CN203203286U - Refrigerating plant - Google Patents
Refrigerating plant Download PDFInfo
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- CN203203286U CN203203286U CN 201320189441 CN201320189441U CN203203286U CN 203203286 U CN203203286 U CN 203203286U CN 201320189441 CN201320189441 CN 201320189441 CN 201320189441 U CN201320189441 U CN 201320189441U CN 203203286 U CN203203286 U CN 203203286U
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- producing medium
- cold
- guiding valve
- screw rotor
- refrigerant
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Abstract
The utility model discloses a refrigerating plant, which is provided with a suction pressure sensor (141) for detecting the suction pressure of a compression chamber and a suction temperature sensor (142) for detecting the temperature of a refrigerant to be sucked into the compression chamber, and when the degree of superheat of the sucked refrigerant rises to a preset value, the amount of movement of a sliding valve towards a full-open side is limited so as to enable the amount of movement to be smaller than the maximum amount of movement. Thus, under the operation state that the degree of overheat of refrigerant gas to be sucked into a screw rotor (40) is increased, the screw rotor (40) can be prevented from contacting with a shell or being burned.
Description
Technical field
The utility model relates to a kind of refrigerating plant with varying capacity helical-lobe compressor, particularly a kind of unloading mechanism by having used guiding valve refrigerating plant that the capacity of helical-lobe compressor is controlled.
Background technology
Up to the present, helical-lobe compressor uses as the compressor that cold-producing medium, air are compressed.For example, the single screw compressor that comprises a screw rotor and two gate rotors is disclosed in patent documentation 1.
Screw rotor and gate rotor are installed in the housing in this single screw compressor.Be formed with helical groove at screw rotor, form discharge chambe by this groove.Enclosure interior is formed with low-voltage space and high-pressure space.After screw rotor was driven in rotation, the fluid in the low-voltage space will be inhaled into discharge chambe and compressed, and compressed fluid sprays to high-pressure space in discharge chambe.
In patent documentation 1 disclosed helical-lobe compressor, be provided with guiding valve.It is relative and can slide along the direction parallel with the rotating shaft of screw rotor that guiding valve is arranged to the outer peripheral face of its front (being positioned at the face of the radially inner side of housing) and screw rotor.The guiding valve of patent documentation 1 disclosed single screw compressor is used in the unloading mechanism that the working capacity of compressor is regulated.
This guiding valve constitutes: the aperture of bypass path that will make compression cold-producing medium midway return the suction side of discharge chambe is adjusted to standard-sized sheet from full cut-off.Guiding valve can be along the moving axially of screw rotor, and adjust the aperture of bypass path according to its position, and the flow of the bypass gas that flows through bypass path is changed.And control the working capacity of helical-lobe compressor by the flow of adjusting bypass gas.
Patent documentation 1: Japanese Laid-Open Patent Publication JP 2010-285973 communique
-utility model technical problem to be solved-
Because in opening the running unloaded process that guiding valve carries out, the refrigerant gas in the compression way that temperature has risen returns the suction side, just rises so be inhaled into the temperature of the cold-producing medium of discharge chambe.Following bad phenomenon might occur if the cold-producing medium that the temperature rising degree of superheat is increased compresses then: screw rotor contacts with housing or screw rotor and housing are burnt and quit work.
Particularly, under the low working capacity operating condition that thin low evaporating temperature operating condition, the circulating mass of refrigerant of suction cold-producing medium tails off or under the state of the lack of refrigerant in the refrigerant loop, the result of running unloaded causes the degree of superheat of the cold-producing medium of suction side to be easy to increase.
The motor operated by rotary motion of drive screw rotor is between the opening of the suction inlet of helical-lobe compressor and described bypass path.Therefore, in the process of carrying out running unloaded, the amount of the refrigerant gas that motor is cooled off is to obtain after the discharge capacity by screw rotor deducts the flow of bypass gas, than lacking in the normal operation process.And the temperature with the cooled refrigerant gas of motor significantly rises, and the degree of superheat that is about to suck the refrigerant gas in the screw rotor is easy to rise, screw rotor contact with housing or screw rotor burn and out-of-work possibility with regard to raising.
The utility model content
The utility model is finished in view of above-mentioned each problem points just, and its purpose is: can prevent also that under the operating condition that the degree of superheat that is about to suck the refrigerant gas in the screw rotor increases screw rotor from contacting with housing or burn.
-in order to the technical scheme of technical solution problem-
The utility model of first aspect is take a kind of refrigerating plant as prerequisite, and this refrigerating plant comprises: the refrigerant loop with varying capacity helical-lobe compressor.Described helical-lobe compressor comprises: housing, driven the screw rotor that rotates in housing, the bypass path that is communicated with the suction side of this discharge chambe from the compression half-way that is formed on the discharge chambe between housing and the screw rotor and the unloading mechanism with guiding valve of the removable aperture of adjusting this bypass path.
This refrigerating plant comprises: the suction pressure sensor and detecting that detects the suction pressure of discharge chambe is about to suck the inlet temperature sensor of the temperature of the cold-producing medium in the discharge chambe, described unloading mechanism constitutes: when the degree of superheat that sucks cold-producing medium rises to the value that sets in advance, unloading mechanism limits this guiding valve towards the amount of movement of standard-sized sheet one side, make this towards the amount of movement of standard-sized sheet one side less than maximum amount of movement.
In the utility model of this first aspect, obtain the suction degree of superheat by pressure anti-saturation temperature and actual inlet temperature that suction pressure is obtained, just the amount of movement to guiding valve limits when this suction degree of superheat rises to the value that sets in advance.After the amount of movement of guiding valve was restricted, the flow that flows through the bypass gas of bypass path in the running unloaded process will reduce.This bypass gas is the cold-producing medium that is compressed in discharge chambe in the way, and temperature is higher than sucking cold-producing medium, but because flow has reduced, so can suppress to be inhaled into the degree of superheat of the cold-producing medium of discharge chambe.Therefore be that the cold-producing medium that suppressed of the degree of superheat is compressed.
The utility model of second aspect is such, in the utility model of first aspect, comprises the mechanism for filling liquid that liquid refrigerant is injected the suction side of described discharge chambe in the described refrigerant loop.Described mechanism for filling liquid constitutes: when the degree of superheat that is sucking cold-producing medium rose to that working capacity is greater than desired value under the state that amount of movement that the value that sets in advance causes guiding valve is subject to limit processed, this mechanism for filling liquid injected the fluid injection action of liquid refrigerant.
In the utility model of this second aspect, when working capacity is greater than desired value under the state of the amount of movement that has been limited guiding valve by unloading mechanism, carried out liquid refrigerant is injected the fluid injection action of the suction side of discharge chambe by unloading mechanism.So, suck the amount minimizing of the cold-producing medium of compressor from evaporimeter one side of refrigerant loop, the internal circulating load of cold-producing medium just descends.And, because if liquid refrigerant is injected in the suction side to discharge chambe, the degree of superheat that sucks cold-producing medium will descend, so can increase the amount of movement towards standard-sized sheet one side of guiding valve, increase the bypass gas amount under the running unloaded, reduce the working capacity of compressor.Cause the degree of superheat of cold-producing medium to rise if increase the bypass gas amount, then the preferred injection rate that further increases liquid refrigerant makes the degree of superheat and the working capacity balance of cold-producing medium.
The utility model of the third aspect is such, and in the utility model of second aspect, described helical-lobe compressor comprises the suction side that is arranged on screw rotor and the motor that drives this screw rotor.Described mechanism for filling liquid constitutes: liquid refrigerant is introduced the suction side of screw rotor and the upstream side of motor.
In the utility model of this third aspect, passed through motor because inject the cold-producing medium of the suction side of compressor with liquid state, so motor is the suction refrigerant cools that has been descended by temperature.
The utility model of fourth aspect is such, in the utility model of first aspect, described refrigerant loop comprises the mechanism for filling liquid that liquid refrigerant is injected the suction side of described discharge chambe, described mechanism for filling liquid constitutes: when the temperature that rises to ejection cold-producing medium under the state that amount of movement that the value that sets in advance causes guiding valve is subject to limit processed when the degree of superheat that is sucking cold-producing medium was higher than desired value, this mechanism for filling liquid injected the fluid injection action of liquid refrigerant.
In the utility model of the 4th fermentation, although limited the amount of movement of guiding valve, the temperature of ejection cold-producing medium still rises when excessive, just carries out injecting to the suction side of discharge chambe the fluid injection action of liquid refrigerant.Because if liquid refrigerant is injected in the suction side of discharge chambe, the temperature that sucks cold-producing medium just descends, so also can suppress to spray the temperature of cold-producing medium.
The utility model of the 5th aspect is such, and in the utility model of fourth aspect, described mechanism for filling liquid constitutes: the injection rate of adjusting liquid refrigerant according to the temperature of ejection cold-producing medium.
In the utility model aspect the 5th, for example be arranged on the aperture of the flow rate regulating valve in the mechanism for filling liquid by adjustment, and adjust the injection rate of liquid refrigerant based on the temperature of ejection cold-producing medium, then can directly suppress to spray temperature and rise.
The effect of-utility model-
According to the utility model, increase if suck the degree of superheat of cold-producing medium, then utilize unloading mechanism that the amount of the refrigerant gas of the suction side of returning discharge chambe is reduced, just can suppress to suck like this degree of superheat of cold-producing medium.Therefore, can prevent that screw rotor from contacting with housing or burn.Particularly, under the low working capacity operating condition that sucks the thin low evaporating temperature operating condition of cold-producing medium, circulating mass of refrigerant minimizing or under the state of the refrigerant charge quantity not sufficient in the refrigerant loop, the refrigerant superheat degree that also can suppress the suction side increases, and prevents that therefore the effect of screw rotor burn etc. is very high.
In refrigerant loop, the temperature sensor of the temperature that detects cold-producing medium is set at the outlet side of evaporimeter generally.If use together the inlet temperature sensor in this temperature sensor and the utility model, both sides' temperature this phenomenon that rises is all detected, then can accurately not enough this phenomenon of the cold-producing medium loading in the refrigerant loop be detected.
Utility model according to above-mentioned second aspect, although limited the amount of movement of guiding valve towards standard-sized sheet one side, working capacity is during but still greater than desired value, then carries out fluid injection and moves to reduce the internal circulating load of cold-producing medium and make the degree of superheat that sucks cold-producing medium and the working capacity balance of compressor.Therefore, can either prevent that compressor is out of order and can make compressor carry out the low capacity running.
According to the utility model of the above-mentioned third aspect, because the cold-producing medium that injects the suction side of compressor with liquid state is cooled motor by motor, rise so can suppress fully the temperature of motor.
Utility model according to above-mentioned the 4th, the 5th aspect, although limited the amount of movement of guiding valve, the temperature of ejection cold-producing medium but still rises excessively, then reduce the temperature that sucks cold-producing medium by injecting liquid refrigerant to the suction side of discharge chambe, consequently also can suppress to spray the temperature of cold-producing medium.
Description of drawings
Fig. 1 is loop structure figure, and not only the refrigerant loop of the refrigerating plant that embodiment of the present utility model is related has been illustrated out, and the schematic configuration of helical-lobe compressor has also been illustrated out.
Fig. 2 is the schematic diagram that the part of refrigerant loop is shown.
Fig. 3 is the cutaway view of structure that the major part of helical-lobe compressor is shown.
Fig. 4 is the cutaway view that the A-A section among Fig. 3 is shown.
Fig. 5 takes out the major part of helical-lobe compressor and the stereogram that shows.
Fig. 6 is the stereogram of guiding valve.
Fig. 7 is the front view of guiding valve.
Fig. 8 (A), Fig. 8 (B) and Fig. 8 (C) are respectively the top views that the working condition of the compressing mechanism in the helical-lobe compressor is shown, Fig. 8 (A) represents suction process, Fig. 8 (B) represents compression process, Fig. 8 (C) expression ejection process.
Fig. 9 is the part amplification view of helical-lobe compressor, and the working capacity maximum rating is shown.
Figure 10 is the part amplification view of helical-lobe compressor, and the working capacity minimum state is shown.
-symbol description-
The 1-helical-lobe compressor; The 10-housing; The 15-motor; The 23-discharge chambe; The 33-bypass path; The 40-screw rotor; The 70-guiding valve; The 80-unloading mechanism; The 110-refrigerant loop; The 120-mechanism for filling liquid; 141-suction pressure sensor; 142-inlet temperature sensor.
The specific embodiment
Below, describe embodiment of the present utility model in detail with reference to accompanying drawing.
＜unitary construction of refrigerant loop 〉
As shown in Figure 1, the refrigerating plant 100 in the present embodiment is provided with varying capacity single screw compressor 1 (being helical-lobe compressor hereinafter to be referred as it) in the refrigerant loop 110 that carries out kind of refrigeration cycle.
This refrigerant loop 110 consists of by the closed-loop path that consists of behind helical-lobe compressor 1, condenser 111, the first expansion valve 112, gas-liquid separator 113, the second expansion valve 114 and the evaporimeter 115 is set.Particularly, ejection one side of helical-lobe compressor 1 is connected with the gas side of condenser 111, and the liquid side of condenser 111 is connected with the cold-producing medium inflow entrance of gas-liquid separator 113 through the first expansion valve 112.Cold-producing medium flow export on the gas-liquid separator 113 is connected with the liquid side of evaporimeter 115 through the second expansion valve 114, and the gas side of evaporimeter 115 is connected with the suction side of helical-lobe compressor 1.
Gas-liquid separator 113 is connected with helical-lobe compressor 1 through mechanism for filling liquid 120.Be provided with liquid injection port 121 on the gas-liquid separator 113.Be connected with liquid injection pipe 123 on this liquid injection port 121, be provided with magnetic valve 122 on this liquid injection pipe 123, this liquid injection pipe 123 is connected to middle pressure position with respect to the compressing mechanism 20 with helical-lobe compressor 1.The fluid injection arm 125 that flow rate regulating valve 124 is installed is arranged on the downstream of magnetic valve 122 on the liquid injection pipe 123.Fluid injection arm 125 is connected with the intake line 116 of refrigerant loop 110.
The part of refrigerant loop 110 as shown in Figure 2 is the same, and the suction pressure sensor 141 and detecting that is provided with the pressure of the cold-producing medium that detects the evaporator outlet side in the refrigerant loop 110 of this refrigerating plant 100 is about to be inhaled into the inlet temperature sensor 142 of temperature of the cold-producing medium of discharge chambe 23.Be provided with the temperature sensor 143 of the temperature of the cold-producing medium that detects the evaporator outlet side on the intake line 116.
＜unitary construction of helical-lobe compressor 〉
As shown in Figure 1, in this helical-lobe compressor 1, compressing mechanism 20 and its motor 15 of driving are installed in the housing 10.This helical-lobe compressor 1 constitutes semi-hermetic type compressor.
In housing 10, motor 15 is arranged in the low-voltage space S1, and compressing mechanism 20 is arranged between low-voltage space S1 and the high-pressure space S2.Driving shaft 21 and the motor 15 of compressing mechanism 20 are connected.The motor 15 of helical-lobe compressor 1 is connected with source power supply (not shown).Source power supply is supplied with motor 15 with alternating current, and motor 15 is by certain rotating speed rotation.
In housing 10, gs-oil separator 16 is arranged in the high-pressure space S2.Gs-oil separator 16 is separated refrigerating machine oil from the cold-producing medium by compressing mechanism 20 ejections.In high-pressure space S2 gs-oil separator 16 below be formed with that to store lubricating oil be the reservoir compartment 17 of refrigerating machine oil.The refrigerating machine oil of in gs-oil separator 16, having been separated from cold-producing medium towards below flow down and be stored in the reservoir compartment 17.
As shown in Figure 3 and Figure 4, compressing mechanism 20 comprise the cylindrical wall 30 that is formed in the housing 10, be arranged in this cylindrical wall 30 screw rotor 40 and with two gate rotors 50 of these screw rotor 40 engagements.Cylindrical wall 30 consists of cylinder part with retainer described later (bearing holder) 35.Driving shaft 21 is inserted in the screw rotor 40, and screw rotor 40 and driving shaft 21 are connected by key 22.Driving shaft 21 is arranged on the same axial line with screw rotor 40.The motor 15 that screw rotor 40 is arranged on the suction side of this screw rotor 40 is driving in housing 10 interior rotations.
Retainer 35 is inserted in the end of high-pressure space S2 one side of cylindrical wall 30.Retainer 35 roughly forms cylindric.The diameter essence of the inner peripheral surface of the external diameter of retainer 35 and cylindrical wall 30 (that is the face that slips with the outer peripheral face of screw rotor 40) equates.It is spigot surface 37 that the part of slipping with guiding valve 70 described later in the outer peripheral face of retainer 35 becomes the face of slipping.Be provided with ball bearing 36 in the inboard of retainer 35.Insert in the ball bearing 36 one end of driving shaft 21, and this ball bearing 36 is supporting driving shaft 21 rotates freely this driving shaft 21.
As shown in Figure 5, screw rotor 40 is roughly to form columned metal-made parts.Screw rotor 40 rotatably is embedded in cylindrical wall 30, and the inner peripheral surface of the outer peripheral face of screw rotor 40 and cylindrical wall 30 is through the oil film sliding-contact.Be formed with a plurality of (being in the present embodiment 6) helicla flute 41 from an end of screw rotor 40 towards other end spiral extension at the peripheral part of screw rotor 40.
The end of front one side in Fig. 5 of each helicla flute 41 on the screw rotor 40 is top, and the end of a side is terminal at a distance in this Fig. 5.The end (end of suction side) of screw rotor 40 front one side in Fig. 5 forms round platform.In screw rotor shown in Figure 5 40, the top of helicla flute 41 opens wide towards the end face of front one side that forms conical surface shape, and the terminal of helicla flute 41 is closed by the end face of distant place one side.
Each gate rotor 50 is resin parts.On each gate rotor 50, form tabular a plurality of (being the in the present embodiment 11) lock 51 of rectangle and be arranged to radial.Each gate rotor 50 with respect to the rotating shaft state arrangement axisymmetricly of screw rotor 40 in cylindrical wall 30 outsides.The axle center of each gate rotor 50 is vertical with the axle center of screw rotor 40.The lock 51 that each gate rotor 50 is arranged on it runs through the part of cylindrical wall 30 and helicla flute 41 engagements of screw rotor 40.
The rotor supports parts 55 that gate rotor 50 is installed are adjacent with cylindrical wall 30, are installed in housing 10 interior divisions gate rotor chamber 90 out (with reference to Fig. 4).The rotor supports parts 55 that are arranged on screw rotor 40 right sides among Fig. 4 with gate rotor 50 become lower end side towards setting.On the other hand, the rotor supports parts 55 that screw rotor 40 left sides in the figure are set with gate rotor 50 become upper end side towards setting.The axial region 58 of each rotor supports parts 55 is being supported by the bearing cap in the gate rotor chamber 90 (bearing housing) 91 through ball bearing 92,93 and is rotating freely.In addition, each gate rotor chamber 90 is communicated with low-voltage space S1.
In compressing mechanism 20, the space that is fenced up by inner peripheral surface and the helicla flute 41 on the screw rotor 40, the lock 51 of gate rotor 50 of cylindrical wall 30 becomes discharge chambe 23.Helicla flute 41 on the screw rotor 40 is open towards low-voltage space S1 in the end, suction side, and this open portion is the suction inlet 24 of compressing mechanism 20.
Be provided with capacity regulating guiding valve 70 on the helical-lobe compressor 1.This guiding valve 70 is arranged in the guiding valve installation portion 31.Guiding valve installation portion 31 is that cylindrical wall 30 bloats next part at its circumferencial direction two places towards radial outside, forms from ejection side end (right part Fig. 3) the roughly semicircular cylinder shape that extend (left part among Fig. 3) towards the end, suction side.Guiding valve 70 constitutes and can slide along the axis direction of cylindrical wall 30, and the wall with screw rotor 40 under the state that guiding valve 70 is inserted in the guiding valve installation portion 31 is relative.The detailed structure aftermentioned of guiding valve 70, the mobile terminal towards ejection one side among Fig. 3 is standard-sized sheet sidesway moved end, is full cut-off sidesway moved end towards the mobile terminal of suction side.
In housing 10, be formed with access 32 in the outside of cylindrical wall 30.Be formed with an access 32 corresponding to each guiding valve installation portion 31.Access 32 is the axially extended paths along cylindrical wall 30, and the one end opens wide towards low-voltage space S1, and its other end is open ended towards the suction side of guiding valve installation portion 31.The part adjacent with the other end (right-hand member among Fig. 3) of access 32 consists of valve seat (seat) section 13 of the end face P2 close contact of guiding valve 70 in the cylindrical wall 30.Seat portion 13 face relative with the end face P2 of guiding valve 70 consists of valve seat P1.
When guiding valve 70 be partial to high-pressure space S2 (in Fig. 1 driving shaft 21 axially as left and right directions the time close right side) during slip, understand between the end face P2 of the end face P1 of guiding valve installation portion 31 and guiding valve 70 forming end play.This end play is configured for making cold-producing medium to return the bypass path 33 of low-voltage space S1 from discharge chambe 23 with access 32.That is to say, an end of bypass path 33 is that low-voltage space S1 is communicated with the suction side of discharge chambe 23, and the other end of bypass path 33 can be that the inner peripheral surface of cylindrical wall 30 opens wide towards the compression half-way of discharge chambe 23.If guiding valve 70 moves to change the aperture of bypass path 33, the capacity of compressing mechanism 20 will change.Be formed be used to the ejiction opening 25 that discharge chambe 23 is communicated with high-pressure space S2 at guiding valve 70.
Be provided with on the described helical-lobe compressor 1 and drive the spool actuation mechanism (unloading mechanism) 80 that the aperture of bypass path 33 is adjusted in guiding valve 70 slips.The slide plate 84 that this spool actuation mechanism 80 comprises the cylinder 81 that is fixed on the bearing fender bracket 35, be installed in piston 82 in this cylinder 81, be connected with the piston rod 83 of this piston 82, the link rod 85 that links this slide plate 84 and guiding valve 70 and in Fig. 1 right-hand (making slide plate 84 leave the direction of housing 10) to the spring 86 of slide plate 84 application of forces.
In spool actuation mechanism 80 shown in Figure 3, the interior pressure of the leftward space of piston 82 (spaces of close screw rotor 40 1 sides of piston 82) equates with the interior pressure of the rightward space (spaces of close slide plate 84 1 sides of piston 82) of piston 82, when the interior pressure of the inner pressure ratio rightward space of leftward space is high, just right-hand movement in the figure of piston 82.And spool actuation mechanism 80 constitutes: the interior pressure of the rightward space by regulating piston 82 (being the gas pressure in the rightward space) is adjusted the position of guiding valve 70.
In the operation process of helical-lobe compressor 1, the suction pressure of compressing mechanism 20 acts on the end face in the axial end of guiding valve 70, on the other end of ejection pressure-acting in the axial end of guiding valve 70 of compressing mechanism 20.Therefore, in the operation process of helical-lobe compressor 1, the power of guiding valve 70 being pushed on the direction of low-voltage space S1 one side always acts on the guiding valve 70.Therefore, when the interior pressure of the leftward space of the piston 82 that changes spool actuation mechanism 80 and rightward space, the size of returning the power on the direction of guiding valve 70 towards high-pressure space S2 one layback can change, and consequently the position of guiding valve 70 can change.
＜structure of guiding valve 〉
With reference to Fig. 6 and Fig. 7 guiding valve 70 is described in detail.
Guiding valve 70 is made of valve body 71, guide part 75 and linking part 77.In this guiding valve 70, valve body 71, guide part 75 and linking part 77 are made of metal-made parts.That is to say, valve body 71, guide part 75 and linking part 77 form as one.
Also illustrate among Fig. 4, valve body 71 is left the shape that part becomes after being a part of cutting away solid cylinder, and (part of front one side: the part that is positioned at the housing radially inner side) state towards screw rotor 40 is arranged on housing 10 to be reamed part with valve body 71.In the valve body 71, the slip face 72 relative with screw rotor 40 is arc surface and the extending axially towards valve body 71 that its radius of curvature equates with the radius of curvature of the inner peripheral surface of cylindrical wall 30.The face that slips 72 and the screw rotor 40 of this valve body 71 slip, and towards the discharge chambe 23 that is formed by helicla flute 41.
In the valve body 71, an end face (left side among Fig. 7) is the axial vertical plane with valve body 71.This end face becomes the end face P2 on the slippage direction of guiding valve 70.Other end in the valve body 71 (right side among Fig. 7) is for favouring the axial inclined-plane of valve body 71.Valve body 71 be that the gradient of the helicla flute 41 on gradient and the screw rotor 40 of other end on inclined-plane equates.
Linking part 77 forms column and shorter, connecting valve body 71 and guide part 75.This linking part 77 is arranged on a side opposite with the face that slips 76 of the face that slips 72 of valve body 71, guide part 75 and departs from this and slips face 72 and this slips the position of face 76.In the guiding valve 70, the space of the space between valve body 71 and the guide part 75 and the rear side of guide part 75 (namely with slipping face 76 opposite a side) forms the path of ejection gas, becomes ejiction opening 25 between the face that slips 72 of valve body 71 and the face that slips 76 of guide part 75.
Be provided with controller 130 in this refrigerating plant 100 as shown in Figure 1.Controller 130 constitutes: the working capacity of control helical-lobe compressor 1, adjust the working condition that first, second expansion valve 112,114 aperture are controlled refrigerant loop 110, and the working condition of control mechanism for filling liquid 120.
Particularly, the detected value input control device 130 of the detected value of suction pressure sensor 141 and inlet temperature sensor 142 is obtained the degree of superheat that sucks cold-producing medium by the suction pressure anti-saturation temperature that detects at suction pressure sensor 141 with the actual inlet temperature that detects at inlet temperature sensor 142.When the degree of superheat of the suction cold-producing medium of obtaining rises to the value (for example 50 ℃) that sets in advance, then by the amount of movement of described unloading mechanism 80 restriction guiding valves 70 towards standard-sized sheet one side, make this amount of movement towards standard-sized sheet one side less than maximum amount of movement.That is to say, amount of movement is limited, so that the position between the mobile terminal of standard-sized sheet one side (spraying a side) of the mobile terminal of full cut-off one side (suction side) of guiding valve shown in Figure 9 and guiding valve shown in Figure 10 becomes the position of the mobile terminal of ejection one side.If the amount of movement to guiding valve 70 limits, the amount of returning the suction side of discharge chambe 23 by be compressed to cold-producing medium that temperature midway risen at discharge chambe 23 will reduce, and therefore can suppress to suck the degree of superheat of cold-producing medium.
Described controller 130 constitutes the working condition of further control mechanism for filling liquid 120.Particularly, when the degree of superheat that is sucking cold-producing medium rises under the state that the amount of movement of value (for example 50 ℃) guiding valve 70 that sets in advance is restricted and working capacity when larger than desired value, carried out liquid refrigerant is injected the fluid injection action of the suction side of discharge chambe 23 by described mechanism for filling liquid 120.That is to say, magnetic valve 122 is opened, and middle compression refrigerant is injected compressing mechanism 20, and flow has been carried out the suction side of the low pressure refrigerant injection discharge chambe 23 of adjustment by flow rate regulating valve.
When injecting liquid refrigerant towards the suction side of discharge chambe, the refrigerant flow that sucks compressing mechanism 20 from intake line 116 will reduce.Therefore, apparent (apparent) working capacity of helical-lobe compressor 1 reduces.
Because when liquid refrigerant is injected the suction side of discharge chambe 23, the degree of superheat that sucks cold-producing medium just descends, so can increase the slippage (reducing the mobile quantitative limitation towards standard-sized sheet one side) of guiding valve 70.Increase by the amount of movement that increases guiding valve 70 if return the amount of intermediate pressure by-pass gaseous refrigerant of the suction side of discharge chambe 23, then further adjust reservoir quantity, control the working capacity of helical-lobe compressor 1 and the degree of superheat that sucks cold-producing medium to such an extent that reach balance.
In addition, in the present embodiment, as depicted in figs. 1 and 2, utilize described mechanism for filling liquid 120 that liquid refrigerant is injected the suction side of screw rotor 40 and the upstream side of motor 15, motor 15 namely can be cooled off by liquid refrigerant.
Rise to the value that sets in advance and when making the temperature of ejection cold-producing medium under the state that the amount of movement of guiding valve 70 is restricted higher than desired value (for example 120 ℃), described mechanism for filling liquid 120 will carry out the fluid injection action under the control of described controller 130 in the degree of superheat that sucks cold-producing medium.Reservoir quantity is adjusted by the aperture of controlling flow rate regulating valve 124 according to the temperature of ejection cold-producing medium.Control the temperature of ejection cold-producing medium by such adjustment reservoir quantity.
The working condition of-helical-lobe compressor-
With reference to Fig. 8 the working condition of helical-lobe compressor 1 integral body is explained.
One starts the motor 15 in the helical-lobe compressor 1, and screw rotor 40 will rotate along with driving shaft 21 rotations.Gate rotor 50 also can rotate along with these screw rotor 40 rotations, and compressing mechanism 20 carries out suction process, compression process and ejection process repeatedly.Here, mainly the discharge chambe 23 that represents with the shade pore among Fig. 8 is explained.
Among Fig. 8 (A), the discharge chambe 23 that represents with the shade pore is communicated with low-voltage space S1.Form the lock that is positioned at this figure downside 51 engagements of helicla flute 41 with the gate rotor 50 of this discharge chambe 23.After screw rotor 40 rotations, this lock 51 just can relatively move towards the terminal of helicla flute 41, and the volume of discharge chambe 23 can be followed in this and increase.Consequently, the low-pressure gaseous refrigerant in the low-voltage space S1 is inhaled into discharge chambe 23 through suction inlet 24.
Next, explanation is how the working capacity of the compressing mechanism 20 that used guiding valve 70 to be controlled with reference to Fig. 3, Fig. 9 and Figure 10.In addition, the capacity of compressing mechanism 20 means " certainly sucking pipe jointing part 11 in the time per unit by the refrigerant amount in the evaporimeter suction compressor 1 ".The working capacity synonym of the capacity of this compressing mechanism 20 and helical-lobe compressor 1.
Be pulled under the state of the leftmost side among Fig. 3 at guiding valve 70, as shown in Figure 9, guiding valve 70 is positioned at the mobile terminal of full cut-off one side (suction side).The end face P2 of guiding valve 70 is pulled on the valve seat P1 of seat portion 13, and the capacity of compressing mechanism 20 is maximum.That is to say, under this state, bypass path 33 is by valve body 71 full cut-offs of guiding valve 70, and the refrigerant gas that sucks discharge chambe 23 from low-voltage space S1 all sprays to high-pressure space S2.Therefore, the working capacity of helical-lobe compressor 1 is maximum under this state.
On the other hand, return when guiding valve 70 right side in Fig. 3, the end face P2 of guiding valve 70 has left after the valve seat P1, and 33 inner peripheral surfaces towards cylindrical wall 30 of bypass path open wide.Under this state, from low-voltage space S1 suck discharge chambe 23 refrigerant gas some return low-voltage space S1 from compression process discharge chambe 23 midway by bypass path 33, remainder then is compressed to last and is sprayed to high-pressure space S2.
Along with (that is to say every increasing between the valve seat P1 of the end face P2 of guiding valve 70 and guiding valve installation portion 31, the aperture area of bypass path 33 on the inner peripheral surface of cylindrical wall 30 increases), the refrigerant amount that returns low-voltage space S1 by bypass path 33 increases, and the refrigerant amount that sprays to high-pressure space S2 reduces.And the interval between the end face P2 of guiding valve 70 and the valve seat P1 of guiding valve installation portion 31 is larger, and the flow that sucks the cold-producing medium of compressor 1 from intake line 116 reduces, and the capacity of compressing mechanism 20 reduces.
When guiding valve 70 was positioned at the mobile terminal of standard-sized sheet side shown in Figure 10 (ejection side), the distance between the end face P2 of guiding valve 70 and the cylindrical wall 30 valve seat P1 was maximum.That is to say, under this state, the aperture area that bypass path 33 is positioned on the inner peripheral surface of barrel 30 is maximum, and the flow of bypass gaseous refrigerant that returns low-voltage space S1 from discharge chambe 23 by bypass path 33 is maximum.Therefore, under this state, the refrigerant flow that sprays to high-pressure space S2 from compressing mechanism 20 is minimum.And if the flow of bypass gaseous refrigerant is maximum, the flow of cold-producing medium that sucks compressors 1 from intake line 116 is just minimum, and the working capacity of helical-lobe compressor 1 is just minimum.
In addition, the cold-producing medium that sprays to high-pressure space S2 from discharge chambe 23 is first towards ejiction opening 25 diffluences that are formed on the guiding valve 70, and afterwards, the path of guide part 75 back sides one side of this cold-producing medium by being formed on guiding valve 70 flows in the high-pressure space S2.
In the present embodiment, when the degree of superheat that sucks cold-producing medium rises to the value (for example 50 ℃) that sets in advance, just the amount of movement towards standard-sized sheet one side by 80 pairs of guiding valves 70 of described unloading mechanism limits, make this towards the amount of movement of standard-sized sheet one side less than maximum amount of movement, the maximum amount of movement of guiding valve 70 is limited in the position (reference point line) between the mobile terminal of the mobile terminal of full cut-off one side shown in Figure 9 (suction side) and standard-sized sheet shown in Figure 10 one side (spraying a side).Like this after the amount of movement of restriction guiding valve 70, be compressed to the amount that the cold-producing medium that risen of temperature in the way returns the suction side of discharge chambe 23 and reduce in discharge chambe 23, the degree of superheat that sucks cold-producing medium is suppressed.
When the degree of superheat that is sucking cold-producing medium rises under the state that amount of movement that the value that sets in advance causes guiding valve 70 is restricted and working capacity during greater than desired value, then carried out liquid refrigerant is injected the fluid injection action of the suction side of discharge chambe 23 by described mechanism for filling liquid 120.When injecting liquid refrigerant towards the suction side of discharge chambe, the refrigerant flow that sucks compressing mechanism 20 from intake line 116 will reduce.Therefore the apparent working capacity of helical-lobe compressor 1 reduces.
If inject liquid refrigerant towards the suction side of discharge chambe 23, the degree of superheat that sucks cold-producing medium will descend, so can become and a kind of the slippage of guiding valve 70 is increased the state of (reducing the system limit towards the amount of movement of standard-sized sheet one side).If returning the middle compression refrigerant amount of the suction side of discharge chambe 23 increases by the amount of movement that increases guiding valve 70, so further adjust the injection rate of liquid refrigerant, just the degree of superheat of the working capacity of helical-lobe compressor 1 and suction cold-producing medium can be controlled to such an extent that reach balance.
When the temperature that rises to state that amount of movement that the value that sets in advance causes guiding valve 70 is restricted and ejection cold-producing medium in the degree of superheat that sucks cold-producing medium is higher than desired value (for example 120 ℃), then carry out the fluid injection action by the aperture of control flow rate regulating valve 124.The temperature that the temperature that sucks cold-producing medium by such reduction just can suppress to spray cold-producing medium rises excessive.
The effect of-embodiment-
According to present embodiment, when the degree of superheat that sucks cold-producing medium rises to the value (for example 50 ℃) that sets in advance, the degree of superheat that amount of movement by restriction guiding valve 70 suppresses to suck cold-producing medium rises, this phenomenon that quits work so can be suppressed in the course of work of compressing mechanism screw rotor contact housing or screw rotor burn.
When working capacity is greater than desired value under the state that the amount of movement at guiding valve 70 is restricted, by further carrying out the fluid injection action, then can reduce working capacity by limit inhibition degree of superheat rising edge.
When the ejection temperature is higher than desired value under the state that the amount of movement at guiding valve 70 is restricted, can prevent by injecting liquid refrigerant that also the ejection temperature of cold-producing medium from rising excessively.
(other embodiment)
Can also adopt in the above-described embodiment following structure.
For example, in the above-described embodiment, when the degree of superheat that sucks cold-producing medium rises to the value that sets in advance, just limit guiding valve 70 towards standard-sized sheet one sidesway momentum make this towards standard-sized sheet one sidesway momentum less than maximum amount of movement, and when working capacity is greater than desired value under the state that the amount of movement at guiding valve 70 is restricted, carry out the fluid injection action, but be not to carry out the fluid injection action.Also can prevent the bad phenomenon such as screw rotor burn in the situation that do not carry out the fluid injection action.
In the above-described embodiment, mechanism for filling liquid 120 is constituted liquid refrigerant is introduced the suction side of screw rotor 40 and the upstream side of motor 15, still liquid refrigerant is introduced between screw rotor 40 and the motor 15 also being fine.
In addition, above embodiment is preferred example in essence, and the intention of unrestricted the utility model, its applicable thing or its purposes scope.
-industrial applicability-
In sum, the utility model comprises that for utilization the refrigerating plant of capacity of unloading mechanism control helical-lobe compressor of guiding valve is useful.
Claims (5)
1. refrigerating plant, it comprises the refrigerant loop (110) with varying capacity helical-lobe compressor (1),
Described helical-lobe compressor (1) comprising: the screw rotor (40) of housing (10), driven rotation in housing (10), the bypass path (33) that is communicated with the suction side of this discharge chambe (23) from the compression half-way that is formed on the discharge chambe (23) between housing (10) and the screw rotor (40) and the unloading mechanism (80) with guiding valve (70) of the removable aperture of adjusting this bypass path (33) is characterized in that:
This refrigerating plant comprises: detect the inlet temperature sensor (142) that the suction pressure sensor (141) of suction pressure of discharge chambe (23) and detection are about to suck the temperature of the interior cold-producing medium of discharge chambe (23),
Described unloading mechanism (80) constitutes: when the degree of superheat that sucks cold-producing medium rises to the value that sets in advance, unloading mechanism (80) limits this guiding valve (70) towards the amount of movement of standard-sized sheet one side, make this towards the amount of movement of standard-sized sheet one side less than maximum amount of movement.
2. refrigerating plant according to claim 1 is characterized in that:
Comprise the mechanism for filling liquid (120) that liquid refrigerant is injected the suction side of described discharge chambe (23) in the described refrigerant loop (110),
Described mechanism for filling liquid (120) constitutes: when the degree of superheat that is sucking cold-producing medium rose to that working capacity is greater than desired value under the state that amount of movement that the value that sets in advance causes guiding valve (70) is subject to limit processed, this mechanism for filling liquid (120) injected the fluid injection action of liquid refrigerant.
3. refrigerating plant according to claim 2 is characterized in that:
Described helical-lobe compressor (1) comprises the suction side that is arranged on screw rotor (40) and drives the motor (15) of this screw rotor (40),
Described mechanism for filling liquid (120) constitutes: liquid refrigerant is introduced the suction side of screw rotor (40) and the upstream side of motor (15).
4. refrigerating plant according to claim 1 is characterized in that:
Described refrigerant loop (110) comprises the mechanism for filling liquid (120) that liquid refrigerant is injected the suction side of described discharge chambe (23),
Described mechanism for filling liquid (120) constitutes: when the temperature that rises to ejection cold-producing medium under the state that amount of movement that the value that sets in advance causes guiding valve (70) is subject to limit processed when the degree of superheat that is sucking cold-producing medium was higher than desired value, this mechanism for filling liquid (120) injected the fluid injection action of liquid refrigerant.
5. refrigerating plant according to claim 4 is characterized in that:
Described mechanism for filling liquid (120) constitutes: the injection rate of adjusting liquid refrigerant according to the temperature of ejection cold-producing medium.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-096298 | 2012-04-20 | ||
| JP2012096298A JP5831345B2 (en) | 2012-04-20 | 2012-04-20 | Refrigeration equipment |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203203286U true CN203203286U (en) | 2013-09-18 |
Family
ID=49147388
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320189441 Expired - Lifetime CN203203286U (en) | 2012-04-20 | 2013-04-16 | Refrigerating plant |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP5831345B2 (en) |
| CN (1) | CN203203286U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112710098A (en) * | 2021-01-17 | 2021-04-27 | 北京工业大学 | Air supplementing device and method for single-screw refrigeration compressor coupled with composite slide valve under partial load |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6942265B2 (en) * | 2018-09-14 | 2021-09-29 | 三菱電機株式会社 | Heat source equipment and refrigeration cycle equipment |
| CN115355659A (en) * | 2022-07-19 | 2022-11-18 | 凌腾金属材料制品(苏州)有限公司 | Preparation cooling arrangement that electronic product material was used |
-
2012
- 2012-04-20 JP JP2012096298A patent/JP5831345B2/en active Active
-
2013
- 2013-04-16 CN CN 201320189441 patent/CN203203286U/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112710098A (en) * | 2021-01-17 | 2021-04-27 | 北京工业大学 | Air supplementing device and method for single-screw refrigeration compressor coupled with composite slide valve under partial load |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013224757A (en) | 2013-10-31 |
| JP5831345B2 (en) | 2015-12-09 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20130918 |