CN102037217B

CN102037217B - Fluid machine and refrigeration cycle device

Info

Publication number: CN102037217B
Application number: CN200980117999.5A
Authority: CN
Inventors: 和田贤宣; 长谷川宽; 松井大; 田口英俊; 咲间文顺
Original assignee: Matsushita Electric Industrial Co Ltd
Current assignee: Panasonic Holdings Corp
Priority date: 2008-05-22
Filing date: 2009-05-20
Publication date: 2013-04-17
Anticipated expiration: 2029-05-20
Also published as: WO2009142014A1; JP5296065B2; US20110100025A1; JPWO2009142014A1; EP2295721A1; CN102037217A

Abstract

A fluid machine (110) is comprised of a power recovery mechanism (105) which recovers power from the working fluid, a sub-compressor (102) which is driven by the recovered power, and a shaft (12) which links the power recovery mechanism (105) and the sub-compressor (102) so that the recovered power is transmitted from the power recovery mechanism (105) to the sub-compressor (102). In the power recovery mechanism (105), a first intake port (26) and a second intake port (27) are provided to open and close accompanying the rotation of a piston (21) and let the working fluid flows into a working chamber (23a) on the high pressure side. The second intake port (27) is provided at a position facing the first intake port (26) with respect to the axial direction of the shaft (12).

Description

Fluid machinery and refrigerating circulatory device

Technical field

The present invention relates to a kind of fluid machinery and refrigerating circulatory device.

Background technique

Usually, the refrigerant circuit of refrigerating circulatory device has the structure that compressor, radiator, expansion valve and vaporizer are connected successively.Refrigeration agent changes when following from high pressure to inflated with low pressure in expansion valve, emits at this moment internal energy.Pressure difference between the low voltage side of refrigerant circuit (vaporizer side) and high pressure side (heat sink side) is larger, and the internal energy of emitting is larger, so the energy efficiency of refrigeration cycle descends.In view of such problem, the technology of the internal energy of various recovery refrigeration agents is proposed.

Fig. 8 is at TOHKEMY 2004-324595 communique and the international structural drawing that discloses disclosed, existing refrigerating circulatory device 501 in No. 2008/050654 communique.Refrigerating circulatory device 501 has the refrigerant circuit that is connected in sequence by radiator 502, power recovery mechanism 503 (decompressor), vaporizer 504, volume type blower 505 (auxiliary compressor) and main compressor 506.Fluid machinery 507 has power recovery mechanism 503, volume type blower 505, axle 508 and accommodates their seal container 509.Power recovery mechanism 503 and volume type blower 505 are connected to each other by axle 508, so that the power that is reclaimed by power recovery mechanism 503 transmits to volume type blower 505.The part of the internal energy of emitting from refrigeration agent in power recovery mechanism 503 converts the torque of axle 508 to and transmits to volume type blower 505, and utilizes as the power that is used for driving volume type blower 505.The refrigeration agent preparation that volume type blower 505 will be drawn into before the main compressor 506 is boosted.

The starting of convection cell machinery 507 in TOHKEMY 2004-324595 communique (independent starting) as described below.When starting main compressor 506, in the spraying pipe of volume type blower 505, produce negative pressure at first.So, produce the torque that makes axle 508 rotations.Next, in the suction pipe of power recovery mechanism 503, produce positive power, thus, 503 rotations of power recovery mechanism.

Yet different from the main compressor 506 that is subject to starting force by motor, the fluid machinery 507 only malleation in the suction pipe of the negative pressure in the spraying pipe of volume type blower 505 or power recovery mechanism 503 is accepted starting force.Therefore, possibly can't guarantee sufficient starting force.

The concrete example of fluid machinery 507 discloses in No. 2008/050654 communique in the world and discloses.Fig. 9 is the sectional view that discloses the power recovery mechanism in the disclosed fluid machinery in No. 2008/050654 communique in the world.Power recovery mechanism 503 has clutch release slave cylinder 510, piston 513 and blade 511.Refrigeration agent flows into working rooms 515 by suction pipe 514, follows the rotation of axle 508 and flows out to the outside of power recovery mechanism 503 by spraying pipe 516.According to this power recovery mechanism 503, overlapping at piston 513 and suction port 517 and in the situation about stopping, when starting, in the malleation of suction pipe 514 interior generations piston 513 is pressed towards end plate (member of inaccessible clutch release slave cylinder 510) next time.That is, piston 513 and the frictional ratio between the end plate when starting is larger.Therefore, need more torque in order to make piston 513 rotations.This smooth starting for fluid machinery 507 is not preferred.

Patent documentation 1: JP 2004-324595 communique

Patent documentation 2: the international communique that discloses No. 2008/050654

Summary of the invention

The present invention is in view of the above problems and proposes, and its purpose is to provide a kind of fluid machinery of the starting that is fit to be well on.In addition, the present invention also provides the refrigerating circulatory device that uses this fluid machinery.

That is, the invention provides a kind of fluid machinery, wherein, have:

Power recovery mechanism, it reclaims power from working fluid;

Auxiliary compressor, it is by the motivational drive of described recovery;

Axle, it links described power recovery mechanism and described auxiliary compressor, so that the power of described recovery is delivered to described auxiliary compressor from described power recovery mechanism,

Described power recovery mechanism comprises:

(a1) the first obstruction component;

(b1) the second obstruction component, itself and described the first obstruction component are opposed;

(c1) clutch release slave cylinder, it is along a part that circumferentially centers on described axle, and two ends are inaccessible by described the first obstruction component and described the second obstruction component;

(d1) piston, it is installed on described axle in described clutch release slave cylinder, and self outer circumferential face and the inner peripheral surface of described clutch release slave cylinder between form the working room;

(e1) partition member, it is separated into described working room the working room of on high-tension side working room and low voltage side;

(f1) the first suction port, it is arranged at described the first obstruction component, and follows the rotation of described piston and open and close, so that working fluid flows into described on high-tension side working room;

(g1) the second suction port, its be arranged at described the second obstruction component, described axle axially on the position relative with described the first suction port, and follow the rotation of described piston and open and close, so that working fluid flows into described on high-tension side working room.

The invention effect

According to the invention described above, power recovery mechanism has the first suction port and the second suction port that is arranged at the position relative with the first suction port.Therefore, the malleation that produces in suction pipe acts on upper surface and this two side of lower surface of piston by first and second suction port.That is the power of, piston being pressed towards obstruction component offsets.Thus, according to the present invention, can provide the fluid machinery of the starting that is suitable for being well on.According to circumstances, do not need the help of the auxiliary drive of motor etc. yet.

Description of drawings

Fig. 1 is the structural drawing of the related refrigerating circulatory device of one embodiment of the present invention.

Fig. 2 A is the longitudinal section of fluid machinery shown in Figure 1.

Fig. 2 B is longitudinal section under the cut-out angle different from the cut-out angle of Fig. 2 A, fluid machinery.

Fig. 3 is the amplification sectional view that is arranged at the suction path of power recovery mechanism.

Fig. 4 is the cross-sectional view along the D1-D1 line of fluid machinery shown in Figure 2.

Fig. 5 is the schematic diagram of movements of power recovery mechanism.

Fig. 6 is the cross-sectional view along the D2-D2 line of fluid machinery shown in Figure 2.

Fig. 7 is the schematic diagram of movements of auxiliary compressor.

Fig. 8 is the structural drawing of existing refrigerating circulatory device.

Fig. 9 is the cross-sectional view of existing decompressor.

Embodiment

Below, with reference to the description of drawings embodiments of the present invention.But the present invention does not limit to following mode of execution.

In the present embodiment, according to its characteristic, with the fluid pressure motor that usually only uses for incompressible working fluid as with power recovery mechanism and the auxiliary compressor use of constrictive refrigeration agent as the refrigerating circulatory device of working fluid.Thus, improve the energy efficiency of the running of refrigerating circulatory device.

In this manual, " fluid pressure motor " refers to that the pressure difference between the pressure of working fluid of the pressure of the working fluid (being typically refrigeration agent) because of the suction side and ejection side rotates, and do not make the working fluid Volume Changes of suction and begins to spray the motor of stroke.The pressure of the working fluid of suction side refers to the pressure for the working fluid that is drawn into the fluid pressure motor.The pressure of the working fluid of ejection side refers to from the pressure of the working fluid of fluid pressure motor ejection.In detail, the fluid pressure motor refers to not make the motor of working fluid Volume Changes before the ejection stroke begins.In addition, in ejection after stroke begins, in other words be the inside of fluid pressure motor with after the ejection path is communicated with, the inside of fluid pressure motor is depressurized or boosts, working fluid expansion or compress.

Disclosed in this manual technology is using carbon dioxide etc. to become in the refrigerating circulatory device of refrigeration agent of supercritical state especially effective in the high pressure side.Become in the situation of refrigeration agent of supercritical state using in the high pressure side, the expansivity of the refrigeration agent that the density of the refrigeration agent in the outlet port of radiator and the ratio of the density of the refrigeration agent of the ingress of vaporizer are represented is very little.In the energy of emitting when this refrigeration agent expands, the internal energy of emitting owing to pressure drop accounts for major part.The internal energy of emitting owing to the increase of specific volume seldom, it according to circumstances becomes less than the overexpansion loss.Thus, abandon reluctantly reclaiming the recovery of the internal energy of emitting owing to the increase of specific volume, employing can prevent the structure of generation and comparing more favourable aspect the energy recovery efficiency of the full dose of attempting reclaiming the internal energy of emitting of overexpansion loss.

In addition, in the present embodiment, the fluid pressure motor that uses as power recovery mechanism and auxiliary compressor sucks the suction stroke of refrigeration agent and the ejection stroke of the refrigeration agent ejection that will suck in fact continuously.Specifically, suction port and ejiction opening close simultaneously during do not exist in fact, that is, in fact during whole at least one party of suction port and ejiction opening open.

Therefore, can suppress the moving generation of pressure guanidine.Thus, the problem of the generation of destabilization, vibration and the noise of the rotation of the caused fluid pressure motor of breakage, cogging of the member of formation of the refrigerating circulatory devices such as suction pipe in formation suction path is difficult for coming to the surface.In addition, " suction port and ejiction opening close simultaneously during do not exist in fact " is to be included in the concept that suction port and ejiction opening in the degree of the cogging that does not produce fluid pressure motor moment closes simultaneously.

In addition, as following, at least a portion that refrigerant circuit constitutes the refrigeration agent of driven force recovering mechanism ejection becomes gas phase.Part by refrigeration agent becomes gas phase and obtains compressibility, and the hydraulic impact take the change of the ejection flow velocity that produces because of intermittent refrigeration agent ejection as cause is relaxed.Consequently, power recovery mechanism can start smoothly, and it can reduce vibration and noise.

Below, describe the related refrigerating circulatory device of present embodiment in detail with reference to Fig. 1～7.

As shown in Figure 1, refrigerating circulatory device 101 possess and have main compressor 103, the refrigerant circuit 109 of radiator 104, power recovery mechanism 105, vaporizer 106, auxiliary compressor 102.In refrigerant circuit 109, be filled with the refrigeration agents such as carbon dioxide or hydrogen fluorohydrocarbon as working fluid.Using the high pressure side in refrigeration cycle as carbon dioxide to become in the situation of refrigeration agent of supercritical state, the present invention especially brings into play good effect.

Main compressor 103 has compressing mechanism 103a (compressor main body), the motor 108 that is connected with compressing mechanism 103a, takes in the seal container 160 of compressing mechanism 103a and motor 108.Compressing mechanism 103a is driven by motor 108.Compressing mechanism 103a will be compressed into High Temperature High Pressure at refrigerant circuit 109 interior circulating refrigerants.Can use scroll compressor, the such displacement type compressor of rotary compressor as main compressor 103.

Radiator 104 is connected with main compressor 103.Radiator 104 makes the refrigerant loses heat by main compressor 103 compressions.In other words, radiator 104 is with refrigerant cools.Refrigeration agent by radiator 104 coolings becomes middle temperature high pressure.

Power recovery mechanism 105 is connected with radiator 104.Power recovery mechanism 105 is made of the fluid pressure motor.Specifically, power recovery mechanism 105 sucks the stroke from the stroke of the refrigeration agent of radiator 104 and the refrigeration agent ejection that will suck in fact continuously.That is, power recovery mechanism 105 sucks the refrigeration agent that is varied to middle temperature high pressure in radiator 104, goes out to vaporizer 106 side sprays in the situation that its essence upper volume is changed.At this, under the effect of main compressor 103, clip power recovery mechanism 105, radiator 104 sides become than higher pressure, vaporizer 106 sides become comparison low pressure.Therefore, the refrigeration agent that is drawn in the power recovery mechanism 105 expands when 105 ejection of driven force recovering mechanism, becomes low pressure.

Vaporizer 106 is connected with power recovery mechanism 105.The refrigeration agent heating of vaporizer ultromotivity recovering mechanism in 106 future 105 also makes its evaporation.

Auxiliary compressor 102 is configured in refrigerant circuit 109 between vaporizer 106 and the main compressor 103.Auxiliary compressor 102 links with power recovery mechanism 105 by axle 12.Auxiliary compressor 102 is driven by the power that is reclaimed by power recovery mechanism 105.Auxiliary compressor 102 is made of the fluid pressure motor equally with power recovery mechanism 105.Auxiliary compressor 102 sucks the stroke of refrigeration agent of from evaporator drier 106 and the stroke that the refrigeration agent that will suck goes out to main compressor 103 side sprays in fact continuously.Auxiliary compressor 102 sucks the refrigeration agent of from evaporator drier 106 to go out to main compressor 103 side sprays in the situation that its essence upper volume is changed.Come the refrigeration agent of from evaporator drier 106 by being prepared compression from auxiliary compressor 102 ejections.The refrigeration agent that is prepared compression is further compressed and again become High Temperature High Pressure by main compressor 103.

Refrigerating circulatory device 101 also has bypass circulation 107a.Bypass circulation 107a is circuitous and the outlet of vaporizer 106 is connected with the entrance of main compressor 103 in auxiliary compressor 102.In bypass circulation 107a, be provided with bypass valve 107b.When common running, bypass valve 107b closes, to allow to obtain the pressurized effect (preparation compression effectiveness) based on auxiliary compressor 102.When refrigerating circulatory device 101 starting, bypass valve 107b is opened.If bypass valve 107b is opened, then can between the entrance of power recovery mechanism 105 and outlet, produce larger pressure difference.Consequently, start smoothly easily refrigerating circulatory device 101.

Shown in Fig. 2 A, power recovery mechanism 105 (first fluid mechanism) consists of a fluid machinery 110 with auxiliary compressor 102 (second fluid mechanism).Fluid machinery 110 has the seal container 111 that cooled machine oil is full of.Power recovery mechanism 105 is configured in this seal container 111 with auxiliary compressor 102.Thus, can realize the compactness of refrigerating circulatory device 101.

In fluid machinery 110, be provided with balancer weight 152.Specifically, be separately installed with balancer weight 152 in each end of axle 12.Balancer weight 152 is responsible for the effect of the axial weight inequality in center of reduction axle 12.One end of oil equalizing pipe 163 is connected with seal container 111.The other end of this oil equalizing pipe 163 is connected with the seal container 160 of main compressor 103.In the present embodiment, fluid machinery 110 does not have motor.

(formation of power recovery mechanism 105)

Power recovery mechanism 105 is configured in the bottom in the seal container 111.In the present embodiment, power recovery mechanism 105 is described by the example that helicoid fluid pressure motor consists of.But, be not that power recovery mechanism 105 is defined in helicoid fluid pressure motor.Power recovery mechanism 105 also can be by the decompressor with intrinsic volume ratio, and for example rotary type decompressor or scroll expansion machine consist of.

Power recovery mechanism 105 has the first obstruction component 115 and the second obstruction component 113.The first obstruction component 115 and the second obstruction component 113 are mutually opposed.Between the first obstruction component 115 and the second obstruction component 113, dispose the first clutch release slave cylinder 22.The inner space that the first clutch release slave cylinder 22 has general cylindrical shape.The inner space of this first clutch release slave cylinder 22 is by the first obstruction component 115 and the second obstruction component 113 obturations.The first obstruction component 115 and the second obstruction component 113 lay respectively at the first clutch release slave cylinder 22 about.

Axle 12 along the first clutch release slave cylinder 22 axially in the 22 interior perforations of the first clutch release slave cylinder.The first clutch release slave cylinder 22 is along a part that circumferentially centers on axle 12.Axle 12 is configured on the central shaft of the first clutch release slave cylinder 22.Axle 12 is by the second obstruction component 113 and the 3rd obstruction component described later 114 supportings.Be formed with the vertically oil supply hole 12a of through shaft 12 at axle 12.Refrigerating machine oil in the seal container 111 via this oil supply hole 12a to the supply such as between the bearing of auxiliary compressor 102 or power recovery mechanism 105, crack.In addition, axle 12 can be made of single parts, also can be made of a plurality of parts.

First piston 21 is configured in the inner space of the general cylindrical shape shape that is formed by the inner peripheral surface of the first clutch release slave cylinder 22, the first obstruction component 115 and the second obstruction component 113.First piston 21 is installed on axle 12 with the state with respect to the eccentricity of central axis of axle 12.Specifically, axle 12 possesses the eccentric part 12b with central shaft different from the central shaft of axle 12.Embed the first piston 21 of tubular at this eccentric part 12b.Therefore, first piston 21 is with respect to the eccentricity of central axis of the first clutch release slave cylinder 22.Thus, first piston 21 is followed the rotation of axle 12 and eccentric rotary.

In the first clutch release slave cylinder 22, be formed with the first working room 23 (also with reference to Fig. 4) by the outer circumferential face of first piston 21, inner peripheral surface, the first obstruction component 115 and second obstruction component 113 of the first clutch release slave cylinder 22.Even first piston 21 rotates jointly with axle 12, the volume of the first working room 23 is in fact also constant.

As shown in Figure 4, be formed with to the groove 22a of the lines of the first working room 23 openings at the first clutch release slave cylinder 22.The first tabular partition member 24 is inserted among this lines groove 22a sliding freely.Between the bottom of the first partition member 24 and lines groove 22a, dispose force application mechanism 25.Under the effect of this force application mechanism 25, the first partition member 24 is pressed towards the outer circumferential face of first piston 21.Thus, the first working room 23 is divided into two spaces.Specifically, the first working room 23 is divided into the 23b of ejection working room of the on high-tension side suction 23a of working room and low voltage side.

In addition, force application mechanism 25 for example can be made of spring.Specifically, force application mechanism 25 can be compression helical spring.

In addition, force application mechanism 25 also can be so-called air spring etc.Namely, after the first partition member 24 slides to the direction of the volume-diminished of the backside space that makes the first partition member 24, the pressure of pressure ratio the first working room 23 in its backside space is high, and the first partition member 24 is pressed also passable towards first piston 21 under the effect of this pressure difference.The backside space that for example also can make the first partition member 24 is confined space, when the volume in space reduces because of retreating of the first partition member 24 overleaf the first partition member 24 is applied reaction force.Certainly, also can consist of by the spring of a plurality of kinds such as compression helical spring, air spring force application mechanism 25.In addition, the pressure of the first working room 23 is made as the middle pressure of the pressure that sucks the 23a of working room and the pressure that sprays the 23b of working room.Backside space refers to the space that forms between the bottom of the rear end of the first partition member 24 and lines groove 22a.

Shown in Fig. 2 A, be provided with the rotation of following first piston 21 and open and close so that refrigeration agent flow into to suck the first suction port 26 of the 23a of working room at the first obstruction component 115.Similarly, on the second obstruction component 113, axle 12 axially on the position relative with the first suction port 26 be provided with the rotation of following first piston 21 and open and close so that refrigeration agent flows into the second suction port 27 that sucks the 23a of working room.That is, power recovery mechanism 105 has two suction ports 26 and 27.Stop even first piston 21 and

suction port

26 and 27 are overlapping, when starting next time, also have positive pressure upper surface and this two side of lower surface of first piston 21.Thus, can avoid first piston 21 to be pressed by advantage towards

obstruction component

115 or 113, thereby refrigerating circulatory device 101 can start smoothly.In addition, too, the pressure-acting of refrigeration agent is upper surface and this two side of lower surface of first piston 21 when usually turning round.Therefore, the slippage loss between first piston 21 and

obstruction component

115 or 113 reduces, the improved efficiency of power recovery mechanism 105.

Specifically, power recovery mechanism 105 comprise for refrigeration agent from the outside (radiator 104) of this power recovery mechanism 105 respectively via the first suction port 26 and the second suction port 27 and to the suction path 53 that sucks the 23a of working room and supply with.This suction path 53 sucks path 51 by general suction path 40, first and the second suction path 52 consists of.The first suction port 26 is positioned at the terminal in the first suction path 51, and the second suction port 27 is positioned at the terminal in the second suction path 52.In addition, power recovery mechanism 105 has refrigeration agent from the outside of seal container 111 to the suction pipe 28 that sucks path 53 guiding.

General suction path 40 is formed at the second obstruction component 113, is the thick path of extending towards the center of axle 12 from the outer circumferential face of the second obstruction component 113.Suction pipe 28 directly is connected with this general suction path 40.First sucks path 51 from general suction path 40 branches and runs through vertically the first clutch release slave cylinder 22 to first suction ports 26, refrigeration agent can be supplied with to sucking the 23a of working room from general suction path 40 via the first suction port 26.Second sucks path 52 upwards sucks position in the inner part, path 51 from general suction path 40 branches and extends to vertically the second suction port 27 than first in the footpath of axle 12, refrigeration agent can be supplied with to sucking the 23a of working room from general suction path 40 via the second suction port 27.According to such structure, need not to increase the radical of suction pipe 28, two

suction ports

26 and 27 can be set.

In detail, first suck that path 51 is included in part that the second obstruction component 113 forms, the part that forms at the first clutch release slave cylinder 22 and the part that forms at the first obstruction component 115.In the axial direction, first suck path 51 from the working room 23 downside around entering upside.That is, first suck the cross section profile that path 51 is hook-type.

In addition, suck the length in path 51 and the equal in length in the second suction path 52 in order to make first, also consider in the first clutch release slave cylinder 22, to arrange the structure in general suction path 40.Yet, in the little situation of the volume of working room 23, because to compare wall thickness thinner with the first clutch release slave cylinder 22, therefore general suction path 40 can't be arranged in the first clutch release slave cylinder 22.Under these circumstances, the structure of present embodiment is effective.This is also applicable for ejection described later path.

Next, shown in Fig. 2 B, be provided with the rotation of following first piston 21 and open and close so that the first ejiction opening 29 (first-class outlet) that refrigeration agent flows out from the ejection 23b of working room at the first obstruction component 115.Similarly, on the second obstruction component 113, relative with the first ejiction opening 29 in the axial direction position is provided with the rotation of following first piston 21 and opens and closes so that the second ejiction opening 30 (second outlet) that refrigeration agent flows out from the ejection 23b of working room.That is, power recovery mechanism 105 has two ejiction openings 29 and 30.Stop even first piston 21 and

ejiction opening

29 and 30 are overlapping, when starting next time, also have suction function upper surface and this two side of lower surface of first piston 21.Thus, can avoid first piston 21 towards

obstruction component

115 or 113 by surging drawing, therefore easily refrigerating circulatory device 101 is successfully started.In addition, even when usually turning round, the pressure of refrigeration agent also can act on upper surface and this two side of lower surface of first piston 21.Therefore, the slippage loss between first piston 21 and

obstruction component

115 or 113 reduces, the improved efficiency of power recovery mechanism 105.

Specifically, power recovery mechanism 105 comprise for refrigeration agent from the ejection 23b of working room respectively via the first ejiction opening 29 and the second ejiction opening 30 ejection path 58 to outside (vaporizer 106) guiding of this power recovery mechanism 105.This ejection path 58 is made of general spraying outbound path 55, the first ejection path 56 and the second ejection path 57.The first ejiction opening 29 is positioned at the top in the first ejection path 56, and the second ejiction opening 30 is positioned at the top in the second ejection path 57.In addition, power recovery mechanism 105 has the spraying pipe 31 of refrigeration agent from ejection path 58 to the exterior guiding of seal container 111.When refrigerating circulatory device 101 starting, if being opened, bypass valve 107b makes main compressor 103 actions, then in ejection path 58 interior generation negative pressure.

General spraying outbound path 55 is formed at the second obstruction component 113, is the thick path of extending towards the center of axle 12 from the outer circumferential face of the second obstruction component 113.Spraying pipe 31 directly is connected with this general spraying outbound path 55.The first ejection path 56 from the first ejiction opening 29 stretch out and run through vertically the first clutch release slave cylinder 22 and with general spraying outbound path 55 interflow, thereby with refrigeration agent from the ejection 23b of working room via the first ejiction opening 29 to 55 guiding of general spraying outbound path.The second ejection path 57 is extended vertically and is upwards collaborated with general spraying outbound path 55 than position in the inner part, the first ejection path 56 in the footpath of axle 12 from the second ejiction opening 30, thereby refrigeration agent is guided to general spraying outbound path 55 via the second ejiction opening 30 from spraying the 23b of working room.According to such structure, need not to increase the radical of spraying pipe 31, two

ejiction openings

29 and 30 can be set.

In detail, the first ejection path 56 is included in part that the first obstruction component 115 forms, the part that forms at the first clutch release slave cylinder 22 and the part that forms at the second obstruction component 113, and from the working room 23 upside around entering downside.That is, the first ejection path 56 is the cross section profile of hook-type.

As shown in Figure 4, in the zone adjacent with the first partition member 24, suck path 53 towards sucking the 23a of working room opening.In detail, first suck path 51 and second and suck path 52 respectively towards sucking working room 23a opening with reference to what Fig. 2 A had illustrated.

The second suction port 27 forms from the part adjacent with the first partition member 24 that suck the 23a of working room and is the roughly fan-shaped of extending to sucking the direction that the 23a of working room broadens circular-arcly.The second suction port 27 is only entirely shut by first piston 21 when first piston 21 is positioned at upper dead center.And during whole the moment that is positioned at upper dead center except first piston 21, at least a portion of the second suction port 27 is exposed to sucking the 23a of working room.Specifically, overlook under the observation, the outboard end limit 27a of the second suction port 27 forms circular-arc along the outer circumferential face of the first piston 21 that is positioned at upper dead center.In other words, outboard end limit 27a forms roughly the same circular-arc of the outer circumferential face of radius and first piston 21.In addition, " outboard end limit " refers to be positioned at the end limit in the outside radially of axle 5." upper dead center " refers to that blade at utmost is pressed into the position of the piston under the state of depths in the blade groove.

Although not shown among Fig. 4, the first suction port 26 has the opening shape identical with the opening shape of the second suction port 27.In addition, the first suction port 26 has the opening area that equates with the opening area of the second suction port 27.According to such structure, the power of the upper surface by acting on first piston 21 can offset with the power that acts on lower surface effectively.

Flow into the pressure of the refrigeration agent that sucks the 23a of working room and the pressure that flows into the refrigeration agent that sucks the 23a of working room from the second suction port 27 from the first suction port 26 about equally.Therefore, in the first suction port 26 and situation that the second suction port 27 overlaps in the axial direction fully, the overlapping area of the area that first piston 21 and the first suction port 26 are overlapping and first piston 21 and the second suction port 27 equates.Therefore, the power that acts on the upper surface of first piston 21 equates (power=pressure * area) with the power that acts on lower surface.That is the effect that, the power of the thickness direction (axially) that acts on first piston 21 is offseted is the highest.

In addition, owing to the first suction path 51 to the second sucks paths 52 length, therefore in the equal situation of both sectional areas, the pressure loss in the first suction path 51 is greater than second pressure loss that sucks in the path 52.Therefore, strictly speaking, under the impact of the size of the pressure loss, even the first suction port 26 overlaps in the axial direction fully with the second suction port 27, the power that acts on the upper surface of first piston 21 can not equate with the power that acts on lower surface yet.

As shown in Figure 3, in the present embodiment, the first suction path 51 has the sectional area greater than the sectional area in the second suction path 52.According to this structure, can suppress first pressure loss that sucks in the path 51, therefore have the more approaching effect that equates of the power that makes the upper surface that acts on first piston 21 and the power that acts on lower surface.Consequently, can improve the effect of the power of negative function on the thickness direction of first piston 21.

The not special limitation of shape that each sucks the cross section in path respectively sucks the cross section that the path has circle but be typically.Suck the shallow spot-facing that path 51 and second sucks the end in path 52 by being located at first, form the first suction port 26 and the second suction port 27 with shape shown in Figure 4.Such structure also can adopt for ejection path, ejiction opening, in addition, also can adopt for auxiliary compressor 102.

As shown in Figure 4, in the zone adjacent with the first partition member 24, ejection path 58 is towards the ejection 23b of working room opening.In detail, the first ejection path 56 that has illustrated with reference to Fig. 2 B and the second ejection path 57 are respectively towards ejection working room 23b opening.

The second ejiction opening 30 forms from the part adjacent with the first partition member 24 of the ejection 23b of working room and is the roughly fan-shaped of extending to the direction that the ejection 23b of working room broadens circular-arcly.The second ejiction opening 30 is only entirely shut by first piston 21 when first piston 21 is positioned at upper dead center.And during whole the moment that is positioned at upper dead center except first piston 21, at least a portion of the second ejiction opening 30 is exposed to the ejection 23b of working room.Specifically, overlook under the observation, the outboard end limit 30a of the second ejiction opening 30 forms circular-arc along the outer circumferential face of the first piston 21 that is positioned at upper dead center.In other words, outboard end limit 30a forms roughly the same circular-arc of the outer circumferential face of radius and first piston 21.

Although not shown in Fig. 4, the first ejiction opening 29 has the opening shape identical with the opening shape of the second ejiction opening 30.In addition, the first ejiction opening 29 has the opening area that equates with the opening area of the second ejiction opening 30.According to such structure, the power (attraction force) of upper surface that can be by acting on first piston 21 offsets with the power that acts on lower surface (attraction force) effectively.

The pressure of the pressure of the refrigeration agent from the first ejiction opening 29 to 58 ejections of ejection path and the refrigeration agent from the second ejiction opening 30 to 58 ejections of ejection path about equally.Therefore, in the first ejiction opening 29 and situation that the second ejiction opening 30 overlaps in the axial direction fully, first piston 21 equates with the area of overlap of the second ejiction opening 30 with area of overlap and the first piston 21 of the first ejiction opening 29.Therefore, the power that acts on the upper surface of first piston 21 equates (power=pressure * area) with the power that acts on lower surface.That is the effect that, the power on the thickness direction (axially) that acts on first piston 21 is offseted is the highest.

First suck path 51 and second and suck path 52 similarly with reference Fig. 3 has illustrated, the first ejection path 56 also can have the sectional area greater than the sectional area in the second ejection path 57.According to this structure, can suppress the pressure loss in the first ejection path 56, therefore have the more approaching effect that equates of the power that makes the upper surface that acts on first piston 21 and the power that acts on lower surface.

In addition, make effect that the power that acts on first piston 21 offsets in the situation that is provided with a plurality of

suction ports

26 and 27 and be provided with in the situation of a plurality of

ejiction openings

29 and 30 and can independently obtaining.Yet, suck the pressure of the refrigeration agent in the path 53 far above the pressure of the refrigeration agent in the ejection path 58.For example, using as refrigeration agent in the situation of carbon dioxide, what suck pressure in pressure and the ejection path 58 in the path 53 differs from even reaches several MPa.If the consideration this point is then high than the resulting effect of the combination of passing through

ejiction opening

29 and 30 by the resulting effect of the combination of

suction port

26 and 27.

Fig. 5 is the schematic diagram of movements of power recovery mechanism 105, and the figure of this one of four states of ST1～ST4 is shown.

In first piston 21 rotation, when

suction port

26 and 27 is opened, (shown in the ST2～ST4), from the refrigeration agent of

suction port

26 and 27 high pressure that flow into the volume that sucks the 23a of working room is increased gradually such as Fig. 5.Follow the volume of the 23a of this suction working room to amplify, the rotating torques that puts on first piston 21 becomes the part of the rotary driving force of axle 12.In the overlapping in the axial direction situation of the first suction port 26 and the second suction port 27, two

suction

26 and 27 switching are constantly also consistent.Similarly, in the overlapping in the axial direction situation of the first ejiction opening 29 and the second ejiction opening 30, two

ejiction openings

29 and 30 switching are constantly also consistent.

When driven force recovering mechanism 105 was observed, vaporizer 106 sides and radiator 104 sides were in a ratio of low pressure.The refrigeration agent of the cryogenic high pressure in the ejection 23b of working room is attracted to vaporizer 106 sides, from the ejection 23b of working room to 58 ejections of ejection path.Be communicated with ejection path 58 at the ejection 23b of working room, when the ejection stroke began, the specific volume of refrigeration agent increased severely.By the ejection stroke of this refrigeration agent, the rotating torques that puts on first piston 21 also becomes the part of the rotary driving force of axle 12.That is, axle 12 is owing to the refrigeration agent of high pressure rotates to the attraction that sucks the refrigeration agent in the 23a of working room inflow and the ejection stroke.And the rotating torques of this axle 12 is utilized as the power of auxiliary compressor 102 as the back is described in detail.

Sucking the 23a of working room is communicated with suction path 53 all the time.In addition, the ejection 23b of working room is communicated with ejection path 58 all the time.In other words, in power recovery mechanism 105, suck in fact continuously the stroke of refrigeration agent and the stroke of the refrigeration agent that will suck ejection.Therefore, the refrigeration agent of suction substantially volume do not have in the vicissitudinous situation by power recovery mechanism 105.

Shown in the picture left above (ST1) of Fig. 5, suction port 27 and ejiction opening 30 these two sides only close fully in the moment that first piston 21 is positioned at upper dead center.That is, suction port 27 and ejiction opening 30 these two sides become moment of one and close fully in the first working room 23.In more detail, before sucking the 23a of working room and moment that ejection path 58 is communicated with, the suction 23a of working room is communicated with suction path 53.Then, sucking that the 23a of working room is communicated with ejection path 58 after sucking the 23a of working room and becoming the moment of the ejection 23b of working room, make by first piston 21 to spray the 23b of working room and isolate from suction path 53.Therefore, can suppress refrigeration agent passes to ejection path 58 from sucking path 53.Thus, can realize high efficiency power recovery.

From the viewpoint consideration that the total ban refrigeration agent passes to ejection path 58 from sucking path 53, preferably be positioned at the moment of upper dead center at first piston 21, suction port 27 is closed with ejiction opening 30 these two sides.But, even be positioned at the moment of upper dead center at first piston 21, in the situation that only side in suction port 27 and the ejiction opening 30 closes, if the difference in the moment that the moment that suction port 27 is closed and ejiction opening 30 are closed, is then passed with spraying not produce in fact between the path 58 sucking path 53 less than about 10 ° as the angle of rotation of axle 12.That is, the difference in the moment of closing by the moment and ejiction opening 30 that suction port 27 is closed is set as angle of rotation as axle 12 less than about 10 °, can suppress refrigeration agent and pass to ejection path 58 from sucking path 53.

Consider that from the viewpoint of passing that prevents refrigeration agent preferred

suction port

26 and 27 switching are constantly consistent, and the switching of

ejiction opening

29 and 30 is constantly also consistent.

(formation of auxiliary compressor 102)

Shown in Fig. 2 A, auxiliary compressor 102 is configured to the 105 top sides than power recovery mechanism in seal container 111.By being configured to than the auxiliary compressor 102 of higher temperatures like this 105 top sides of power recovery mechanism of lower temperature frequently, can suppress the heat exchange between auxiliary compressor 102 and the power recovery mechanism 105.But, also auxiliary compressor 102 can be configured to than power recovery mechanism 105 on the lower.

Auxiliary compressor 102 links with power recovery mechanism 105 via axle 12.In the present embodiment, auxiliary compressor 102 is described by the example that helicoid fluid pressure motor consists of.But, be not that auxiliary compressor 102 is defined as helicoid fluid pressure motor.Auxiliary compressor 102 also can be by the compressor with intrinsic volume ratio, and for example rotary compressor or scroll compressor consist of.

The basic structure of auxiliary compressor 102 and above-mentioned power recovery mechanism 105 are roughly the same.Specifically, shown in Fig. 2 A, auxiliary compressor 102 has as the first obstruction component 115 of lower obstruction component with as the 3rd obstruction component 114 of upper obstruction component.Power recovery mechanism 105 is adjacent to be configured in the seal container 111 with auxiliary compressor 102 vertically, so that the first obstruction component 115 of power recovery mechanism 105 is shared as the lower obstruction component of auxiliary compressor 102.According to such structure, can reduce number of components, and the compactness of convection cell machinery 110 is favourable.

The first obstruction component 115 and the 3rd obstruction component 114 are mutually opposed.Specifically, the 3rd obstruction component 114 and the first obstruction component 115 and opposition side 113 opposed of the second obstruction components in the face of putting.Between the first obstruction component 115 and the 3rd obstruction component 114, dispose the second clutch release slave cylinder 42.The inner space that the second clutch release slave cylinder 42 has general cylindrical shape.The inner space of this second clutch release slave cylinder 42 is by the first obstruction component 115 and the 3rd obstruction component 114 obturations.The 3rd obstruction component 114 and the first obstruction component 115 lay respectively at the second clutch release slave cylinder 42 about.

Axle 12 along the second clutch release slave cylinder 42 axially in the 42 interior perforations of the second clutch release slave cylinder.The second clutch release slave cylinder 42 is along a part that circumferentially centers on axle 12.Axle 12 is configured on the central shaft of the second clutch release slave cylinder 42.The second piston 41 is configured in the inner space of the general cylindrical shape shape that is formed by the inner peripheral surface of the second clutch release slave cylinder 42, the first obstruction component 115 and the 3rd obstruction component 114.The second piston 41 is installed on axle 12 with the state with respect to the eccentricity of central axis of axle 12.Specifically, axle 12 possesses the eccentric part 12c with central shaft different from the central shaft of axle 12.Embed the second piston 41 that tubular is arranged at this eccentric part 12c.Therefore, the second piston 41 is with respect to the eccentricity of central axis of the second clutch release slave cylinder 42.Thus, the second piston 41 is followed the rotation of axle 12 and eccentric rotary.

In addition, eccentric part 12c is to the direction off-centre roughly the same with eccentric part 12b.Therefore, in the present embodiment, first piston 21 is roughly the same each other with respect to the eccentric direction of the central shaft of the second clutch release slave cylinder 42 with respect to eccentric direction and second piston 41 of the central shaft of the first clutch release slave cylinder 22.The meaning of " roughly the same " is for not only comprising identical situation, also comprises the situation of the error about existence ± 2～3 °.

In the second clutch release slave cylinder 42, be formed with the second working room 43 (also with reference to Fig. 6) by the outer circumferential face of the second piston 41, inner peripheral surface, the first obstruction component 115 and the 3rd obstruction component 114 of the second clutch release slave cylinder 42.Even the second piston 41 rotates jointly with axle 12, the volume of the second working room 43 is in fact also constant.

As shown in Figure 6, be formed with to the groove 42a of the lines of the second working room 43 openings at the second clutch release slave cylinder 42.The second tabular partition member 44 inserts among this lines groove 42a sliding freely.Between the bottom of the second partition member 44 and lines groove 42a, dispose force application mechanism 45.Under the effect of this force application mechanism 45, the second partition member 44 is pressed towards the outer circumferential face of the second piston 41.Thus, the second working room 43 is divided into two spaces.Specifically, the second working room 43 is divided into the 43a of suction working room and the on high-tension side ejection 43b of working room of low voltage side.

In addition, force application mechanism 45 can be made of for example spring.Specifically, force application mechanism 45 is same with above-mentioned force application mechanism 25, can be compression helical spring, also can be so-called air spring.

Shown in Fig. 2 B, be provided with the rotation of following the second piston 41 and open and close so that the first ejiction opening 49 (lower ejiction opening) that refrigeration agent flows out from the ejection 43b of working room at the first obstruction component 115.Similarly, on the 3rd obstruction component 114, relative with the first ejiction opening 49 in the axial direction position is provided with the rotation of following the second piston 41 and opens and closes so that the second ejiction opening 50 that refrigeration agent flows out from the ejection 43b of working room (upper ejiction opening).That is, auxiliary compressor 102 has two ejiction openings 49 and 50.Even the second piston 41 stops overlappingly with

ejiction opening

49 and 50, when starting next time, also have suction function in upper surface and this two side of lower surface of the second piston 41.Thus, can avoid the second piston 41 towards

obstruction component

115 or 114 by surging drawing, refrigerating circulatory device 101 is successfully started.In addition, even when usually turning round, the pressure of refrigeration agent also can act on upper surface and this two side of lower surface of the second piston 41.Therefore, the slippage loss between the second piston 41 and

obstruction component

115 or 114 reduces, the improved efficiency of auxiliary compressor 102.

Specifically, auxiliary compressor 102 comprise for refrigeration agent from the ejection 43b of working room respectively via the first ejiction opening 49 and the second ejiction opening 50 and to the ejection path 68 of outside (main compressor 103) guiding of this auxiliary compressor 102.This ejection path 68 is made of general spraying outbound path 65, the first ejection path 66 and the second ejection path 67.The first ejiction opening 49 is positioned at the top in the first ejection path 66, and the second ejiction opening 50 is positioned at the top in the second ejection path 67.In addition, auxiliary compressor 102 has the spraying pipe 151 of refrigeration agent from ejection path 68 to the exterior guiding of seal container 111.When refrigerating circulatory device 101 starting, bypass valve 107b is opened and make main compressor 103 actions, in ejection path 68 interior generation negative pressure.

General spraying outbound path 65 is formed at the 3rd obstruction component 114, is the thick path of extending towards the center of axle 12 from the outer circumferential face of the 3rd obstruction component 114.Spraying pipe 151 directly is connected with this general spraying outbound path 65.The first ejection path 66 from the first ejiction opening 49 stretch out and run through vertically the second clutch release slave cylinder 42 and with general spraying outbound path 65 interflow, thereby with refrigeration agent from the ejection 43b of working room via the first ejiction opening 49 to 65 guiding of general spraying outbound path.The second ejection path 67 is extended vertically and is upwards collaborated with general spraying outbound path 65 than position in the inner part, the first ejection path 66 in the footpath of axle 12 from the second ejiction opening 50, thereby refrigeration agent is guided to general spraying outbound path 65 via the second ejiction opening 50 from spraying the 43b of working room.According to such structure, need not to increase the radical of spraying pipe 151, two

ejiction openings

49 and 50 can be set.

In detail, the part that the first ejection path 66 is included in part that the first obstruction component 115 forms, form at the second clutch release slave cylinder 42, the part that forms at the 3rd obstruction component 114, and from the working room 43 downside to upside around entering.That is, the first ejection path 66 is the cross section profile of hook-type.

Next, shown in Fig. 2 A, be provided with the rotation of following the second piston 41 and open and close so that refrigeration agent flow into to suck the first suction port 46 (lower suction port) of the 43a of working room at the first obstruction component 115.Similarly, on the 3rd obstruction component 114, axle 12 axially on the position relative with the first suction port 46 be provided with the rotation of following the second piston 41 and open and close so that refrigeration agent flows into the second suction port 47 (upper suction port) that sucks the 43a of working room.That is, auxiliary compressor 102 has two suction ports 46 and 47.Even the second piston 41 stops overlappingly with

suction port

46 and 47, when starting next time, also have suction function in upper surface and this two side of lower surface of the second piston 41.Thus, can avoid the second piston 41 towards

obstruction component

115 or 114 by surging drawing, therefore refrigerating circulatory device 101 is successfully started.In addition, even when usually turning round, the pressure of refrigeration agent also can act on upper surface and this two side of lower surface of the second piston 41.Therefore, the slippage loss between the second piston 41 and

obstruction component

115 or 114 reduces, the improved efficiency of auxiliary compressor 102.

Specifically, auxiliary compressor 102 comprise for refrigeration agent from the outside (vaporizer 106) of this auxiliary compressor 102 respectively via the first suction port 46 and the second suction port 47 and to the suction path 63 that sucks the 43a of working room and supply with.This suction path 63 sucks path 61 by general suction path 60, first and the second suction path 62 consists of.The first suction port 46 is positioned at the terminal in the first suction path 61, and the second suction port 47 is positioned at the terminal in the second suction path 62.In addition, auxiliary compressor 102 has refrigeration agent from the outside of seal container 111 to the suction pipe 48 that sucks path 63 guiding.When refrigerating circulatory device 101 starting, if being opened, bypass valve 107b makes main compressor 103 actions, then in sucking path 63, also produce negative pressure.That is, under the state that bypass valve 107b is opened, pressure and the ejection path 68 interior pressure that suck in the path 63 equate.

General suction path 60 is formed at the 3rd obstruction component 114, is the thick path of extending towards the center of axle 12 from the outer circumferential face of the 3rd obstruction component 114.Suction pipe 48 directly is connected with this general suction path 60.First sucks path 61 from general suction path 60 branches and runs through vertically the second clutch release slave cylinder 42 to first suction ports 46, thereby refrigeration agent can be supplied with to sucking the 43a of working room from general suction path 60 via the first suction port 46.Second sucks path 62 upwards sucks position in the inner part, path 61 from general suction path 60 branches and extends to vertically the second suction port 47 than first in the footpath of axle 12, thereby refrigeration agent can be supplied with to sucking the 43a of working room from general suction path 60 via the second suction port 47.According to such structure, need not to increase the radical of suction pipe 48, two

suction ports

46 and 47 can be set.

In detail, first suck that path 61 is included in part that the 3rd obstruction component 114 forms, the part that forms at the second clutch release slave cylinder 42 and the part that forms at the first obstruction component 115.In the axial direction, first suck path 61 from the working room 43 upside around entering downside.That is, first suck the cross section profile that path 61 is hook-type.

As shown in Figure 6, in the zone adjacent with the second partition member 44, suck path 63 towards sucking the 43a of working room opening.In detail, first suck path 61 and second and suck path 62 respectively towards sucking working room 43a opening with reference to what Fig. 2 A had illustrated.

The first suction port 46 forms from the part adjacent with the second partition member 44 that suck the 43a of working room and is the roughly fan-shaped of extending to sucking the direction that the 43a of working room broadens circular-arcly.The first suction port 46 is only entirely shut by the second piston 41 when the second piston 41 is positioned at upper dead center.And during whole the moment that is positioned at upper dead center except the second piston 41, at least a portion of the first suction port 46 is to sucking the 43a of working room.Specifically, overlook under the observation, the outboard end limit 46a of the first suction port 46 forms circular-arc along the outer circumferential face of the second piston 41 that is positioned at upper dead center.In other words, outboard end limit 46a forms roughly the same circular-arc of the outer circumferential face of radius and the second piston 41.

Although not shown in Fig. 6, the second suction port 47 has the opening shape identical with the opening shape of the first suction port 46.In addition, the first suction port 46 has the opening area that equates with the opening area of the second suction port 47.According to such structure, the power of upper surface that can be by acting on the second piston 41 offsets with the power that acts on lower surface effectively.

Flow into the pressure of the refrigeration agent that sucks the 43a of working room and the pressure that flows into the refrigeration agent that sucks the 43a of working room from the second suction port 47 from the first suction port 46 about equally.Therefore, in the first suction port 46 and situation that the second suction port 47 overlaps in the axial direction fully, the second piston 41 equates with the area of overlap of the second suction port 47 with area of overlap and second piston 41 of the first suction port 46.Therefore, the power that acts on the upper surface of the second piston 41 equates (power=pressure * area) with the power that acts on lower surface.That is the effect that, the power of the thickness direction (axially) that acts on the second piston 41 is offseted is the highest.

As shown in Figure 6, with the second partition member 44 adjacent areas in, ejection path 68 is towards the ejection 43b of working room opening.In detail, the first ejection path 66 that has illustrated with reference to Fig. 2 B and the second ejection path 67 are respectively towards ejection working room 43b opening.

The first ejiction opening 49 forms from the part adjacent with the second partition member 44 of the ejection 43b of working room and is the roughly fan-shaped of extending to the direction that the ejection 43b of working room broadens circular-arcly.The first ejiction opening 49 is only entirely shut by the second piston 41 when the second piston 41 is positioned at upper dead center.And during whole the moment that is positioned at upper dead center except the second piston 41, at least a portion of the first ejiction opening 49 is exposed to the ejection 43b of working room.Specifically, overlook under the observation, the outboard end limit 49a of the first ejiction opening 49 forms circular-arc along the outer circumferential face of the second piston 41 that is positioned at upper dead center.In other words, outboard end limit 49a forms roughly the same circular-arc of the outer circumferential face of radius and the second piston 41.

Although not shown in Fig. 6, the second ejiction opening 50 has the opening shape identical with the opening shape of the first ejiction opening 49.That is, the first ejiction opening 49 has the opening area that equates with the opening area of the second ejiction opening 50.According to such structure, the power of upper surface that can be by acting on the second piston 41 offsets with the power that acts on lower surface effectively.

The pressure of the pressure of the refrigeration agent from the first ejiction opening 49 to 68 ejections of ejection path and the refrigeration agent from the second ejiction opening 50 to 68 ejections of ejection path about equally.Therefore, in the first ejiction opening 49 and situation that the second ejiction opening 50 overlaps in the axial direction fully, the second piston 41 equates with the area of overlap of the second ejiction opening 50 with area of overlap and second piston 41 of the first ejiction opening 49.Therefore, the power that acts on the upper surface of the second piston 41 equates (power=pressure * area) with the power that acts on lower surface.That is the effect that, the power of the thickness direction (axially) that acts on the second piston 41 is offseted is the highest.

As shown in Figure 6, ejection path 68 is connected with backside space 155 via communication path 156.Specifically, in the present embodiment, this communication path 156 the central shaft of the second partition member 44 and axle 12 near the time be communicated with backside space 155.Communication path 156 forms when the second partition member 44 leaves a certain degree from the central shaft of axle 12 by the second partition member 44 obturations.Namely, the second partition member 44 from going-back position after the immediate progressive position of the central shaft of axle 12 at utmost separates to the central shaft from axle 12 slide during, communication path 156 is from opening state to closing change of state, and backside space 155 changes to the confined space that is cut off from communication path 156 from the open space that is communicated with communication path 156.Therefore, make communication path 156 obturations by the second partition member 44, after backside space 155 became confined space, backside space 155 was pressed towards the second piston 41 the second partition member 44 as air spring.

The suction path 51 of the power recovery mechanism 105 that has illustrated with reference to Fig. 3 in addition, and 52 structure also can adopt in auxiliary compressor 102.That is, in auxiliary compressor 102, the first suction path 61 also can have the sectional area greater than the sectional area in the second suction path 62.In addition, the first ejection path 66 also can have the sectional area greater than the sectional area in the second ejection path 67.According to such structure, owing to can suppress first pressure loss that sucks in path 61, the first ejection path 66, therefore has the more approaching effect that equates of the power that makes the upper surface that acts on the second piston 41 and the power that acts on lower surface.

Make effect that the power that acts on the second piston 41 offsets in the situation that is provided with a plurality of

suction ports

46 and 47 and be provided with in the situation of a plurality of

ejiction openings

49 and 50 and can obtaining independently.Yet the effect that the combination by

ejiction opening

49 and 50 obtains is higher than the effect that the combination by

suction port

46 and 47 obtains.It is the reasons are as follows.At first, when refrigerating circulatory device 101 starting, the pressure that sucks in path 63 and the ejection path 68 temporarily equates.Bypass valve 107b opened (with reference to Fig. 1) when its reason was to start.On the other hand, because bypass valve 107b closes after refrigerating circulatory device 101 startings, the pressure that therefore sprays in the path 68 is higher than the pressure that sucks in the path 63.Thus, the combination by

ejiction opening

49 and 50 can more effectively reduce the usually slippage loss during running of refrigerating circulatory device 101.

Next, describe the operating principle of auxiliary compressor 102 in detail with reference to Fig. 7.The figure of this one of four states of T1～T4 shown in Fig. 7.The operating principle of the operating principle of auxiliary compressor 102 and power recovery mechanism 105 is roughly the same.

The dynamic rotation of axle 12 by being reclaimed by power recovery mechanism 105.Follow the rotation of axle 12, the second piston 41 also rotates, and auxiliary compressor 102 is driven.In the overlapping in the axial direction situation of the first suction port 46 and the second suction port 47, two

suction

46 and 47 switching are constantly also consistent.Similarly, in the overlapping in the axial direction situation of the first ejiction opening 49 and the second ejiction opening 50, two

ejiction openings

49 and 50 switching are constantly also consistent.

The in fact constancy of volume of the second working room 43.Sucking the 43a of working room is communicated with all the time with suction path 63.The ejection 43b of working room is communicated with all the time with ejection path 68.Therefore, in the second working room 43 of auxiliary compressor 102, refrigeration agent neither compresses also and does not expand.Rotate by power recovery mechanism 105 at axle 12, when auxiliary compressor 102 is driven, compare with the upstream side of the second working room 43, this side of the downstream side of the second working room 43 becomes high pressure.In other words, under the effect of the driven auxiliary compressor 102 of power that is reclaimed by power recovery mechanism 105, compare with

ejiction opening

49 and 50, the pressure of main compressor 103 sides uprises, and compares with

suction port

46 and 47, and the pressure of vaporizer 106 sides uprises.That is, boost by auxiliary compressor 102.

Sucking the 43a of working room is communicated with suction path 63 all the time.In addition, the ejection 43b of working room is communicated with ejection path 68 all the time.In other words, in auxiliary compressor 102, suck in fact continuously the stroke of refrigeration agent and the stroke of the refrigeration agent that will suck ejection.Therefore, the refrigeration agent that is inhaled into substantially under the state of constancy of volume by auxiliary compressor 102.

In addition, in the present embodiment, it is roughly consistent with the moment that the second piston 41 is positioned at upper dead center that first piston 21 is positioned at moment of upper dead center.

Shown in the picture left above (T1) of Fig. 7, suction port 46 and ejiction opening 49 these two sides only close fully in the moment that the second piston 41 is positioned at upper dead center.That is, suction port 46 and ejiction opening 49 these two sides become moment of one and close fully in the second working room 43.In more detail, before sucking the 43a of working room and moment that ejiction opening 49 is communicated with, the suction 43a of working room is communicated with suction path 63.Then, is communicated with ejection path 68 and after sucking the 43a of working room and becoming the moment of the ejection 43b of working room, sprays the 43b of working room and isolated from suction path 63 by the second piston 41 sucking the 43a of working room.Therefore, can suppress the adverse current of refrigeration agent from the higher ejection path 68 of pressure ratio to the lower suction path 63 of pressure ratio.Thus, can realize high efficiency supercharging.Consequently, the utilization ratio of the power of recovery improves.

In addition, consider from limiting the viewpoint of refrigeration agent from ejection path 68 to the adverse current that sucks path 63 fully, preferably be positioned at the moment of upper dead center at the second piston 41, suck path 63 and close with ejection path 68 these two sides.But, even in moment that the second piston 41 is arranged in upper dead center situation that only a side of suction port 46 and ejiction opening 49 closes, as long as the difference in the moment that suction port 46 moment of closing and ejiction opening 49 are closed less than about 10 °, does not then produce in fact refrigeration agent from ejection path 68 to the adverse current that sucks path 63 as the angle of rotation of axle 12.That is, the difference in the moment of closing by the moment and ejiction opening 49 that suction port 46 is closed is set as angle of rotation as axle 12 less than about 10 °, can suppress refrigeration agent from ejection path 68 to the adverse current that sucks path 63.

From preventing that the viewpoint that refrigeration agent passes from considering,

preferred suction port

46 and 47 switching are constantly consistent, and the switching of

ejiction opening

49 and 50 is constantly also consistent.

Industrial utilizability

The present invention is useful in the refrigerating circulatory device of water supplying machine, refrigeration and heating air-conditioning etc.

Claims

1. refrigerating circulatory device, it has the refrigerant circuit of refrigerant circulation, wherein,

Described refrigerant circuit has:

Fluid machinery, it has: power recovery mechanism, it reclaims power from working fluid; Auxiliary compressor, it is by the described motivational drive of reclaiming; Axle, it links described power recovery mechanism and described auxiliary compressor, so that the described power that reclaims is delivered to described auxiliary compressor from described power recovery mechanism;

To in the described auxiliary compressor of described fluid machinery, prepare the main compressor that the refrigeration agent after compressing further compresses;

The radiator of the refrigeration agent after cooling is compressed by described main compressor;

Make from the vaporizer of the refrigeration agent evaporation of the described power recovery mechanism ejection of described fluid machinery,

Described power recovery mechanism comprises:

(a1) the first obstruction component;

(g1) the second suction port, its be arranged at described the second obstruction component and described axle axially on the position relative with described the first suction port, and follow the rotation of described piston and open and close, so that working fluid flows into described on high-tension side working room.

2. refrigerating circulatory device according to claim 1, wherein,

Described power recovery mechanism also comprises:

(h1) the first ejiction opening, it is arranged at described the first obstruction component, and follows the rotation of described piston and open and close, so that working fluid flows out from the working room of described low voltage side;

(i1) the second ejiction opening, its be arranged at described the second obstruction component and described axially on the position relative with described the first ejiction opening, and follow the rotation of described piston and open and close, so that working fluid flows out from the working room of described low voltage side.

3. refrigerating circulatory device according to claim 2, wherein,

Described the first ejiction opening has the opening shape identical with the opening shape of described the second ejiction opening.

4. refrigerating circulatory device according to claim 2, wherein,

Described the first ejiction opening has the opening area that equates with the opening area of described the second ejiction opening.

5. refrigerating circulatory device according to claim 1, wherein,

Described the first suction port has the opening shape identical with the opening shape of described the second suction port and has the opening area that equates with the opening area of described the second suction port,

The switching of described the first suction port is constantly constantly consistent with the switching of described the second suction port.

6. refrigerating circulatory device according to claim 1, wherein,

Described power recovery mechanism also comprises the suction path of supplying with to described on high-tension side working room via described the first suction port and described the second suction port respectively from the outside of this power recovery mechanism for working fluid,

Described suction path comprises: (i) general suction path, and its outer circumferential face from described the second obstruction component extends towards the center of described axle; (ii) first suck the path, it axially runs through described clutch release slave cylinder to described the first suction port from described general suction path branches and along described, supplying with working fluid to described on high-tension side working room from described general suction path via described the first suction port; (iii) second suck the path, its footpath at described axle upwards sucks position in the inner part, path than described first and extends axially to described the second suction port from described general suction path branches and along described, supplying with working fluid to described on high-tension side working room from described general suction path via described the second suction port.

7. refrigerating circulatory device according to claim 6, wherein,

Described the first suction path has the large sectional area of sectional area than described the second suction path.

8. refrigerating circulatory device according to claim 1, wherein,

Described auxiliary compressor comprises:

(a2) lower obstruction component;

(b2) upper obstruction component, itself and described lower obstruction component are opposed;

(c2) the second clutch release slave cylinder, it is along a part that circumferentially centers on described axle, and two ends are inaccessible by described lower obstruction component and described upper obstruction component;

(d2) the second piston, it is installed on described axle in described the second clutch release slave cylinder, and self outer circumferential face and the inner peripheral surface of described the second clutch release slave cylinder between form the second working room;

(e2) the second partition member, it is divided into described the second working room the second working room and on high-tension side second working room of low voltage side;

(f2) the first suction port of auxiliary compressor, it is arranged at described lower obstruction component, and follows the rotation of described the second piston and open and close, so that working fluid flows into the second working room of described low voltage side;

(g2) the second suction port of auxiliary compressor, its be arranged at described upper obstruction component and described axle axially on the position relative with the first suction port of described auxiliary compressor, and follow the rotation of described the second piston and open and close, so that working fluid flows into the second working room of described low voltage side.

9. refrigerating circulatory device according to claim 8, wherein,

Described auxiliary compressor also comprises:

(h2) the first ejiction opening, it is arranged at described lower obstruction component, and follows the rotation of described the second piston and open and close, so that working fluid flows out from described on high-tension side the second working room;

(i2) the second ejiction opening, its be arranged at described upper obstruction component and described axially on the position relative with described the first ejiction opening, and follow the rotation of described the second piston and open and close, so that working fluid flows out from described on high-tension side the second working room.

10. refrigerating circulatory device according to claim 8, wherein,

Described fluid machinery also has the seal container of accommodating described power recovery mechanism, described auxiliary compressor and described axle,

Described power recovery mechanism and described auxiliary compressor axially are adjacent to be disposed in the described seal container described, so that described first obstruction component of the described power recovery mechanism described lower obstruction component as described auxiliary compressor is shared.

11. refrigerating circulatory device according to claim 5, wherein,

Described the first suction port and described the second suction port respectively only when described piston is positioned at upper dead center by described piston locking, during whole the moment that is positioned at upper dead center except described piston, at least a portion of at least a portion of described the first suction port and described the second suction port is exposed to described on high-tension side working room respectively.

12. refrigerating circulatory device according to claim 1, wherein,

Also have:

Bypass circulation, it is circuitous in described auxiliary compressor, and connects the outlet of described vaporizer and the entrance of described main compressor;

Bypass valve, it is arranged at described bypass circulation, and opens when this refrigerating circulatory device starting,

Described power recovery mechanism also comprises:

13. refrigerating circulatory device according to claim 12, wherein,

The opening area that described the first ejiction opening has the opening shape identical with the opening shape of described the second ejiction opening and equates with the opening area of described the second ejiction opening,

The switching of described the first ejiction opening is constantly constantly consistent with the switching of described the second ejiction opening,

Described the first ejiction opening and described the second ejiction opening respectively only when described piston is positioned at upper dead center by described piston locking, during whole the moment that is positioned at upper dead center except described piston, at least a portion of at least a portion of described the first ejiction opening and described the second ejiction opening is exposed to described on high-tension side working room respectively.