part of the cryogen circuit of air conditioner shown in Figure 17, is to be made of above-mentioned rotary compressor 10 and controller 210 etc.The refrigerant discharge tube 96 of rotary compressor 10 is connected the inlet of outdoor heat exchanger 152.Above-mentioned controller 210 and rotary compressor 10, outdoor heat exchanger 152 are arranged on the not shown outdoor unit that goes out of air conditioner.The pipe arrangement that is connected with the outlet of this outdoor heat converter 152 is connected on the expansion valve 154 as the mechanism of decompressor, and the pipe arrangement that comes out from expansion valve 154 is connected with indoor side heat exchanger 156.These expansion valves 154 and indoor side heat exchanger 156 are arranged on the not shown indoor set that goes out of air conditioner.In addition, at the outlet side of indoor side heat exchanger 156, connecting the above-mentioned refrigerant pipe arrangement 100 of rotary compressor 10.
In addition,, be to use the refrigerant of HFC or HC class,, be to use for example existing machine oil such as mineral oil (oil), alkymer, ether oil, ester oil as the machine oil of lubricant oil as refrigerant.
With above-mentioned formation, the action of rotary compressor 10 is described then.
(1) first operation mode (load or the running during high load usually)
At first, use Figure 18, first operation mode that compresses work done with regard to two rotation compressing members 32,34 describes.In addition, Figure 18 is the figure that flows (thick line is represented flowing of refrigerant among the figure) that is illustrated in the refrigerant in first operation mode of rotary compressor 10.
According to the above-mentioned running instruction input that is arranged on the controller of the not shown indoor pusher side that goes out on the indoor set, electric element 14 energisings of 210 pairs of rotary compressors 10 of controller.At this moment, controller 210 is opened the solenoid valve 200 of refrigerant ingress pipe 94 and the solenoid valve 106 of refrigerant pipe arrangement 102 in electric element 14 energisings, closes the solenoid valve 105 (Figure 18) of refrigerant pipe arrangement 101.In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 75 are communicated with, and controller 210 is as the back pressure of second blade 52, and under the state of the discharge side pressure that applies two rotation compressing members 32,34, the revolution of the electric element 14 of control rotary compressor 10 starts.In addition, though controller 210 is controlled, in to electric element 14 energisings, open solenoid valve 200 and solenoid valve 106, close solenoid valve 105, but, as long as the switching of solenoid valve 200 and solenoid valve 105,106 is the prestarts at rotary compressor 10, for example, also can constitute: controller 210 is before to electric element 14 energisings, open solenoid valve 200 and solenoid valve 106, close solenoid valve 105.
Like this, if by wiring terminal 20 and the not shown distribution that goes out, to stator coil 28 energisings of electric element 14, then electric element 14 startings, rotor 24 rotations.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 10.At this moment, as mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 101 is closed, thus can not flow in the pipe arrangement 75 by two refrigerant that rotate the suction side of compressing members 32,34 of refrigerant pipe arrangement 100, but all flow in the accumulator 146.
Having flow into refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in the refrigerant ingress pipe 92 and refrigerant ingress pipe 94 of this accumulator 146 inner openings.The refrigerant gas that has entered refrigerant ingress pipe 92 is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32 through sucking path 58.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.
On the other hand, the refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 94 sucks path 60, is inhaled into the low pressure chamber side of second cylinder 40 of the second rotation compressing member 34.The action of refrigerant gas by second roller 48 and second blade 52 that is inhaled into the low pressure chamber side of second cylinder 40 is compressed.
When here, the inherent rotary compressor 10 of cryogen circuit starts is equilibrium pressure.Promptly, because rotary compressor 10 is after last running once stops, balance pressure gradually, if through scheduled time, then integral body becomes equilibrium pressure in the cryogen circuit, so like this, whole becoming under the situation of equilibrium pressure in cryogen circuit, started under the situation of rotary compressor 10, after rotary compressor 10 had just started, the pressure of the discharge side refrigerant of the two rotation compressing members 32,34 that are applied in as the back pressure of second blade 52 became equilibrium pressure roughly.Equally, the pressure in second cylinder 40 also becomes roughly equilibrium pressure.
Therefore, only constituting, under the situation that second roller suppresses, before the discharge side pressure of two rotation compressing members 32,34 rise to a certain degree, can not make second blade 52 follow second roller 48 in second blade 52 by back pressure.Therefore, in the second rotation compressing member 34, not compressing work done in fact, only is to be provided with first of spring 74 to rotate the compression work done that compressing member 32 is finished refrigerant.
In addition, because the state labile in just starting the back cryogen circuit, so the pulse of the discharge side pressure of two rotation compressing members 32,34 also enlarges markedly.Therefore, any mechanism of suppressing is not set on second blade 52, under the situation of starting under the state of the discharge side pressure that applies two rotation compressing members 32,34, there is following problems, promptly, because the pulse of the discharge side pressure of two rotation compressing members 32,34 causes the tracing ability of second blade 52 to worsen, second blade 52 conflicts with second roller 48, produces the conflict sound.
But, by the weak spring 76 that second blade 52 is suppressed to second roller 48 is set, even in second cylinder 40 and container 472A when be the starting of roughly isobaric (equilibrium pressure), also can pass through the elastic force pressure of weak spring 76, make second blade 52 follow second roller 48.In view of the above, can improve the tracing ability of second blade 52 when starting.In addition, because from when starting, even in the second rotation compressing member 34, also can compress work done, so can seek to improve the performance of air conditioner with this rotary compressor 10.
In addition, by the action compresses of second roller 48 and second blade 52, the refrigerant gas that becomes High Temperature High Pressure passes through in the exhaust port 49 from the hyperbaric chamber side of second cylinder 40, is discharged to and discharges in the anechoic chamber 64.Be discharged to the above-mentioned access 120 of refrigerant gas process of discharging anechoic chamber 64, be discharged to and discharge in the anechoic chamber 62, with the refrigerant gas interflow of being compressed by the above-mentioned first rotation compressing member 32.Then, the refrigerant gas at interflow is discharged in the seal container 12 through connecting the not shown hole that goes out of cap assembly 63.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, in the inflow outdoor heat exchanger 152.On the other hand, as mentioned above,, flow into the 472A of container through pipe arrangements 75 from refrigerant pipe arrangement 102 so pass through the part of the refrigerant of refrigerant discharge tube 96 owing to opened solenoid valve 106 by controller 210.
On the other hand, flow into the refrigerant gas heat release of outdoor heat converter 152, after expansion valve 154 decompressions, flow in the indoor side heat exchanger 156.By this indoor side heat exchanger 156 refrigerant evaporation,, bring into play cooling action, to indoor refrigeration by from the air of indoor circulation, absorbing heat.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
(2) from of the conversion of first operation mode to second operation mode (runnings of light hours)
Then, become the light load state as if indoor from above-mentioned common load or higher load condition, then controller 210 is changed to second operation mode from first operation mode.This second operation mode is to have only the first rotation compressing member 32 to compress the pattern of work done in fact, is to be light load indoor, and in above-mentioned first operation mode, the operation mode of electric element 14 for carrying out under the low speed rotation situation.Little ability zone at compression system CS, by having only the first rotation compressing member 32 to compress work done in fact, compare with the situation of compressing work done by first and second liang of cylinder 38,40, owing to can reduce the amount of the refrigerant gas of compression, so this amount also makes the revolution of electric element 14 rise in the light hours, improved the running efficiency of electric element 14, and, also make the leakage loss that reduces refrigerant become possibility.
Here, from first operation mode when second operation mode carries out mode switch, controller 210 makes electric element 14 with low speed rotation, for example, revolution is controlled at smaller or equal to 50Hz, with two the rotation compressing members 32 compression ratios be controlled at smaller or equal to 3.0.
Like this, controller 210 is closed above-mentioned solenoid valve 200 as shown in figure 19, cuts off the inflow to the refrigerant of second cylinder 40.Therefore, in the second rotation compressing member 34, do not finish the compression work done.If cut off inflow to the refrigerant of second cylinder 40, then become the pressure higher slightly (because second roller, 48 rotations in second cylinder 40 than the suction side pressure of two above-mentioned rotation compressing members 32,34, and, high pressure in the seal container 12 is some from the inflows such as gap of second cylinder 40, so become the pressure higher slightly than suction side pressure in second cylinder 40).
Like this, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101, closes the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 75 is communicated with, and the part of the refrigerant of the suction side of the first rotation compressing member 32 by refrigerant pipe arrangement 100 flows into the 472A of container through pipe arrangements 75 from refrigerant pipe arrangement 101.In view of the above, container 472A becomes the suction side pressure of the first rotation compressing member 32, as the back pressure of second blade 52, applies the suction side pressure of the first rotation compressing member 32.
Here, because weak spring 76 is set to suction side pressure smaller or equal to the first rotation compressing member 32 to the elastic force pressure of second roller 48, so as mentioned above, in second cylinder 40 the high pressure of suction side pressure than the first rotation compressing member 32, back pressure as second blade 52, by applying the suction side pressure of the first rotation compressing member 32, since the pressure of the container 472A that second blade 52 is suppressed to second roller 48 and the elastic force pressure of weak spring 76, and the pressure in second cylinder 40 are uprised.
Promptly, because by the pressure in second cylinder 40, the elastic force pressure that second blade 52 is suppressed to back pressure side (container 472A side) is greater than the pressure of the container 472A that second blade 52 is suppressed to second roller 48 and the elastic force pressure of weak spring 76, so second blade 52 is pressed with the container 472A thruster of second roller, 48 opposite sides to conduct, is incorporated in the steering channel 72.In view of the above,, second blade 52 is introduced in early days in second cylinder 40, be accommodated in the steering channel 72 when second operation mode is changed.
At this moment, back pressure side at second blade 53 does not have setting to suppress under the situation of mechanism, there is following problems, promptly, when conversion, second blade 52 is by the pressure pushing in second cylinder 40, when introducing in second cylinder 40, second blade 52 conflicts with the wall portion of container 472A or the front end of pipe arrangement 75, produces the conflict sound.But,, can when second blade 52 is introduced, absorb impact in second cylinder 40 by weak spring 76 by weak spring 76 is set.In view of the above, can possibly avoid conflicting of second blade 52 and second roller 48, produce the such problem of conflict sound, can be transformed into second operation mode that has only the first rotation compressing member 32 to finish the compression work done in fact.
(3) second operation modes
Then, just the action of the rotary compressor in second operation mode 10 describes.In addition, with above-mentioned identical when second operation mode is changed from first operation mode, the solenoid valve 200 that is refrigerant ingress pipe 94 is closed, and the solenoid valve 105 of refrigerant pipe arrangement 101 is opened, the pent like this state of the solenoid valve 106 of refrigerant pipe arrangement 102 (Figure 19).Flowing into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation from the refrigerant pipe arrangement 100 of rotary compressor 10, only is that refrigerant gas enters in the refrigerant discharge tube 92 of this accumulator 146 inner openings.The refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
On the one hand, because the solenoid valve of refrigerant pipe arrangement 101 105 controlled devices 210 are opened, flow into the 472A of container through pipe arrangements 75 from refrigerant pipe arrangement 101 so pass through the refrigerant of the part of refrigerant pipe arrangement 100.In view of the above, container 472A becomes the suction side pressure of the first rotation compressing member 32, as the back pressure of second blade 52, applies the suction side pressure of this first rotation compressing member 32.
On the other hand, the action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure, through in the not shown exhaust port that goes out, be discharged to and discharge in the anechoic chamber 62 from the hyperbaric chamber side of first cylinder 38.Be discharged to the refrigerant gas of discharging in the anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, in the inflow outdoor heat exchanger 152.In addition, because aforesaid solenoid valve 106 is closed, thus can not flow in the pipe arrangement 75 at the refrigerant discharge tube 96 first mobile refrigerant that rotate the discharge side of compressing member 32, but in whole inflow outdoor heat exchanger 152.Like this, flow into the refrigerant gas heat release of outdoor heat converter 152, after expansion valve 154 decompressions, flow in the indoor side heat exchanger 156.Here, the refrigerant evaporation at this moment, by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 10.
In addition, in this second operation mode, close above-mentioned solenoid valve 200 by making controller 210, to cut off state running to the refrigerant inflow of second cylinder 40, in second operation mode, the pressure in second cylinder 40 is maintained at the state higher than the back pressure of second blade 52 like this.Therefore, second blade 52 is because the pressure in second cylinder 40, be pushed to as with the container 472A side (weak spring 76 sides) of the opposite side of second roller 48, can not appear in second cylinder 40.In view of the above, in the running of second operation mode, can possibly avoid second blade 52 to appear in second cylinder 40, conflict, produce the such problem of conflict sound with second roller 48.
(4) from of the conversion of second operation mode to first operation mode
On the other hand, become common load or higher load condition as if indoor from above-mentioned light load state, then controller 210 is changed to first operation mode from second operation mode.Here, for describing from the switching motion of second operation mode to first operation mode.In this case, controller 210 is controlled, and makes electric element 14 low speed rotation (revolution is smaller or equal to 50Hz), and the compression ratio that makes two rotation compressing members 32,34 is smaller or equal to 3.0.Controller 210 is opened solenoid valve 200, makes refrigerant flow into second cylinder 40, simultaneously, closes the solenoid valve 105 of refrigerant pipe arrangement 101, opens the solenoid valve 106 of refrigerant pipe arrangement 102.
In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 75 are communicated with, and the discharge side refrigerant of two rotation compressing members 32,34 flows among the 472A of container, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
Back pressure as second blade 52, by applying the discharge side pressure of two rotation compressing members 32,34, owing to be in a ratio of very high pressure in the container 472A of second blade 52 and second cylinder 40, so second blade 52 is by this high pressure and the weak spring 76 of container 472A, be pushed to second roller, 48 sides, follow.In view of the above, in the second rotation compressing member 34, begin to compress work done once more.
Like this, by weak spring 76 is set, from second operation mode when first operation mode is changed, second blade 52 can be suppressed fully to second roller, 48 sides, can make it follow second roller 48 in early days.
In view of the above, improved, improved running efficiency at tracing ability from second blade 52 of second operation mode during to the conversion of first operation mode, and, the generation of the conflict sound of second blade 52 can be avoided.
As above detailed description, according to the present invention, can seek to improve performance and the reliability of the compression system CS with rotary compressor 10, this rotary compressor 10 can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member 32,34 compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member 32 to compress work done in fact.
In view of the above, by using this compression system CS, constitute the cryogen circuit of air conditioner, can improve the running efficiency and the performance of this air conditioner, also make to seek to reduce to consume electric power and become possibility.
In addition, in the present embodiment, at first operation mode, during starting and from second operation mode to first operation mode when running conversion, open the solenoid valve 106 of refrigerant pipe arrangement 102 by controller 210, be communicated with refrigerant pipe arrangement 102 and pipe arrangement 75, make two rotation compressing members 32,34 discharge side refrigerant flows among the 472A of container, back pressure as second blade 52, two rotation compressing members 32 have been applied, 34 discharge side pressure, but be not limited only to this, also can be back pressure, apply two rotation compressing members 32 as second blade 52, intermediate pressure between 34 suction side pressure and the discharge side pressure.
In this case, for example as shown in figure 20, if close solenoid valve 105 and solenoid valve 106 by controller 210, make in the pipe arrangement 75 that is communicated with the container 472A of second blade 52 and become enclosed space, then because the refrigerant in many second cylinders 40 flows into the 472A of container between second blade 52 and container 70A, so the pressure in the container 472A of second blade 52 becomes the suction side pressure of two rotation compressing members 32,34 and discharges intermediate pressure between the side pressure, this intermediate pressure is applied in as the back pressure of second blade 52.
Like this,, apply under the situation of intermediate pressure,, just second blade 52 can be suppressed fully to second roller 48, it is followed in early days also by apply the elastic force pressure of weak spring 76 same as the previously described embodimentsly in back pressure as second blade 52.
(embodiment 15)
Then, the compression system, multi-cylinder rotary compressor (rotary compressor) with regard to other embodiments' of the present invention compression system describes.Figure 21 and Figure 22 are respectively the vertical profile side views of rotary compressor 310 in the present embodiment.In addition, in Figure 21 and Figure 22, giving with Fig. 1 to Figure 20 is the parts that can produce identical or similar effect for the parts of same-sign.
In Figure 22, the 176th, the weak spring that tension load is used is arranged on the outside of steering channel 72 of second blade 52 of taking in the second rotation compressing member 34, that is, and on the container 472A of the back side of second blade 52.This weak spring 176 be used for second blade 52 to the opposite side traction of second roller 48, the one end is installed in the front end of second blade 52, the other end is installed on the pipe arrangement 75.In addition, the tensile force of this weak spring 176 is smaller or equal to two rotation compressing members 32,34, or the suction side pressure of the first rotation compressing member 32 is applied elastic force pressure under the situation as the back pressure of second blade 52.
, use Figure 23 here, the installation method of this weak spring 176 is described.This weak spring 176 forms the part of the diameter at two ends greater than other.Like this, second blade 52 do not contact the center of the end of a side with second roller 48, form the groove 52A consistent with an end of this weak spring 176, an end of weak spring 176 embeds this groove 52A.Equally, on the inwall of the pipe arrangement 75 that is connected with container 472A, form the groove 75A consistent with the other end of this weak spring 176, the other end of weak spring 176 embeds this groove 75A.In view of the above, weak spring 176 can be installed in the back side of second blade 52, can with second blade 52 to the opposite side traction of second roller 48.In addition, be not limited only to resemble and use the diameter at two ends big above-mentioned, the situation of the weak spring 176 that other part is little, also can install like this, for example as shown in figure 24, under the situation of using the identical weak spring of integral diameter,, then can make weak spring can not run into second blade 52 if enlarge the spacing at the two end part of this spring.In addition, also can be as shown in figure 25, at an end of weak spring hook 177 is set, will link up with and 177 be installed on second blade 52 (on second blade 52, be formed for installing link up with 177 hole 178), draw second blade 52.
With above-mentioned formation, the action of rotary compressor 310 is described.
(1) first operation mode (load or the running during high load usually)
At first, first operation mode that compresses work done with regard to two rotation compressing members 32,34 describes.According to the above-mentioned running instruction input that is arranged on the controller of the not shown indoor pusher side that goes out on the indoor set, electric element 14 energisings of 210 pairs of rotary compressors 310 of controller.At this moment, controller 210 is opened the solenoid valve 106 of refrigerant pipe arrangement 102 in electric element 14 energisings, closes the solenoid valve 105 of refrigerant pipe arrangement 101.In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 75 is communicated with, and controller 210 is in the back pressure as second blade 52, applies under the state of discharge side pressure of two rotation compressing members 32,34, and the revolution of the electric element 14 of control rotary compressor 310 starts.In addition, though controller 210 is controlled, in to electric element 14 energisings, open solenoid valve 106, close solenoid valve 105, but as long as the switching of solenoid valve 105,106 is the prestarts at rotary compressor 310, for example, also can be controller 210 to electric element 14 energising front opening solenoid valves 106, close solenoid valve 105.
Like this, if by wiring terminal 20 and the not shown distribution that goes out, to stator coil 28 energisings of electric element 14, then electric element 14 startings, rotor 24 rotations.By this rotation, first and second roller 46,48 is entrenched on the eccentric part up and down 42,44 that is wholely set with running shaft 16, eccentric rotation in first and second cylinder 38,40.
In view of the above, refrigerant flows in the accumulator 146 from the refrigerant pipe arrangement 100 of rotary compressor 310.At this moment, as mentioned above, because the solenoid valve 105 of refrigerant pipe arrangement 101 is closed, thus can not flow in the pipe arrangement 75 by two refrigerant that rotate the suction side of compressing members 32,34 of refrigerant pipe arrangement 100, but all flow in the accumulator 146.
Having flow into refrigerant in the accumulator 146 here by after the gas-liquid separation, only is that refrigerant gas enters in the refrigerant ingress pipe 92 and refrigerant ingress pipe 94 of this accumulator 146 inner openings.The refrigerant gas that has entered refrigerant ingress pipe 92 is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32 through sucking path 58.
The action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure,, be discharged to and discharge in the anechoic chamber 62 by in the not shown exhaust port that goes out from the hyperbaric chamber side of first cylinder 38.
When here, the inherent rotary compressor 310 of cryogen circuit starts is equilibrium pressure.Promptly, because at rotary compressor 310 after last running once stops, balance pressure gradually, if through scheduled time, then integral body becomes equilibrium pressure in the cryogen circuit, so whole becoming under the situation of equilibrium pressure in cryogen circuit like this started under the situation of rotary compressor 310, after rotary compressor 310 had just started, the pressure of the discharge side refrigerant of the two rotation compressing members 32,34 that are applied in as the back pressure of second blade 52 became equilibrium pressure roughly.Equally, the pressure in second cylinder 40 also becomes roughly equilibrium pressure.
Therefore, before the discharge side pressure of two rotation compressing members 32,34 rises to a certain degree, can not make second blade 52 follow second roller 48.Therefore, in the second rotation compressing member 34, not compressing work done in fact, only is to be provided with first of spring 74 to rotate the compression work done that compressing member 32 is finished refrigerant.
In this case, because the state labile in just starting the back cryogen circuit, so the pulse of the discharge side pressure of two rotation compressing members 32,34 also enlarges markedly.Therefore, under the situation of starting under the state of the discharge side pressure that applies two rotation compressing members 32,34, there is following problems, promptly, because the pulse of the discharge side pressure of two rotation compressing members 32,34 causes the tracing ability of second blade 52 to worsen, second blade 52 conflicts with second roller 48, produces the conflict sound.
But, in the present embodiment, by being provided with second blade 52 to the weak spring of using with the tension load of the opposite side traction of second roller 48 176, tensile force by weak spring 76, because second blade 52 can not appear in second cylinder 40, so can possibly avoid second blade 52 to conflict, produce the such problem of conflict sound with second roller 48.
On the other hand,, be discharged to the refrigerant gas of discharging in the anechoic chamber 62, be discharged in the seal container 12 through connecting the not shown hole that goes out of cap assembly 63 by above-mentioned first rotation compressing member 32 compression.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, in the inflow outdoor heat exchanger 152.On the other hand,, opened solenoid valve 106, flowed into the 472A of container through pipe arrangements 75 from refrigerant pipe arrangement 102 so pass through the part of the refrigerant of refrigerant discharge tube 96 by controller 210 because as mentioned above.
On the other hand, the refrigerant gas heat release of inflow outdoor heat exchanger 152 after expansion valve 154 decompressions, flows in the indoor side heat exchanger 156.By this indoor side heat exchanger 156 refrigerant evaporation,, bring into play cooling action, to indoor refrigeration by from the air of indoor circulation, absorbing heat.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 310.
On the other hand, if starting rotary compressor 310 through the stipulated time, then produces height pressure reduction gradually in cryogen circuit 10.That is, the suction side pressure of the first rotation compressing member 32 becomes low pressure, and discharging side pressure becomes high pressure.In view of the above, second blade 52 is discharged side pressure by this, follows second roller 48, even in the second rotation compressing member 34, also finish the compression work done.Here, because the tensile force of weak spring 176 is the elastic force pressure smaller or equal to the situation that the suction side pressure of the first rotation compressing member 32 (or two rotation compressing members 32,34) is applied as the back pressure of second blade 52 as mentioned above, so can make second blade 52 not be subjected to follow second roller 48 as the influence of the high pressure of this discharge side pressure.
In addition, by the action compresses of second roller 48 and second blade 52, the refrigerant gas that becomes High Temperature High Pressure passes through in the exhaust port 49 from the hyperbaric chamber side of second cylinder 40, is discharged to and discharges in the anechoic chamber 64.Be discharged to the above-mentioned access 120 of refrigerant gas process of discharging in the anechoic chamber 64, be discharged to and discharge in the anechoic chamber 62, with the refrigerant gas interflow of being compressed by the above-mentioned first rotation compressing member 32.Then, the refrigerant gas at interflow is discharged in the seal container 12 through connecting the not shown hole that goes out of cap assembly 63.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, in the inflow outdoor heat exchanger 152.On the other hand, because as mentioned above, by controller 210, solenoid valve 106 is opened, and flows into the 472A of container through pipe arrangements 75 from refrigerant pipe arrangement 102 so pass through the part of the refrigerant of refrigerant discharge tube 96.
On the other hand, flow into the refrigerant gas heat release in the outdoor heat converter 152, after expansion valve 154 decompressions, flow in the indoor side heat exchanger 156.By this indoor side heat exchanger 156 refrigerant evaporation,, bring into play cooling action, to indoor refrigeration by from the air of indoor circulation, absorbing heat.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 310.
(2) from of the conversion of first operation mode to second operation mode (runnings of light hours)
Then, become the light load state as if indoor from above-mentioned common load or higher load condition, then controller 210 is changed to second operation mode from first operation mode.This second operation mode is to have only the first rotation compressing member 32 to compress the pattern of work done in fact, is to be light load indoor, and in above-mentioned first operation mode, the operation mode of electric element 14 for carrying out under the low speed rotation situation.Little ability zone at compression system CS, by having only the first rotation compressing member 32 to compress work done in fact, compare with the situation of compressing work done by first and second liang of cylinder 38,40, owing to can reduce the amount of the refrigerant gas of compression, so this amount also makes the revolution of electric element 14 rise in the light hours, improved the running efficiency of electric element 14, and, also make the leakage loss that reduces refrigerant become possibility.
Here, from first operation mode when second operation mode carries out mode switch, controller 210 makes electric element 14 with low speed rotation, for example, revolution is controlled at smaller or equal to 50Hz, with two the rotation compressing members 32 compression ratios be controlled at smaller or equal to 3.0.
Like this, controller 210 is opened the solenoid valve 105 of refrigerant pipe arrangement 101, closes the solenoid valve 106 of refrigerant pipe arrangement 102.In view of the above, refrigerant pipe arrangement 101 and pipe arrangement 75 is communicated with, and the part of the refrigerant of the suction side of two rotation compressing members 32,34 by refrigerant pipe arrangement 100 flows into the 472A of container through pipe arrangements 75 from refrigerant pipe arrangement 101.In view of the above, container 472A becomes the suction side pressure of two rotation compressing members 32,34, as the back pressure of second blade 52, applies the suction side pressure of two rotation compressing members 32,34.
Become the suction side pressure of two identical rotation compressing members 32,34 here, in second cylinder 40 with the back pressure of second blade 52.At this moment, back pressure side at second blade 52 is not provided with under the situation of weak spring 176, because be identical pressure with second blade 52 in second cylinder 40 as mentioned above, so there is following problems, that is, second blade 52 is needed the time from second cylinder, 40 interior introducings, during this period, second blade 52 conflicts with second roller 48, produces the conflict sound.
But by the weak spring 176 that tension load is used is set, by the tensile force of this weak spring 176, second blade, 52 quilts are housed in it in steering channel 72 to the container 472A side traction of conduct with an opposite side of second roller 48.In view of the above,, second blade 52 is introduced in early days in second cylinder 40, be accommodated in the steering channel 72 when second operation mode is changed.
In view of the above, can possibly avoid second blade 52 to conflict, produce the such problem of conflict sound, can be transformed into second operation mode that has only the first rotation compressing member 32 to finish the compression work done in fact with second roller 48.
(3) second operation modes
Then, just the action of the rotary compressor in second operation mode 310 describes.In addition, with above-mentioned identical when second operation mode is changed, be that the solenoid valve 105 of refrigerant pipe arrangement 101 is opened from first operation mode, the solenoid valve 106 of refrigerant pipe arrangement 102 is closed such state.Flowing into low-pressure refrigerant in the accumulator 146 here by after the gas-liquid separation from the refrigerant pipe arrangement 100 of rotary compressor 310, only is that refrigerant gas enters in the refrigerant discharge tube 92 of this accumulator 146 inner openings.The refrigerant gas process that enters into the low pressure of refrigerant ingress pipe 92 sucks path 58, is inhaled into the low pressure chamber side of first cylinder 38 of the first rotation compressing member 32.
On the one hand, because the solenoid valve of refrigerant pipe arrangement 101 105 controlled devices 210 are opened, flow into the 472A of container through pipe arrangements 75 from refrigerant pipe arrangement 101 so pass through a part of refrigerant of refrigerant pipe arrangement 100.In view of the above, container 472A becomes the suction side pressure of the first rotation compressing member 32, as the back pressure of second blade 52, applies the suction side pressure of this first rotation compressing member 32.
On the other hand, the action of refrigerant gas by first roller 46 and first blade 50 that is inhaled into the low pressure chamber side of first cylinder 38 is compressed, become the refrigerant gas of High Temperature High Pressure, through in the not shown exhaust port that goes out, be discharged to and discharge in the anechoic chamber 62 from the hyperbaric chamber side of first cylinder 38.Be discharged to the refrigerant gas of discharging anechoic chamber 62 by connecting the not shown hole that goes out of cap assembly 63, be discharged in the seal container 12.
Thereafter, the refrigerant in the seal container 12 is discharged to the outside from the refrigerant discharge tube 96 on the end cap 12B that is formed at seal container 12, in the inflow outdoor heat exchanger 152.In addition, because as mentioned above, solenoid valve 106 is closed, thus can not flow in the pipe arrangement 75 at the refrigerant discharge tube 96 first mobile refrigerant that rotate the discharge side of compressing member 32, but in whole inflow outdoor heat exchanger 152.Like this, flow into the refrigerant gas heat release of outdoor heat converter 152, after expansion valve 154 decompressions, flow in the indoor side heat exchanger 156.Here, the refrigerant evaporation at this moment, by from absorbing heat, is brought into play cooling action, to indoor refrigeration the air of indoor circulation.Then, carry out repeatedly refrigerant is discharged from indoor side heat exchanger 156, be drawn into the circulation of rotary compressor 310.
In addition, by above-mentioned weak spring 176, in this second operation mode, second blade, 52 quilts can not appear in second cylinder 40 to drawing with the container 472A side (weak spring 176 sides) of an opposite side that becomes second roller 48.In view of the above, in the running of second operation mode, can possibly avoid second blade 52 to appear in second cylinder 40, conflict, produce the such problem of conflict sound with second roller 48.
(4) from of the conversion of second operation mode to first operation mode
On the other hand, become common load or higher load condition as if indoor from above-mentioned light load state, then controller 210 is changed to first operation mode from second operation mode.Here, just describe from the switching motion of second operation mode to first operation mode.In this case, controller 210 is controlled, and makes electric element 14 low speed rotation (revolution is smaller or equal to 50Hz), and the compression ratio that makes two rotation compressing members 32,34 is smaller or equal to 3.0.Controller 210 is closed the solenoid valve 105 of refrigerant pipe arrangement 101, opens the solenoid valve 106 of refrigerant pipe arrangement 102.
In view of the above, refrigerant pipe arrangement 102 and pipe arrangement 75 are communicated with, and the discharge side refrigerant of two rotation compressing members 32,34 flows among the 472A of container, as the back pressure of second blade 52, apply the discharge side pressure of two rotation compressing members 32,34.
Back pressure as second blade 52, by applying the discharge side pressure of two rotation compressing members 32,34, because it is second blade 52 is bigger than the tensile force of weak spring 176 to the elastic force pressure that second roller 48 suppresses, so second blade 52 is by this high pressure of container 472A, be pushed to second roller, 48 sides, follow.In view of the above, in the second rotation compressing member 34, begin to compress work done once more.
As above detailed description, according to the present invention, can seek to improve performance and the reliability of the compression system CS with rotary compressor 310, this rotary compressor 310 can be changed and be used first operation mode and second operation mode, at above-mentioned first operation mode, first and the second rotation compressing member 32,34 compresses work done, at above-mentioned second operation mode, has only the first rotation compressing member 32 to compress work done in fact.
In view of the above, by using this compression system CS, constitute the cryogen circuit of air conditioner, can improve the running efficiency and the performance of this air conditioner, also make to seek to reduce to consume electric power and become possibility.
In addition, in the present embodiment, at first operation mode, during starting and from second operation mode to first operation mode when running conversion, by controller 210, open the solenoid valve 106 of refrigerant pipe arrangement 102, be communicated with refrigerant pipe arrangement 102 and pipe arrangement 75, make two rotation compressing members 32,34 discharge side refrigerant flows among the 472A of container, back pressure as second blade 52, two rotation compressing members 32 have been applied, 34 discharge side pressure, but being not limited only to this, also can be the back pressure as second blade 52, applies two rotation compressing members 32, intermediate pressure between 34 suction side pressure and the discharge side pressure.Even in this case, because the tensile force of weak spring 176 is set to smaller or equal to applying elastic force pressure under the situation as the back pressure of second blade 52 with above-mentioned two rotation compressing members 32,34 or with the suction side pressure of the first rotation compressing member 32, so can make second blade 52 follow second roller 48 insusceptibly.
In addition, in the various embodiments described above, as refrigerant, be to use the refrigerant of HFC or HC class, but also can use the big refrigerant of height pressure reduction of carbon dioxide etc., for example, as refrigerant, also can use the refrigerant after carbon dioxide and PAG (polyglycols) combination.In this case, because the refrigerant by each rotation compressing member 32,34 compression is very high high pressure, so if make discharge anechoic chamber 62 become the shape that covers the upside of upper support member 54 by cap assembly 63 as the various embodiments described above, then exist, cause the possibility of cap assembly 63 breakages owing to this high pressure.
Therefore, if make the refrigerant interflow by two rotation compressing members 32,34 compressions upper support member 54 upside the discharge anechoic chamber be shaped as shown in Figure 8 shape, then can guarantee resistance to pressure.That is, the discharge anechoic chamber 162 of Fig. 8 is constructed as follows: the upside in upper support member 54 forms depressed part, utilizes the upper cap 66 of depressed part as the lid of the thickness with regulation sealed.In view of the above, even under the situation that contains the big refrigerant of height pressure reduction resemble the carbon dioxide, also can use the present invention.
In addition, in the various embodiments described above, use running shaft 16 to be illustrated for the vertical rotary compressor of putting type, this invention can certainly be applied in to be used under the situation of running shaft as the rotary compressor of horizontal arrangement type.
Have again, in the various embodiments described above, be to use the rotary compressor of two cylinders, can certainly be applied in the compression system of compression system, multi-cylinder rotary compressor with the rotation compressing member more than three cylinders or three cylinders.

Claims (2)

1. compression system, multi-cylinder rotary compressor, this compression system, multi-cylinder rotary compressor is being taken in driving element and is being rotated compressing member by the rotation shaft-driven first and second of this driving element in seal container, this first and second rotation compressing member is made of first and second cylinder, first and second roller, first and second blade, this first and second roller is chimeric with the eccentric part that forms on above-mentioned running shaft, eccentric rotation in above-mentioned each cylinder respectively; This first and second blade with this first and second roller contact; Low-pressure chamber side and hyperbaric chamber side will be divided into respectively in above-mentioned each cylinder; Simultaneously; This compression system, multi-cylinder rotary compressor suppresses above-mentioned first blade by spring members to above-mentioned first roller; Can change and be used first operation mode and second operation mode; At above-mentioned first operation mode; Above-mentioned two rotary compression elements compress work done; At above-mentioned second operation mode; Only have in fact the above-mentioned first rotary compression element to compress work done; It is characterized in that
Be provided with above-mentioned second blade suppressed mechanism to what above-mentioned second roller suppressed,
Make this elastic force pressure that suppresses mechanism apply elastic force pressure under the situation as the back pressure of above-mentioned second blade smaller or equal to suction side pressure with the above-mentioned two rotation compressing members or the first rotation compressing member.
2. compression system, multi-cylinder rotary compressor as claimed in claim 1 is characterized in that, is provided for controlling the control valve unit to the refrigerant circulation of above-mentioned second cylinder,
In above-mentioned first operation mode, make refrigerant flow into above-mentioned second cylinder by above-mentioned control valve unit, and back pressure as above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members and the intermediate pressure between the discharge side pressure, or apply the above-mentioned two discharge side pressure of rotating compressing members, in above-mentioned second operation mode, cut off to above-mentioned second cylinder inflow refrigerant by above-mentioned control valve unit, and, as the back pressure of above-mentioned second blade, apply the suction side pressure of above-mentioned two rotation compressing members.
CN2008101340490A 2004-07-08 2005-06-07 Multi-cylinder rotary compressor Active CN101344089B (en)

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JP2004201915A JP4404708B2 (en) 2004-07-08 2004-07-08 Compression system and refrigeration system using the same
JP2004201915 2004-07-08
JP2004201601A JP2006022723A (en) 2004-07-08 2004-07-08 Compression system and refrigerating apparatus using the same
JP2004203001A JP2006022766A (en) 2004-07-09 2004-07-09 Multi-cylinder rotary compressor
JP2004202994A JP4726444B2 (en) 2004-07-09 2004-07-09 Multi-cylinder rotary compressor
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CN101344086B (en) 2010-06-02
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CN101344087A (en) 2009-01-14
CN101344088A (en) 2009-01-14

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