CN102348942A

CN102348942A - Heat pump system

Info

Publication number: CN102348942A
Application number: CN201080012689XA
Authority: CN
Inventors: 山田拓郎; 奥田则之; 藤本修二; 吉见敦史
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2009-03-13
Filing date: 2010-03-10
Publication date: 2012-02-08
Also published as: WO2010103825A1; JP2010216685A; EP2407734A1; US20120000237A1

Abstract

A heat pump system having increased cycle efficiency in processing of a heat load by a secondary refrigerant. A heat pump circuit (10) in which a carbon dioxide refrigerant circulates has a low-stage compressor (21), a high-stage compressor (25), an expansion valve (5), and an evaporator (4). A heating circuit (60) in which water as a secondary refrigerant circulates has a radiator (61). The heating circuit in which the water as the heat medium for heating circulates has a intermediate-pressure branch path (67) and a high-pressure branch path (68) which are arranged parallel to each other. A control section (11) operates a mixing valve (64) for heating so that the temperature of the secondary refrigerant in a portion of the intermediate-pressure branch path (67), said portion being heated by an intermediate-pressure water heat exchanger (40), and the temperature of the secondary refrigerant in a portion of the high-pressure branch path (68), said portion being heated by a second high-pressure water heat exchanger (52), are the same.

Description

Heat pump

Technical field

The present invention relates to a kind of heat pump.

Background technology

Past, known have a kind ofly utilize the heat pump cycle that supplies the primary coolant circulation to circulate to heat the system of running with the secondary side that supplies the secondary refrigerant circulation.

For example; In the heat pump type air conditioner that patent documentation 1 (Japanese Patent Laid is opened the 2004-177067 communique) is put down in writing; Primary coolant through making on high-tension side primary coolant and low-pressure side carries out heat exchange; And the heat of utilizing the primary coolant of the low-pressure side after being heated comes assistant heating to heat the secondary refrigerant of usefulness, thus the raising of implementation efficiency.

Summary of the invention

Invent technical problem to be solved

In the heat pump type air conditioner that above-mentioned patent documentation 1 (Japanese Patent Laid is opened the 2004-177067 communique) is put down in writing,, make that therefore needed driving force increases in the compressing mechanism because imagination has only the single stage compress form of a compressing mechanism.

Technical problem of the present invention is to provide a kind of heat pump that can in the heat load of carrying out through secondary refrigerant is handled, cycle efficieny improved.

The technical scheme that the technical solution problem is adopted

The heat pump of first invention comprises heat pump circuit, the first heat load loop, first heat exchanger, second heat exchanger, first flow governor motion and control part.Heat pump circuit has rudimentary side pressure contract mechanism, senior side pressure contract mechanism, expansion mechanism and evaporimeter at least.Above-mentioned heat pump circuit supplies the primary coolant circulation.The first heat load loop has the first fork part, the second fork part, the first fork stream, the second fork stream and the first heat load handling part.The first fork stream is connected the first fork part with the second fork part.The second fork stream not with the first fork passage confluent, it is connected the first fork part and the second fork part.The above-mentioned first heat load loop supplies the first fluid circulation.First heat exchanger makes from the contract discharge side of mechanism of rudimentary side pressure and carries out heat exchange each other towards the contract suction side primary coolant that flows and the first fluid that the first fork stream, flows of mechanism of senior side pressure.Second heat exchanger makes from the senior side pressure mechanism of contracting and carries out heat exchange each other towards primary coolant that expansion mechanism flows and the first fluid that the second fork stream, flows.The first flow governor motion can be regulated any at least side's in the flow of flow and the first fluid in the second fork stream of the first fluid of first fork in the stream flow.Control part is operated the Flow-rate adjustment control of first flow governor motion.In above-mentioned Flow-rate adjustment control; Operation first flow governor motion; Thereby can: keep the state that satisfies the set point of temperature condition; Wherein, the afore mentioned rules temperature conditions comprises that the ratio of the temperature of the first fluid that in through the part of second heat exchanger, flows in temperature and the second fork stream of the first fluid that in through the part of first heat exchanger, flows in the first fork stream is 1 situation; Or in the temperature that makes the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream in through the part of second heat exchanger difference of the temperature of mobile first fluid diminish.In addition, contract the mechanism except contract mechanism and rudimentary side pressure of senior side pressure, can also comprise compressing mechanism, the situation of multi-stag compressibility certainly within the scope of the present invention.

In above-mentioned heat pump; Under the identical situation of the heat of the secondary refrigerant that is supplied to the first heat load handling part, can make heated first fluid in first heat exchanger temperature and environment temperature difference and in second heat exchanger any one in the difference of temperature and the environment temperature of heated first fluid can not become big.Therefore, can will be in first heat exchanger heated first fluid arrives the heat release loss of emitting before the first heat load handling part and heated first fluid arrives the heat release loss of emitting before the first heat load handling part in second heat exchanger total suppress lessly.By this, heat pump is improved to the treatment effeciency of the heat load in first load heat exchanger.

The heat pump of second invention is on the basis of the heat pump of first invention; Control part is controlled rudimentary side pressure the contract output of mechanism of mechanism and senior side pressure of contracting; Thereby can make the temperature above temperature of the temperature of the primary coolant that flows into first heat exchanger for the first fluid of inflow first heat exchanger; The temperature that makes the primary coolant that flows into second heat exchanger is the above temperature of temperature of the first fluid that flows into second heat exchanger, and make the temperature of the primary coolant that flows into first heat exchanger and flow into second heat exchanger primary coolant temperature both be the temperature more than the desired first heat load corresponding temperature in the first heat load handling part.

In above-mentioned heat pump, can under the situation of the temperature that does not reduce the first fluid that flows into first heat exchanger, utilize the primary coolant that flows into first heat exchanger to improve the temperature of first fluid reliably.In addition, can prevent that the contract discharging refrigerant temperature anomaly of mechanism of senior side pressure from rising.Likewise, can under the situation of the temperature that does not reduce the first fluid that flows into second heat exchanger, utilize the primary coolant that flows into second heat exchanger to improve the temperature of first fluid reliably.In addition, the heat that only utilizes first fluid in first heat exchanger and second heat exchanger, to obtain just can be corresponding with the heat load in first load heat exchanger.

The heat pump of the 3rd invention is on the basis of the heat pump of second invention; The first heat load loop also has: the part between the first heat load bypass circulation, this first heat load bypass circulation divide the first heat load handling part and first branched portion is connected with part between the first heat load handling part and second branched portion divide; And the first heat load bypass flow governor motion, this first heat load bypass flow governor motion can be regulated the flow through the first fluid of the first heat load bypass circulation.In Flow-rate adjustment control; Control part is controlled, so that the desired value of the temperature of the first fluid that in through the part of second heat exchanger, flows in the desired value of the temperature of the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream is for surpassing the temperature of the first heat load corresponding temperature.Control part is operated the first heat load bypass flow governor motion and is regulated the flow through the first fluid of the first heat load bypass circulation, is the first heat load corresponding temperature so that be supplied to the temperature of the first fluid of the first heat load handling part.

In above-mentioned heat pump; Even the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature of the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream is the operational situation of the temperature that surpasses the first heat load corresponding temperature that in the first heat load handling part, needs; Also can regulate the flow through the first fluid of the first heat load bypass circulation, the temperature of regulating the first fluid that is supplied to the first heat load handling part through utilizing the first heat load bypass flow governor motion.By this; Even the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature of the first fluid that causes for the efficient that improves heat pump circuit in through the part of first heat exchanger, flowing in the first fork stream and the second fork stream surpasses the first heat load corresponding temperature, also can make the temperature of the first fluid that is supplied to the first heat load handling part approach the first load corresponding temperature.

The heat pump of the 4th invention is on the basis of the heat pump of second invention; In Flow-rate adjustment control; Control part is controlled, so that the desired value of the temperature of the first fluid that in through the part of second heat exchanger, flows in the desired value of the temperature of the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream is the first heat load corresponding temperature.

In above-mentioned heat pump, the temperature that is controlled to the first fluid that in through the part of second heat exchanger, flows in temperature and the second fork stream of the first fluid that in through the part of first heat exchanger, flows in the first fork stream all approaches the first heat load corresponding temperature that in the first heat load handling part, needs.By this, the temperature of the first fluid that can avoid in the first heat load loop flowing surpasses the more state of the first heat load corresponding temperature, thereby can reduce the heat release loss effectively.

In addition, be that target is controlled under the situation of first flow governor motion with the first heat load corresponding temperature, the first heat load loop can not need have the function that the temperature of the first fluid that flows towards the first heat load handling part is regulated.

The heat pump of the 5th invention is on the basis of the heat pump of arbitrary invention in second invention to the 4th invention; In Flow-rate adjustment control; Control part to rudimentary side pressure contract mechanism, senior side pressure contract in mechanism and the expansion mechanism any one is controlled at least; Thereby can: keep the state that satisfies regulation compression ratio condition; Wherein, regulation compression ratio condition comprises that rudimentary side pressure the contract ratio of the compression ratio in the mechanism of compression ratio and senior side pressure in the mechanism that contracts is 1 situation; Or rudimentary side pressure the contract difference of the compression ratio in the mechanism of compression ratio and senior side pressure in the mechanism that contracts is diminished.

In above-mentioned heat pump; When carrying out Flow-rate adjustment control; Be the temperature more than the temperature of the first fluid of inflow first heat exchanger so that flow into the temperature of the primary coolant of first heat exchanger; The temperature that flows into the primary coolant of second heat exchanger is the temperature more than the temperature of the first fluid of inflow second heat exchanger; And make the temperature of the primary coolant that flows into first heat exchanger and flow into second heat exchanger primary coolant temperature both when being the above temperature of the first heat load corresponding temperature, senior side pressure can be contracted mechanism and rudimentary side pressure are contracted, and required driven compressor power suppresses lessly in the mechanism.By this, the heat release loss of first fluid is reduced, can also realize utilizing less driving force corresponding simultaneously, thereby can further raise the efficiency with the heat load in the first heat load handling part.

The heat pump of the 6th invention is on the basis of the heat pump of the 5th invention; Under the situation of carrying out Flow-rate adjustment control; Contract the discharge temperature of primary coolant of mechanism when raising in rudimentary side pressure, the rudimentary suction degree of superheat control that the degree of superheat of control part rudimentary side pressure the is contracted primary coolant that mechanism sucks increases.

In general, under the desired value condition with higher of discharge temperature of primary coolant of mechanism is contracted in rudimentary side pressure, there is the contract compression ratio of mechanism of rudimentary side pressure also can become big tendency.In addition, by this, the contract compression ratio of mechanism of senior side pressure also can become big.Therefore, the required driving force of compressing mechanism is increased, thereby make consumed energy increase.

To this, in above-mentioned heat pump, under the situation that the desired value of discharge temperature of primary coolant of mechanism rises is contracted in rudimentary side pressure, the rudimentary suction degree of superheat control that the desired value of the degree of superheat of rudimentary side pressure the is contracted primary coolant that mechanism sucks increases.Therefore, can suppress lessly for the contract compression ratio of mechanism of rudimentary side pressure is contracted rudimentary side pressure that the discharge temperature of primary coolant of mechanism reaches desired value and need.Thereupon, also the compression ratio of senior side compressor can be suppressed less.Thereby, can suppress the required driving force of compressing mechanism littler.On the other hand; Under the lower situation of the desired value of discharge temperature of primary coolant of mechanism is contracted in rudimentary side pressure; Through reducing the contract degree of superheat of the primary coolant that mechanism sucks of rudimentary side pressure; Can not only suppress the contract increase of compression ratio of mechanism of senior side pressure through suppressing the contract increase of compression ratio of mechanism of rudimentary side pressure, can also reduce the contract specific volume of the primary coolant that mechanism sucks of rudimentary side pressure.By this, when suppressing the compression ratio increase, can also guarantee internal circulating load, thereby ability is increased.

The heat pump of the 7th invention is on the basis of the heat pump of the 6th invention; Heat pump circuit also has heat exchanger between primary coolant, between this primary coolant heat exchanger rudimentary side pressure is contracted primary coolant that mechanism sucks with through second heat exchanger after, carry out heat exchange each other towards the mobile primary coolant of expansion mechanism.Heat exchanger carries out rudimentary suction degree of superheat control between control part use primary coolant.

In above-mentioned heat pump, the hotwork that can will be used for the primary coolant that flows into before the expansion mechanism be cooled off is that the heat that the degree of superheat of the primary coolant that mechanism sucks that is used to make rudimentary side pressure to contract increases reclaims.By this, can not only increase the contract degree of superheat of the primary coolant that mechanism sucks of rudimentary side pressure, the primary coolant in can also repression of swelling mechanism through excessive reduction, thereby ability is improved.

The heat pump of the 8th invention is on the basis of the heat pump of arbitrary invention in the 5th invention to the 7th invention; Under the situation of carrying out Flow-rate adjustment control; When the temperature of the first fluid that flows towards first heat exchanger and second heat exchanger from the first heat load handling part rises; Control part carries out controlling when load reduces; In when this load reduces, controlling; The contract desired value of discharge temperature of primary coolant of mechanism of rudimentary side pressure is reduced, and reduce the contract degree of superheat of the primary coolant that mechanism sucks of rudimentary side pressure.

In above-mentioned heat pump; When the temperature of the first fluid that flows towards first heat exchanger and second heat exchanger from the first heat load loop rises; Owing to be the situation that the heat load in the first heat load handling part diminishes; Therefore; Even be varied to above-mentioned operating condition efficiently, also can be corresponding with load.And, can increase the rudimentary side pressure density of the primary coolant that mechanism sucks that contracts, and the internal circulating load of primary coolant is increased.By this, can the ability of heat pump circuit be increased with when load change is corresponding.

The heat pump of the 9th invention is on the basis of the heat pump of the 8th invention, also comprises: the second heat load loop, this second heat load loop supply the circulation of second fluid, and it has the second heat load portion; And the 3rd heat exchanger, the 3rd heat exchanger makes second fluid that in the second heat load loop, circulates and the primary coolant of mechanism towards second heat exchanger flows the way that contract from senior side pressure carry out heat exchange each other.

In above-mentioned heat pump; The heat load that the heat of the primary coolant that mechanism discharges of senior side pressure can not only being contracted is used for the first heat load loop handle with the second heat load loop in heat load processing in the two, can also be in the second heat load loop with the heat utilization outside the temperature range required in the first heat load loop.

The heat pump of the tenth invention is on the basis of the heat pump of the 9th invention; Also comprise the 4th heat exchanger, the 4th heat exchanger make through in second fluid in the second heat load loop from the second heat load handling part towards second fluid that the 3rd heat exchanger flows with through second heat exchanger after primary coolant towards expansion mechanism flows on the way carry out heat exchange each other.

In above-mentioned heat pump; When the range of temperature of the first fluid in the first heat load handling part is included in the range of temperature of second fluid in the second heat load handling part; In the primary coolant that mechanism discharges is contracted in senior side pressure; The primary coolant that can will be in the primary coolant of the condition of high temperature and be in low-temperature condition is distributed into second fluid and carries out heat exchange, and the primary coolant of temperature state is used for the heat exchange with first fluid in will being in.By this, carry out the heat exchange in second heat exchanger, the 3rd heat exchanger and the 4th heat exchanger under the situation that can suppress lessly, therefore, can improve heat exchanger effectiveness in temperature difference with first fluid and second fluid and primary coolant.

The heat pump of the 11 invention is on the basis of the heat pump of the 9th invention or the tenth invention; Contract than senior side pressure under the low situation of the desired value of temperature of the primary coolant that mechanism discharges in the contract desired value of temperature of the primary coolant that mechanism discharges of rudimentary side pressure; Control part is regulated the internal circulating load of second fluid that in the second heat load loop, circulates, so that approach the contract desired value of temperature of the primary coolant that mechanism discharges of rudimentary side pressure through the temperature of the primary coolant of the 3rd heat exchanger.

In above-mentioned heat pump; Maximum temperature through making in first heat exchanger primary coolant that flows is approaching with the maximum temperature of the primary coolant that in second heat exchanger, flows, thus in the temperature that makes the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream in through the part of second heat exchanger temperature of mobile first fluid approaching.

In addition; For example; Under the situation that will suppress lessly to the flow of the first fluid that the first heat load handling part is supplied with; Even first fluid through time of first heat exchanger or elongated through the time of second heat exchanger, also can make the temperature of the primary coolant that in first heat exchanger, flows approaching with the temperature of the primary coolant that in second heat exchanger, flows.Therefore; For any one temperature in the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature of the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream, all can converge near the value the temperature (temperature of the primary coolant that in second heat exchanger, flows) of the primary coolant that in above-mentioned first heat exchanger, flows.

The heat pump of the 12 invention is that the second heat load handling part is the case that heat supply water is used on the basis of the heat pump of arbitrary invention in the 9th invention to the 11 invention.Second fluid is the water that heat supply water is used.

In above-mentioned heat pump, can utilize from the contract temperature of the primary coolant that mechanism discharges of senior side pressure and come the manufacture hot water.

The heat pump of the 13 invention is on the basis of the heat pump of arbitrary invention in second invention to the 12 invention; In Flow-rate adjustment control; Control part is through operation first flow governor motion, makes that side's that temperature is lower among the temperature of the first fluid that in through the part of second heat exchanger, flows in temperature and the second fork stream of the first fluid that in through the part of first heat exchanger, flows in the first fork stream flow decline.

In above-mentioned heat pump; That side's that temperature is lower among the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature through reducing the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream flow can make that lower side of temperature flow velocity reduce and make heated time growth.By this, the recuperation of heat amount of the primary coolant recovery that from first heat exchanger and second heat exchanger, reduces flow one side is increased.

In addition, for example, in the inlet temperature that is not heated to primary coolant, but with under the situation of flow velocity through first heat exchanger or second heat exchanger faster, increase, the recuperation of heat amount is increased through reducing the time that enables to carry out heat exchange through speed.

The heat pump of the 14 invention is on the basis of the heat pump of the 13 invention, and the first flow governor motion can be adjusted in the flow of the first fluid that flows in the first fork stream and the ratio of the flow of the first fluid that in the second fork stream, flows.In Flow-rate adjustment control; Control part is through operation first flow governor motion; Make the flow of the first fluid that is supplied to the first heat load handling part keep fixing, and make that side's that temperature is lower among the temperature of the first fluid that in through the part of second heat exchanger, flows in temperature and the second fork stream of the first fluid that in through the part of first heat exchanger, flows in the first fork stream flow rate ratio decline.

In above-mentioned heat pump; Through regulating flow rate ratio; That higher side of temperature in the temperature of the first fluid that in through the part of second heat exchanger, flows in temperature and the second fork stream of the first fluid that in through the part of first heat exchanger, flows in the first fork stream flow velocity is increased and shortened heat time heating time, and make that lower side of temperature flow velocity reduction and make growth heat time heating time.By this, in the temperature that can make the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream in through the part of second heat exchanger temperature of mobile first fluid so that the mode that temperature difference diminishes change.In addition, when the heat load of the first heat load handling part does not change, temperature difference is diminished, can also be corresponding with the heat load in the first heat load handling part through the flow of keeping the first fluid that is supplied to the first heat load handling part.

The heat pump of the 15 invention is that the first flow governor motion can be regulated the flow of the above-mentioned first fluid that is supplied to the first heat load handling part on the basis of the heat pump of the 13 invention.In Flow-rate adjustment control; That side's that temperature is lower among the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature of the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream flow rate ratio hour, control part is through operating the flow that the first flow governor motion reduces the first fluid that is supplied to the first heat load handling part.

In above-mentioned heat pump; If under the less situation of that side's that temperature is lower among the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature of the first fluid that in the first fork stream, in through the part of first heat exchanger, flows and the second fork stream flow rate ratio; Reduce the flow of the first fluid that is supplied to the first heat load handling part; Then compare with higher that side's of temperature temperature ascending amount, that side's that temperature is lower temperature ascending amount is bigger.By this, can so that the mode that temperature difference diminishes change.In addition, under the situation that the heat load in the first heat load handling part reduces, can not only reduce temperature difference, can also make it corresponding with the heat load in the first heat load handling part.

The heat pump of the 16 invention is on the basis of the heat pump of the 13 invention; The first flow governor motion comprises: rate regulation portion, this rate regulation portion are adjusted in the flow of the first fluid that flows in the first fork stream and the ratio of the flow of the first fluid that in the second fork stream, flows; And flow control division, this flow control division is regulated the flow of the first fluid that is supplied to the first heat load handling part.In Flow-rate adjustment control; Control part is by operation first flow governor motion; Make the flow increase that surpasses that side of the first heat load corresponding temperature among the temperature of the first fluid that in through the part of second heat exchanger, flows in temperature and the second fork stream of the first fluid that in through the part of first heat exchanger, flows in the first fork stream; And/or that side's of the less than first heat load corresponding temperature flow is reduced; And; Temperature at the first fluid that is supplied to the first heat load handling part surpasses under the situation of the first heat load corresponding temperature, and control part makes the flow of the first fluid that is supplied to the first heat load handling part descend along with the rising of the temperature of the first fluid that is supplied to the first heat load handling part.

In above-mentioned heat pump; The difference of the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature that can not only make the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream diminishes, can also make the flow of first fluid mobile in the first heat load loop become with the first heat load handling part in the corresponding amount of heat load.

The heat pump of the 17 invention is on the basis of the heat pump of arbitrary invention in first invention to the 16 invention; Also comprise: the first fork stream detector unit, this first fork stream detector unit is held the temperature of the first fluid that in through the part of first heat exchanger, flows in the first fork stream; And the second fork stream detector unit, this second fork stream detector unit is held the temperature of the first fluid that in through the part of second heat exchanger, flows in second fork stream.

In above-mentioned heat pump; Owing to the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature that can directly hold the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream, so the precision of Flow-rate adjustment control is improved.

The heat pump of the 18 invention is on the basis of the heat pump of arbitrary invention in first invention to the 16 invention, comprises fork part detector unit and interflow portion detector unit.Any at least side in the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature of the first fluid that in through the part of first heat exchanger, flows in the fork part detector unit assurance first fork stream and the second fork stream.Interflow portion temperature detecting element is being held in through the first fluid of the first fork stream and temperature through the first fluid that flows towards the first heat load handling part after the first fluid interflow of the second fork stream.

In above-mentioned heat pump; Can utilize fork part detector unit directly to hold in temperature and the second fork stream of the first fluid that in through the part of first heat exchanger, flows in the first fork stream any side in the temperature of mobile first fluid in through the part of second heat exchanger, and can utilize and collaborate the temperature that the portion temperature detecting element is directly held the first fluid behind the interflow.By this, the difference of the temperature that temperature that fork part detector unit held and interflow portion temperature detecting element held is diminished, the precision of Flow-rate adjustment control is improved through being controlled to.

The heat pump of the 19 invention is on the basis of the heat pump of arbitrary invention in first invention to the 16 invention; Also comprise: the first fork stream flow detecting element, this first fork stream flow detecting element is the flow that is held in the first fluid that flows in the first fork stream; And the second fork stream flow detecting element, this second fork stream flow detecting element is the flow that is held in the first fluid that flows in the second fork stream.

In above-mentioned heat pump,, therefore can make the precision raising of Flow-rate adjustment control owing to can directly reach the flow that is held in the first fluid that flows in the first fork stream flow of the first fluid that in the second fork stream, flows.

The heat pump of the 20 invention is on the basis of the heat pump of arbitrary invention in first invention to the 16 invention; Also comprise: branched portion shunt volume detecting element, this branched portion shunt volume detecting element is any at least side in the flow of flow that is held in the first fluid that flows in the first fork stream and the first fluid that in the second fork stream, flows; And interflow partial discharge detecting element, this interflow partial discharge detecting element is the flow that is held in after first fluid that flows in the first fork stream and the first fluid interflow of in the second fork stream, flowing towards the mobile first fluid of the first heat load handling part.

In above-mentioned heat pump; Can utilize branched portion shunt volume detecting element directly any side in the flow of flow that is held in the first fluid that flows in the first fork stream and the first fluid that in the second fork stream, flows, and can utilize and collaborate the flow that the partial discharge detecting element is directly held the first fluid behind the interflow.By this, the difference of the flow held of the flow that can be held with branched portion shunt volume detecting element and interflow partial discharge detecting element hold will the first fork stream and the second fork stream in the flow of branched portion shunt volume detecting element one side is not set.By this, the precision of Flow-rate adjustment control is improved.

The heat pump of the 21 invention is on the basis of the heat pump of arbitrary invention in first invention to the 20 invention; In first heat exchanger, be in flow relation towards the contract suction side primary coolant that flows and the first fluid that the first fork stream, flows of mechanism of senior side pressure from the contract discharge side of mechanism of rudimentary side pressure.In second heat exchanger, be in flow relation towards primary coolant that expansion mechanism flows and the first fluid that the second fork stream, flows from the senior side pressure mechanism of contracting.

In above-mentioned heat pump, the temperature of the primary coolant that can discharge as the mechanism of contracting from rudimentary side pressure and suppress lowlyer from the contract needed temperature of temperature of the primary coolant that mechanism discharges of senior side pressure.By this, the driving force of compressing mechanism can be suppressed less.

The heat pump of the 22 invention is on the basis of heat pump of arbitrary invention in first invention to the 21 invention, and the first heat load handling part is that heating of heating of the air to the object space that disposes this first heat load handling part used heat exchanger.First fluid is a secondary refrigerant.

In above-mentioned heat pump, can heat the space that disposes the first heat load handling part.

The heat pump of the 23 invention is on the basis of heat pump of arbitrary invention in first invention to the 22 invention, and rudimentary side pressure mechanism and the senior side pressure mechanism of contracting of contracting has and is used for through driving rudimentary side pressure mechanism and the senior side pressure shared rotating shaft that each spinning of mechanism produces work done during compression of contracting of contracting.

In above-mentioned heat pump, through make rotating shaft shared and be provided with 180 the degree phase differences, can improve the driving efficient.

The heat pump of the 24 invention is on the basis of the heat pump of arbitrary invention in first invention to the 23 invention; In Flow-rate adjustment control, control part is maintained the pressure more than the critical pressure of primary coolant with the contract discharge pressure of mechanism of senior side pressure.Heat pump is to use under the environment of the temperature below the critical-temperature of primary coolant in the environment temperature of the first heat load handling part.

In above-mentioned heat pump; Be in primary coolant through the heat load of the critical-temperature that is lower than primary coolant is supplied with, carry out heat release in the zone that the isothermal inclination of primary coolant that can be on mollier diagram eases up and handle above the state of critical pressure.Therefore, the running that the exothermic process of the primary coolant enthalpy difference between beginning and finishing is increased.

On the basis of the heat pump of the 25 invention heat pump of arbitrary invention in first invention to the 24 invention, primary coolant is a carbon dioxide.

In above-mentioned heat pump, can use the nature cold-producing medium to realize the kind of refrigeration cycle of heat pump circuit.

The invention effect

As stated, according to the present invention, can obtain following effect.

In first invention, heat pump is improved to the treatment effeciency of the heat load in first load heat exchanger.

In second invention, the heat that only utilizes first fluid in first heat exchanger and second heat exchanger, to obtain just can be corresponding with the heat load in first load heat exchanger.

In the 3rd invention; Even the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature of the first fluid that causes for the efficient that improves heat pump circuit in through the part of first heat exchanger, flowing in the first fork stream and the second fork stream surpasses the first heat load corresponding temperature, also can make the temperature of the first fluid that is supplied to the first heat load handling part approach the first load corresponding temperature.

In the 4th invention, the temperature of the first fluid that can avoid in the first heat load loop flowing surpasses the more state of the first heat load corresponding temperature, thereby can reduce the heat release loss effectively.

In the 5th invention, the heat release loss of first fluid is reduced, can also realize utilizing less driving force corresponding simultaneously, thereby can further raise the efficiency with the heat load in the first heat load handling part.

In the 6th invention, when suppressing the compression ratio increase, can also guarantee internal circulating load, thereby ability is increased.

In the 7th invention, can not only increase the contract degree of superheat of the primary coolant that mechanism sucks of rudimentary side pressure, the primary coolant in can also repression of swelling mechanism through excessive reduction, thereby ability is improved.

In the 8th invention, can make the ability increase of heat pump circuit with when load change is corresponding.

In the 9th invention; The heat load that the heat of the primary coolant that mechanism discharges of senior side pressure can not only being contracted is used for the first heat load loop handle with the second heat load loop in heat load processing in the two, can also be in the second heat load loop with the heat utilization outside the temperature range required in the first heat load loop.

In the tenth invention, carry out the heat exchange in second heat exchanger, the 3rd heat exchanger and the 4th heat exchanger under the situation that can suppress lessly in temperature difference with first fluid and second fluid and primary coolant, therefore, can improve heat exchanger effectiveness.

In the 11 invention, in the temperature that makes the first fluid that in through the part of first heat exchanger, flows in the first fork stream easily and the second fork stream in through the part of second heat exchanger temperature of mobile first fluid approaching.

In the 12 invention, can utilize from the contract temperature of primary coolant of mechanism discharge of senior side pressure and come the manufacture hot water.

In the 13 invention, the recuperation of heat amount of the primary coolant recovery that from first heat exchanger and second heat exchanger, reduces flow one side is increased.

In the 14 invention; In the temperature that can make the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream in through the part of second heat exchanger temperature of mobile first fluid so that the mode that temperature difference diminishes change; When the heat load in the first heat load handling part does not change; Can not only reduce temperature difference, can also make it corresponding through the flow of keeping the first fluid that is supplied to the first heat load handling part with the heat load in the first heat load handling part.

The 15 the invention in, can so that the mode that temperature difference diminishes change.In addition, under the situation that heat load reduces in the first heat load handling part, can not only reduce temperature difference, can also make it corresponding with the heat load in the first heat load handling part.

In the 16 invention; The difference of the temperature of the first fluid that in through the part of second heat exchanger, flows in the temperature that can not only make the first fluid that in through the part of first heat exchanger, flows in the first fork stream and the second fork stream diminishes, can also make the flow of first fluid mobile in the first heat load loop become with the first heat load handling part in the corresponding amount of heat load.

In the 17 invention, the precision of Flow-rate adjustment control is improved.

In the 18 invention, through being controlled to the difference of the temperature that temperature that fork part detector unit held and interflow portion temperature detecting element held is diminished, the precision of Flow-rate adjustment control is improved.

In the 19 invention, the precision of Flow-rate adjustment control is improved.

In the 20 invention, the precision of Flow-rate adjustment control is improved.

In the 21 invention, the driving force of compressing mechanism can be suppressed less.

In the 22 invention, can heat the space that disposes the first heat load handling part.

The 23 the invention in, through make rotating shaft shared and be provided with 180 the degree phase differences, can improve the driving efficient.

In the 24 invention, can make the running of the exothermic process of the primary coolant enthalpy difference increase between beginning and finishing.

In the 25 invention, can use the nature cold-producing medium to realize the kind of refrigeration cycle of heat pump circuit.

Description of drawings

Fig. 1 is the schematic configuration diagram of the heat pump of first embodiment of the invention.

Fig. 2 is the pressure-enthalpy line chart of the heat pump circuit of first embodiment.

Fig. 3 is the temperature-entropy line chart of the heat pump circuit of first embodiment.

Fig. 4 is the schematic configuration diagram of the heat pump of second embodiment.

Fig. 5 is the schematic configuration diagram of the heat pump of the 3rd embodiment.

Fig. 6 is the schematic configuration diagram of the heat pump of the 4th embodiment.

Fig. 7 is the schematic configuration diagram of the heat pump of the 5th embodiment.

Fig. 8 is the schematic configuration diagram of heat pump of the variation A of the 5th embodiment.

Fig. 9 is the schematic configuration diagram of heat pump of the variation B of the 5th embodiment.

Figure 10 is the schematic configuration diagram of heat pump of the variation C of the 5th embodiment.

Figure 11 is the schematic configuration diagram of the heat pump of the 6th embodiment.

Figure 12 is the schematic configuration diagram of heat pump of the variation A of the 6th embodiment.

Figure 13 is the schematic configuration diagram of the heat pump of the 7th embodiment.

Figure 14 is the schematic configuration diagram of the heat pump of the 8th embodiment.

Figure 15 is the schematic configuration diagram of the heat pump of the 9th embodiment.

Figure 16 is the schematic configuration diagram of the heat pump of the tenth embodiment.

Figure 17 is the schematic configuration diagram of the heat pump of the 11 embodiment.

Figure 18 is the schematic configuration diagram of the heat pump of the 12 embodiment.

Figure 19 is the schematic configuration diagram of the heat pump of the 13 embodiment.

Figure 20 is the schematic configuration diagram of heat pump of the variation < 14-5>of each embodiment.

Figure 21 is the schematic configuration diagram of heat pump of the variation < 14-5>of each embodiment.

Figure 22 is the figure of mollier diagram of the variation < 14-8>of each embodiment of expression.

Figure 23 is the figure of mollier diagram of the variation < 14-9>of each embodiment of expression.

Figure 24 is the schematic configuration diagram of heat pump of the variation < 14-11>of each embodiment.

Figure 25 is the schematic configuration diagram of heat pump of the variation < 14-12>of each embodiment.

Figure 26 is the schematic configuration diagram of heat pump of the variation < 14-13>of each embodiment.

Figure 27 is the figure of expression about the comparative example of the mollier diagram of the variation < 14-17>of each embodiment.

Figure 28 is the figure of mollier diagram of the variation < 14-17>of each embodiment of expression.

Figure 29 is the figure of mollier diagram of the variation < 14-18>of each embodiment of expression.

The specific embodiment

< 1>first embodiment

The structure of < 1-1>heat pump 1

Fig. 1 is the schematic configuration diagram as the heat pump 1 of first embodiment of an embodiment of the present invention.

Heat pump 1 comprises heat pump circuit 10, heating loop 60, heat supply water loop 90, middle setting-out heat exchanger 40 and water under high pressure heat exchanger 50.Heat pump 1 be the heat that not only will obtain by heat pump circuit 10 via heating loop 60 as the heat that heats usefulness, the system of the heat used as heat supply water via heat supply water loop 90 of the heat that will obtain by heat pump circuit 10 also.

(middle setting-out heat exchanger 40)

In middle setting-out heat exchanger 40, circulation carries out heat exchange each other as the carbon dioxide of primary coolant and the water as secondary refrigerant that in heating loop 60, circulates in heat pump circuit 10.

(water under high pressure heat exchanger 50)

Water under high pressure heat exchanger 50 has the first water under high pressure heat exchanger 51, the second water under high pressure heat exchanger 52 and the 3rd water under high pressure heat exchanger 53.In the first water under high pressure heat exchanger 51, the water of using as the carbon dioxide of primary coolant and the heat supply water of circulation in heat supply water loop 90 of circulation carries out heat exchange each other in heat pump circuit 10.In the second water under high pressure heat exchanger 52, circulation carries out heat exchange each other as the carbon dioxide of primary coolant and the water as secondary refrigerant that in heating loop 60, circulates in heat pump circuit 10.In the 3rd water under high pressure heat exchanger 53, the water of using as the carbon dioxide of primary coolant and the heat supply water of circulation in heat supply water loop 90 of circulation carries out heat exchange each other in heat pump circuit 10.

(heat pump circuit 10)

Heat pump circuit 10 is the loops that make as the use nature cold-producing medium of the carbon dioxide of primary coolant circulation.Heat pump circuit 10 comprises rudimentary side compressor 21, senior side compressor 25, economizer heat exchanger 7, inject between stream 70, primary coolant heat exchanger 8, bypass pipe 80, expansion valve 5a, evaporimeter 4, pressure pipe 23, high-voltage tube 27, low-voltage tube 20, fan 4f and a control part 11.Evaporimeter 4 for example is arranged on outdoor.

The middle pipe 23 discharge sides with rudimentary side compressor 21 of pressing are connected with the suction side of senior side compressor 25.In press pipe 23 to comprise to press in first to press among the pipe 23a, second to press among the pipe 23b, the 3rd and press pipe 23d among the pipe 23c and the 4th.

Press pipe 23a the discharge side of rudimentary side compressor 21 to be connected with the upstream-side-end of middle setting-out heat exchanger 40 in first through rudimentary discharge point B.Press in first at this middle pressure temperature sensor 23T that temperature to the primary coolant of process detects is installed on the pipe 23a.Press in second pipe 23b make as the carbon dioxide of primary coolant within it portion flow so that do not mix with the water that heats usefulness as secondary refrigerant as the carbon dioxide of primary coolant, and in passing through in the setting-out heat exchanger 40.Press pipe 23c through some C the end of downstream side of middle setting-out heat exchanger 40 to be connected with injection junction of two streams D in the 3rd through middle setting-out heat exchanger.Pressing pipe 23d will inject junction of two streams D in the 4th is connected with the suction side of senior side compressor 25.In the 4th, press the senior inlet temperature sensor 24T that senior suction pressure sensor 24P that the pressure to the primary coolant of process detects is installed on the pipe 23d and the temperature of the primary coolant of process is detected.

High-voltage tube 27 is connected the discharge side of senior side compressor 25 with expansion valve 5 or a bypass expansion valve 5b.High-voltage tube 27 has the first high-voltage tube 27a, the second high-voltage tube 27b, the 3rd high-voltage tube 27c, the 4th high-voltage tube 27d, the 5th high-voltage tube 27e, the 6th high-voltage tube 27f, the 7th high-voltage tube 27g, the 8th high-voltage tube 27h, the 9th high-voltage tube 27i, the tenth high-voltage tube 27j, the 11 high-voltage tube 27k, the 12 high-voltage tube 27l and the 13 high-voltage tube 27m.

The first high-voltage tube 27a is connected the discharge side of senior side compressor 25 through senior discharge point E with the first water under high pressure heat exchanger 51.The high pressure temperature sensor 27T that high-pressure sensor 27P that pressure to the primary coolant of process detects is installed on this first high-voltage tube 27a and the temperature of the primary coolant of process is detected.The second high-voltage tube 27b make as the carbon dioxide of primary coolant within it portion flow so that do not mix with the water that heat supply water is used as the carbon dioxide of primary coolant, and through in the first water under high pressure heat exchanger 51.The 3rd high-voltage tube 27c is connected the end of downstream side of the first water under high pressure heat exchanger 51 through the first high pressure spot F with the upstream-side-end of the second water under high pressure heat exchanger 52.The 4th high-voltage tube 27d make as the carbon dioxide of primary coolant within it portion flow so that do not mix with the water that conduct heats with secondary refrigerant as the carbon dioxide of primary coolant, and through in the second water under high pressure heat exchanger 52.The 5th high-voltage tube 27e is connected the end of downstream side of the second water under high pressure heat exchanger 52 through the second high pressure spot G with the upstream-side-end of the 3rd water under high pressure heat exchanger 53.The 6th high-voltage tube 27f make as the carbon dioxide of primary coolant within it portion flow so that do not mix with the water that conduct heats with secondary refrigerant as the carbon dioxide of primary coolant, and through in the 3rd water under high pressure heat exchanger 53.The 7th high-voltage tube 27g is connected the end of downstream side of the 3rd water under high pressure heat exchanger 53 with the 3rd high pressure spot H.The 8th high-voltage tube 27h is connected the upstream-side-end on the flow direction of the primary coolant of expansion valve 5a side in the 3rd high pressure spot H and the economizer heat exchanger 7.The 9th high-voltage tube 27i make primary coolant within it portion flow so that this primary coolant with do not mix each other injecting the primary coolants that stream 70 flows, and pass through economizer heat exchanger 7.The tenth high-voltage tube 27j is connected the end of downstream side on the flow direction of the primary coolant of expansion valve 5a side in the economizer heat exchanger 7 with the 4th high pressure spot I.The 11 high-voltage tube 27k is connected the upstream-side-end on the flow direction of the primary coolant of expansion valve 5a side in the heat exchanger 8 between the 4th high pressure spot I and primary coolant.The 12 high-voltage tube 27l make primary coolant within it portion flow so that this primary coolant does not mix with the primary coolant that in low-voltage tube 20, flows each other, and pass through heat exchanger 8 between primary coolant.The 13 high-voltage tube 27m is connected the end of downstream side on the flow direction of the primary coolant of expansion valve 5a side in the heat exchanger between primary coolant 8 through the 5th high pressure spot J with expansion valve 5a.

Low-voltage tube 20 has the first low-voltage tube 20a, the second low-voltage tube 20b, the 3rd low-voltage tube 20c, the 4th low-voltage tube 20d and the 5th low-voltage tube 20e.The first low-voltage tube 20a is connected expansion valve 5a through the first low pressure point K with the 3rd low pressure point M.The second low-voltage tube 20b is connected the 3rd low pressure point M with the upstream-side-end of evaporimeter 4.The 3rd low-voltage tube 20c is connected the upstream-side-end on the flow direction of the primary coolant in the low-voltage tube 20 of heat exchanger 8 between the end of downstream side of evaporimeter 4 and primary coolant through the 4th low pressure point N.The 4th low-voltage tube 20d make primary coolant within it portion flow so that this primary coolant does not mix with the primary coolant that in the 12 high-voltage tube 27l, flows each other, and pass through heat exchanger 8 between primary coolant.The 5th low-voltage tube 20e is connected the end of downstream side on the flow direction of the primary coolant in the low-voltage tube 20 of heat exchanger between primary coolant 8 with suction point A as the suction side of rudimentary side compressor 21.The low pressure temperature sensor 20T that low-pressure sensor 20P that pressure to the primary coolant of process detects is installed on the 5th low-voltage tube 20e and the temperature of the primary coolant of process is detected.

Inject stream 70 and have the expansion valve of injection 73, first ascending pipe 72, second ascending pipe 74, the 3rd ascending pipe 75 and the 4th ascending pipe 76.

First ascending pipe 72 is connected the 3rd high pressure spot H with injection expansion valve 73.Second ascending pipe 74 will inject expansion valve 73 through injection pressure point Q and be connected with the upstream-side-end on the flow direction of the primary coolant that injection stream 70 flows of economizer heat exchanger 7.The 3rd ascending pipe 75 make primary coolant within it portion flow so that this primary coolant does not mix with the primary coolant that in the 9th high-voltage tube 27i, flows each other, and pass through economizer heat exchanger 7.The point R of the 4th ascending pipe 76 after through energy-conservation heat exchange is connected the end of downstream side on the flow direction that injects the primary coolant that stream 70 flows in the economizer heat exchanger 7 with injection junction of two streams D.

As stated, in heat pump circuit 10, adopted injection stream 70, therefore, the coefficient of performance of heat pump circuit has been improved.In addition; Even for example heating less situation of load etc. can't fully obtain under the situation of the cooling effect of the primary coolant at setting-out heat exchanger 40 places of the efficient that is used for improving heat pump circuit 10; Through increasing injection rate, running efficiency is improved through above-mentioned injection stream 70.In addition, in heat pump circuit 10, inject junction of two streams D and be arranged between setting-out heat exchanger 40 and the senior side compressor 25.Therefore, the primary coolant of the high temperature of discharging from rudimentary side compressor 21 can not be cooled before the setting-out heat exchanger 40 arrival, thus setting-out heat exchanger 40 under keeping the situation of the condition of high temperature, being supplied to.Therefore, can make the water that heats usefulness of setting-out heat exchanger 40 in the process be held in sufficiently high temperature.And the 3rd high pressure spot H is arranged on the part that can make primary coolant of economizer heat exchanger 7 upstream sides on the position of injecting stream 70 forks.Therefore, can avoid reducing towards the ability that senior side compressor 25 mobile primary coolants cause from rudimentary side compressor 21 because of sub-cooled.

No. one time bypass pipe 80 has the 14 high-voltage tube 27n, the 6th low-voltage tube 20f and a bypass expansion valve 5b.The 14 high-voltage tube 27n is connected the 4th high pressure spot I with a bypass expansion valve 5b.The 6th low-voltage tube 20f is connected a bypass expansion valve 5b through the second low pressure point L with the 3rd low pressure point M.In addition, owing on a bypass pipe 80, be provided with bypass expansion valve 5b one time, therefore, control part 11 can be regulated the amount of the primary coolant of heat exchanger 8 sides between the process primary coolant.Therefore, can be adjusted to the primary coolant that rudimentary side compressor 21 is sucked and have the suitable degree of superheat.Specifically; Under the situation of the valve opening that reduces a bypass expansion valve 5b; Control part 11 can make the flow through the primary coolant of heat exchanger 8 between primary coolant increase; And the degree of superheat of the primary coolant of rudimentary side compressor 21 suctions is raise; By this, can will make the discharging refrigerant temperature of rudimentary side compressor 21 become the required compression ratio of target temperature and suppress lessly.In addition; Under the situation of the valve opening that increases a bypass expansion valve 5b; Control part 11 can make the flow through the primary coolant of heat exchanger 8 between primary coolant reduce; And the degree of superheat of the primary coolant of rudimentary side compressor 21 suctions is reduced; By this, can avoid significantly reducing to guarantee the situation of internal circulating load because of the suction refrigerant density of rudimentary side compressor 21.

Control part 11 is based on pressing detected values such as temperature sensor 23T, senior suction pressure sensor 24P, senior inlet temperature sensor 24T, high-pressure sensor 27P, high pressure temperature sensor 27T, low-pressure sensor 20P and low pressure temperature sensor 20T in above-mentioned, to rudimentary side compressor 21, senior side compressor 25, inject expansion valve 73, expansion valve 5a, bypass expansion valve 5b, fan 4f etc. and control.

(heating loop 60)

Heating loop 60 makes the water circulation as secondary refrigerant.Heating loop 60 has radiator (radiator) 61, diversion mechanism 62, heats toward the road pipe 65, heats and return road pipe 66, medium voltage side fork stream 67 and high-pressure side fork stream 68.Diversion mechanism 62 comprises and heats mixing valve 64 and heat pump 63.Radiator 61 is arranged in the space as the object that heats, through make as the warm water of secondary refrigerant within it portion flow, thereby the atmosphere temperature rising of object space is heated.The radiator temperature sensor 61T that the temperature of the water that heats usefulness that is used for portion is within it flowed of being provided with radiator 61 detects.Though not shown, radiator 61 has: toward the crossing, this is used to receive from heating the warm water that pump 63 is sent here toward the crossing; And returning the crossing, this returns the crossing and is used for the water after radiator 61 heat releases is seen off to the middle setting-out heat exchanger 40 and the second water under high pressure heat exchanger 52.Heat and return road pipe 66 returning the crossing and heating bifurcation point X and be connected radiator 61.Heating on the bifurcation point X, making the moisture of the heat release of completion in radiator 61 flow to the medium voltage side fork stream 67 of delivering to middle setting-out heat exchanger 40 sides and the high-pressure side fork stream 68 of delivering to the second water under high pressure heat exchanger, 52 sides.Return heating that the temperature that is provided with on the road pipe 66 secondary refrigerant that heats usefulness of process detects and return road temperature sensor 66T heating.

Medium voltage side fork stream 67 has first medium voltage side fork stream 67a, second medium voltage side fork stream 67b and the 3rd medium voltage side fork stream 67c.First medium voltage side fork stream 67a is connected the upstream-side-end that bifurcation point X and the medium voltage side of middle setting-out heat exchanger 40 diverge on the flow direction of the water in the stream 67.Second medium voltage side fork stream 67b make as the water that heats usefulness of secondary refrigerant within it portion flow so that as the water that heats usefulness of secondary refrigerant with in second, press pipe 23b in the carbon dioxide that flows as primary coolant do not mix, and in the process in the setting-out heat exchanger 40.At this; In middle setting-out heat exchanger 40, in second, press flow in the pipe 23b as the carbon dioxide of primary coolant with in second medium voltage side fork stream 67b, flow as the hydromining that heats usefulness of secondary refrigerant with flow towards direction respect to one another to streamed.The 3rd medium voltage side fork stream 67c with the end of downstream side on the flow direction of the water in the medium voltage side fork stream 67 of middle setting-out heat exchanger 40 with heat junction of two streams Y and be connected.On the 3rd medium voltage side fork stream 67c, be provided with the medium voltage side fork stream temperature sensor 67T that the temperature to the water that heats usefulness of process detects.

High-pressure side fork stream 68 has first high-pressure side fork stream 68a, second high-pressure side fork stream 68b and the 3rd high-pressure side fork stream 68c.The upstream-side-end that first high-pressure side fork stream 68a diverges bifurcation point X and the high-pressure side of the second water under high pressure heat exchanger 52 on the flow direction of the water in the stream 68 is connected.Second high-pressure side fork stream 68b make as the water that heats usefulness of secondary refrigerant within it portion flow so that do not mix with carbon dioxide mobile in the 4th high-voltage tube 27d as primary coolant as the water that heats usefulness of secondary refrigerant, and through in the second water under high pressure heat exchanger 52.At this; In the second water under high pressure heat exchanger 52, in the 4th high-voltage tube 27d, flow as the carbon dioxide of primary coolant with in the fork stream 68b of second high-pressure side, flow as the hydromining that heats usefulness of secondary refrigerant with flow towards direction respect to one another to streamed.The 3rd high-pressure side fork stream 68c with the end of downstream side on the flow direction of the water in the high-pressure side fork stream 68 of the second water under high pressure heat exchanger 52 with heat junction of two streams Y and be connected.On the 3rd high-pressure side fork stream 68c, be provided with the high-pressure side fork stream temperature sensor 68T that the temperature to the water that heats usefulness of process detects.

In addition; Since water that heats usefulness that in first medium voltage side fork stream 67a, flows and the water that heats usefulness that in the fork stream 68 of first high-pressure side, flows all heating fork on the bifurcation point X and not with the heat exchange of outside, therefore the temperature of the temperature of the water that heats use that in first medium voltage side fork stream 67a, flows and the water that heats use that in the fork stream 68 of first high-pressure side, flows is identical Temperature Distribution.Relative therewith, the temperature of the water that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows be with middle setting-out heat exchanger 40 in through with in second, press the primary coolant that flows among the pipe 23b to carry out the corresponding temperature of heat that obtains after the heat exchange.In addition, the temperature of the water that heats usefulness that in the 3rd high-pressure side fork stream 68c, flows be with the second water under high pressure heat exchanger 52 in through carrying out the corresponding temperature of heat that obtains after the heat exchange with the primary coolant that in the 4th high-voltage tube 27d, flows.Therefore, the temperature of the water that heats use that in the 3rd medium voltage side fork stream 67c, flows sometimes is different temperature with the temperature that heats the water that uses that in the fork stream 68c of the 3rd high-pressure side, flows.

Heat and to heat junction of two streams Y toward road pipe 65 and be connected with the past crossing of radiator 61.Heat toward being provided with of road pipe 65 midway at this and to heat pump 63 what regulate through the flow that heats the water that heats usefulness of pipe 65 toward the road.Heat mixing valve 64 be arranged on through the water that heats usefulness of the 3rd medium voltage side fork stream 67c with heat Zhi Liudian Y through the hydration stream that heats usefulness of the 3rd high-pressure side fork stream 68c.Heat mixing valve 64 through respectively to the aperture of the aperture of the part that is connected with the 3rd medium voltage side fork stream 67c side and the part that is connected with the 3rd high-pressure side fork stream 68c side, come to the flow of the water that heats usefulness that in medium voltage side fork stream 67, flows and in stream 68c is diverged in the 3rd high-pressure side the ratio of the flow of the mobile water that heats usefulness regulate.

In addition; Control part 11 is based on detected temperature such as above-mentioned radiator temperature sensor 61T, medium voltage side fork stream temperature sensor 67T, high-pressure side fork stream temperature sensor 68T etc.; Flow to heating the shunting ratio in the mixing valve 64 and heating pump 63 is controlled, thereby can supply the secondary refrigerant of desired temperature in radiator 61.

(heat supply water loop 90)

Heat supply water loop 90 makes the water circulation of using as heat supply water.Heat supply water loop 90 has heat storage water tank 91, feed pipe 94, heat supply water pipe 98, heat supply water bypass pipe 99, heat supply water mixing valve 93, heat supply hydro-thermal pump line 95 and heat supply water pump 92.

Though not shown, on heat storage water tank 91, be provided with past crossing of circulation and circulation and return the crossing.After the running water that has led to not shown outside, the water of normal temperature via feed pipe 94 from heat storage water tank 91, supplying with near the bottom of heat storage water tank 91.Heat supply hydro-thermal pump line 95 has the first heat supply hydro-thermal pump line 95a, the second heat supply hydro-thermal pump line 95b, the 3rd heat supply hydro-thermal pump line 95c, the 4th heat supply hydro-thermal pump line 95d, the 5th heat supply hydro-thermal pump line 95e and the 6th heat supply hydro-thermal pump line 95f.

The first heat supply hydro-thermal pump line 95a is connected toward the crossing circulation of heat storage water tank 91 with heat supply water pump 92.On the first heat supply hydro-thermal pump line 95a, be provided with the heat supply water inflow temperature sensor 94T that the temperature of the water that the heat supply water of process is used detects.The second heat supply hydro-thermal pump line 95b is connected the upstream-side-end on the flow direction of the water in the heat supply hydro-thermal pump line 95 of heat supply water pump 92 and the 3rd water under high pressure heat exchanger 53.The 3rd heat supply hydro-thermal pump line 95c make water that heat supply water uses within it portion flow so that the water that heat supply water is used does not mix with the carbon dioxide as primary coolant mobile in the 6th high-voltage tube 27f, and through in the 3rd water under high pressure heat exchanger 53.At this, in the 3rd water under high pressure heat exchanger 53, the hydromining of using as the carbon dioxide of primary coolant and the heat supply water that in the 3rd heat supply hydro-thermal pump line 95c, flows that in the 6th high-voltage tube 27f, flows with flow towards direction respect to one another to streamed.The 4th heat supply hydro-thermal pump line 95d is connected the upstream-side-end on the flow direction of the water in the heat supply hydro-thermal pump line 95 of the end of downstream side on the flow direction of the water in the heat supply hydro-thermal pump line 95 of the 3rd water under high pressure heat exchanger 53 and the first water under high pressure heat exchanger 51.On the 4th heat supply hydro-thermal pump line 95d, be provided with the heat supply water medium temperature sensor 95T that the temperature of the water that the heat supply water of process is used detects.In the second water under high pressure heat exchanger 52, do not carry out water that heat supply water uses and as the heat exchange between the carbon dioxide of primary coolant.The 5th heat supply hydro-thermal pump line 95e make water that heat supply water uses within it portion flow so that the water that heat supply water is used does not mix with the carbon dioxide as primary coolant mobile in the second high-voltage tube 27b, and through in the first water under high pressure heat exchanger 51.At this, in the first water under high pressure heat exchanger 51, the hydromining of using as the carbon dioxide of primary coolant and the heat supply water that in the 5th heat supply hydro-thermal pump line 95e, flows that in the second high-voltage tube 27b, flows with flow towards direction respect to one another to streamed.The 6th heat supply hydro-thermal pump line 95f returns the crossing with the end of downstream side on the flow direction of the water in the heat supply hydro-thermal pump line 95 of the first water under high pressure heat exchanger 51 with the circulation of heat storage water tank 91 and is connected.On the 6th heat supply hydro-thermal pump line 95f, be provided with the heat supply water leaving water temperature sensor 98T that the temperature of the water that the heat supply water of process is used detects.

Heat supply water pipe 98 will accumulate in hot water in the heat storage water tank 91 from guiding to the not shown place that will utilize near the upper end of heat storage water tank 91.Heat supply water pipe 94 is provided with the fork part that begins to diverge from the current to heat storage water tank 91 sides, i.e. the bifurcation point W that supplies water.Heat supply water pipe 98 be provided with from the heat supply hydration flow point Z of heat storage water tank 91 to the current in the place that will utilize interflow.Heat supply water bypass pipe 99 is connected above-mentioned water supply bifurcation point W with above-mentioned heat supply hydration flow point Z.On heat supply hydration flow point Z, be provided with heat supply water mixing valve 93, the blending ratio of the water of the normal temperature that this heat supply water mixing valve 93 can come with supplying with via heat supply water bypass pipe 99 from running water the hot water of sending here via heat supply water pipe 98 from heat storage water tank 91 is regulated.Through regulating the blending ratio of above-mentioned heat supply water mixing valve 93, the temperature that can regulate the water of delivering to the place that will utilize.

In addition, control part 11 is controlled the flow of heat supply water pump 92 based on detected temperature such as above-mentioned heat supply water inflow temperature sensor 94T, heat supply water medium temperature sensor 95T, heat supply water leaving water temperature sensor 98T etc.

The running of < 1-2>heat pump circuit 10

Fig. 2 is the pressure-enthalpy line chart after heat pump 1 running.Fig. 3 is the temperature-entropy line chart after heat pump 1 running.

Below, lift an object lesson temperature distribution state of primary coolant is described.

21 pairs of primary coolants of about 22 ℃ (some A) that in low-voltage tube 20, flow and come of rudimentary side compressor compress, so that the target discharge temperature reaches (some B) about 90 ℃.In addition, utilize control part 11 to regulate, drop to and to make pressure (evaporating pressure) based on the environment temperature that evaporimeter 4 is set as the carbon dioxide evaporation of primary coolant so that this pressure that is in the primary coolant that flows in the low-voltage tube 20 becomes.

The primary coolant of discharging from rudimentary side compressor 21 is via pressing first pipe 23a to press pipe 23b in second in the setting-out heat exchanger 40 in flowing into.The primary coolant of setting-out heat exchanger 40 carries out heat exchange each other through the water that heats with secondary refrigerant with conduct through second medium voltage side fork stream 67b in the inflow, and is cooled to about 35 ℃ (put ℃).At this; Because primary coolant in the middle setting-out heat exchanger 40 and secondary refrigerant are to flow to streamed; Therefore; In middle setting-out heat exchanger 40 second in press near the outlet of pipe 23b, primary coolant is in the state of cooling by heat release in radiator 61 about 30 ℃ secondary refrigerant cools off effectively.

The primary coolant of pressing heat exchanger 40 in the process reaches (some D) about 30 ℃ through being further cooled on the injection junction of two streams D that in the 3rd, presses pipe 23c and via about 27 ℃ the primary coolant interflow that injection stream 70 flows into.At this, control part 11 is controlled, so that have the degree of superheat or be in supercriticality at the primary coolant that injects after collaborating on the junction of two streams D.In addition; At this; Control part 11 is controlled; So that inject on the junction of two streams D primary coolant behind the interflow can be when senior side compressor 25 be driven with the compression ratio identical with the compression ratio of rudimentary side compressor 21, the target temperature that makes the primary coolant of discharging from senior side compressor 25 is identical with the target temperature of the primary coolant of discharging from rudimentary side compressor 21 90 ℃.In addition, 11 pairs of control parts suck the primary coolant of senior side compressor 25 suctions and control, with the thermal balance at setting-out heat exchanger 40 in being adjusted in and injection stream 70 places.

Be inhaled into senior side compressor 25 injecting the primary coolant that collaborates on the junction of two streams D, primary coolant further compressed so that the target discharge temperature reaches the temperature identical with the target temperature of the discharging refrigerant of rudimentary side compressor 21, promptly about 90 ℃.At this, utilize the senior side compressor 25 of control part 11 controls to compress, so that the discharging refrigerant pressure of primary coolant reaches the pressure (some E) above the critical pressure of primary coolant.

The primary coolant of being discharged by senior side compressor 25 flows into the second high-voltage tube 27b in the first water under high pressure heat exchanger 51 via the first high-voltage tube 27a.The primary coolant that flows into the first water under high pressure heat exchanger 51 is cooled to (some F) about 85 ℃ through carrying out heat exchange each other with the water of using through the heat supply water of the 5th heat supply hydro-thermal pump line 95e.Because while the state heat release of keeping above critical pressure, so primary coolant produces variations in temperature continuously.At this; Because primary coolant in the first water under high pressure heat exchanger 51 and secondary refrigerant are to flow to streamed; Therefore; Near the outlet of the second high-voltage tube 27b in the first water under high pressure heat exchanger 51, the water that about 30 ℃ the heat supply water that primary coolant is not also fully heated is used cools off effectively.

Primary coolant through the first water under high pressure heat exchanger 51 flows into the 4th high-voltage tube 27d in the second water under high pressure heat exchanger 52 via the 3rd high-voltage tube 27c.The primary coolant that flows into the second water under high pressure heat exchanger 52 carries out heat exchange each other and is cooled to about 35 ℃ and (puts G) through heating water with secondary refrigerant with conduct through second high-pressure side fork stream 68b.At this; Because primary coolant in the second water under high pressure heat exchanger 52 and secondary refrigerant are to flow to streamed; Therefore; Near the outlet of the 4th high-voltage tube 27d in the second water under high pressure heat exchanger 52, primary coolant is in the state of cooling by heat release in radiator 61 about 30 ℃ secondary refrigerant cools off effectively.

Primary coolant through the second water under high pressure heat exchanger 52 flows into the 6th high-voltage tube 27f in the 3rd water under high pressure heat exchanger 53 via the 5th high-voltage tube 27e.The primary coolant that flows into the 3rd water under high pressure heat exchanger 53 is further cooled through carrying out heat exchange each other with the water of using through the heat supply water of the 3rd heat supply hydro-thermal pump line 95c, becomes (some H) about 30 ℃.At this; Because primary coolant in the 3rd water under high pressure heat exchanger 53 and secondary refrigerant are to flow to streamed; Therefore; Near the outlet of the 6th high-voltage tube 27f in the 3rd water under high pressure heat exchanger 53, that primary coolant is risen than the temperature of running water through mixing in heat storage water tank 91 slightly, promptly the water used of the heat supply water about 20 ℃ cools off effectively.Then, the primary coolant through the 3rd water under high pressure heat exchanger 53 arrives the 3rd high pressure spot H via the 7th high-voltage tube 27g.

At this; Water under high pressure heat exchanger 50 is divided into three heat exchangers; Change because of the primary coolant that in water under high pressure heat exchanger 50, flows is in two critical conditions appearance temperature in exothermic process, and the range of temperature (30 ℃～65 ℃) as the water of secondary refrigerant of circulation is included in the range of temperature (20 ℃～90 ℃) of the water that the heat supply water in the heat supply water loop 90 uses in heating loop 60.Then; Distribute accordingly with said temperature; The primary coolant that is in the primary coolant of temperature higher state in the primary coolant that senior side compressor 25 is discharged and is in the low state of temperature is distributed into the water of using with heat supply water and carries out heat exchange, and the secondary refrigerant that the primary coolant of the state of temperature that mediates is distributed into and heats usefulness carries out heat exchange.By this, no matter be the heat exchange of the water of primary coolant and heat supply water, or primary coolant and heat the heat exchange of the water of usefulness, the temperature difference that all can will carry out between the fluid of heat exchange suppresses lessly, thereby heat exchanger effectiveness is improved.

The primary coolant that arrives the 3rd high pressure spot H is split into via the 8th high-voltage tube 27h to the cold-producing medium stream of expansion valve 5a side with to the cold-producing medium stream that injects stream 70 sides.Control part 11 can be controlled the shunting degree here through regulating the valve opening of injecting expansion valve 73.The primary coolant that branches to injection stream 70 sides is depressurized at injection expansion valve 73 after flowing through first ascending pipe 72, makes the temperature of primary coolant drop to (some Q) about 23 ℃.

The 3rd ascending pipe 75 that the primary coolant that is depressurized at injection expansion valve 73 flows in the economizer heat exchanger 7 via second ascending pipe 74.Flow into the primary coolant of economizer heat exchanger 7 and carry out heat exchange each other, (put R) and be heated to about 27 ℃ with about 30 ℃ the primary coolant that in the 9th high-voltage tube 27i, flows.

About 27 ℃ primary coolant through the 3rd ascending pipe 75 in the economizer heat exchanger 7 collaborates with the primary coolant that flows at pressure pipe 23 on above-mentioned injection junction of two streams D via the 4th ascending pipe 76.

About 30 ℃ the primary coolant that injects stream 70 sides that do not flow into that arrives in the primary coolant of the 3rd high pressure spot H flows into the 9th high-voltage tube 27i in the economizer heat exchanger 7 via the 8th high-voltage tube 27h.About 30 ℃ the primary coolant that flows into the 9th high-voltage tube 27i in the economizer heat exchanger 7 is through carrying out heat exchange with about 27 ℃ the primary coolant that in the 3rd ascending pipe 75, flows as described above each other, and is further cooled to about 25 ℃ (some I).The primary coolant that flows through the 9th high-voltage tube 27i in the economizer heat exchanger 7 arrives the 4th high pressure spot I via the tenth high-voltage tube 27j.

The primary coolant that arrives the 4th high pressure spot I is split into to the cold-producing medium stream of bypass pipe 80 sides with to the cold-producing medium stream of the 11 high-voltage tube 27k side.Control part 11 can be regulated the shunting degree here through the valve opening of regulating a bypass expansion valve 5b.The primary coolant that in the 11 high-voltage tube 27k, flows flows into the 12 high-voltage tube 27l in the heat exchanger 8 between primary coolant.Flow into about 25 ℃ the primary coolant of the 12 high-voltage tube 27l in the heat exchanger 8 between primary coolant and carry out heat exchange each other, (put J) and be cooled to about 20 ℃ with about-3 ℃ the primary coolant that in the 4th low-voltage tube 20d, flows.

Primary coolant through the 12 high-voltage tube 12 in the heat exchanger between primary coolant 8 flows into expansion valve 5a via the 13 high-voltage tube 27m.In expansion valve 5a, through by control part 11 control valve openings, regulate the decompression degree of the primary coolant of process, thereby the refrigerant pressure of the primary coolant of process is reduced, also make refrigerant temperature be reduced to (some K) about-3 ℃.At this, primary coolant is decompressed to the pressure below the critical pressure through the adjusting of the decompression degree of being undertaken by control part 11, becomes the gas-liquid two-phase state.

In addition, in heat pump circuit 10, can not only make the primary coolant cooling, can also make the primary coolant cooling through heat exchanger between primary coolant 8 through economizer heat exchanger 7.In addition, in the cooling of the primary coolant that between to primary coolant, flows in the heat exchanger 8, can use the primary coolant of the suction side of the rudimentary side compressor 21 that temperature is minimum in heat pump circuit 10 primary coolant flows through.By this, density can be improved, and the internal circulating load of the primary coolant in the heat pump circuit 10 can be increased through the primary coolant of expansion valve 5a.

The primary coolant that flows through expansion valve 5a flow to the 3rd low pressure point M via the first low-voltage tube 20a, and the primary coolant interflow of coming with in the 6th low-voltage tube 20f, flowing (some M).

Arrive about 25 ℃ the primary coolant that does not flow to the 11 high-voltage tube 27k side in the primary coolant of the 4th high pressure spot I and flow to bypass pipe 80 sides No. one time, and flow to bypass expansion valve 5b one time via the 14 high-voltage tube 27n.In bypass expansion valve 5b, through by control part 11 control valve openings, regulate the decompression degree of the primary coolant of process, thereby the refrigerant pressure of the primary coolant of process is reduced, also make refrigerant temperature be reduced to (some L) about-3 ℃.At this, the same with a K, primary coolant is decompressed to the pressure below the critical pressure through the adjusting of the decompression degree of being undertaken by control part 11, becomes the gas-liquid two-phase state.

Primary coolant through a bypass expansion valve 5b flow to the 3rd low pressure point M via the 6th low-voltage tube 20f, and flows and next primary coolant interflow (some M) via the first low-voltage tube 20a with above-mentioned.

About-3 ℃ the primary coolant that collaborates at the 3rd low pressure point M place is via the second low-voltage tube 20b inflow evaporator 4.The primary coolant of inflow evaporator 4 with through fan 4f to evaporimeter 4 initiatively air supplied carry out heat exchange each other.Through the heat exchange at evaporimeter 4 places, about-3 ℃ the primary coolant that is in the gas-liquid two-phase state evaporates (carrying out latent heat changes) and aridity is increased under the certain state of temperature maintenance, become the state (some N) that approaches saturation state.

Primary coolant through evaporator 4 flows into the 4th low-voltage tube 20d in the heat exchanger 8 between primary coolant via the 3rd low-voltage tube 20c.About-3 ℃ the primary coolant that flows among the 4th low-voltage tube 20d between primary coolant in the heat exchanger 8 is heated to about 22 ℃ through carrying out heat exchange each other with about 25 ℃ the primary coolant that in the 12 high-voltage tube 27l, flows as described above, becomes the state (some A) that has the degree of superheat.

Primary coolant through the 4th low-voltage tube 20d in the heat exchanger between primary coolant 8 is inhaled into rudimentary side compressor 21 after becoming superheat state.

In heat pump circuit 10, make the primary coolant circulation as described above.

The running of < 1-3>heating loop 60

In order to be heated up in the space that is provided with radiator 61, control part 11 is controlled, so that about 65 ℃ the water as secondary refrigerant is supplied to radiator 61.

Below, lift an object lesson temperature distribution state of the secondary refrigerant that heats usefulness is described.

Though also with the performance of radiator 61 and to heat the degree of load relevant, can be reduced to the temperature about 35 ℃, and return the road and manage 66 and flow to and heat bifurcation point X via heating while pass through the water that the conduct of heat releases in the radiator 61 heats the secondary refrigerant of usefulness.

Heating on the bifurcation point X, be divided into to the cold-producing medium stream of medium voltage side fork stream 67 with to the cold-producing medium stream of high-pressure side fork stream 68 sides.

From heating bifurcation point X second medium voltage side fork stream 67b in the setting-out heat exchanger 40 towards the secondary refrigerant of medium voltage side fork stream 67 side flow flows into via first medium voltage side fork stream 67a.The secondary refrigerant that flows among second medium voltage side fork stream 67b in middle setting-out heat exchanger 40 passes through in through second, to press the primary coolant heating of pipe 23b as described above, and the temperature of the secondary refrigerant about 30 ℃ is risen to about 65 ℃.In addition; As stated; Because primary coolant in the middle setting-out heat exchanger 40 and secondary refrigerant are to flow to streamed; Therefore; Near the outlet of second medium voltage side fork stream 67b in middle setting-out heat exchanger 40, secondary refrigerant is heated by about 90 ℃ higher primary coolant of high temperature effectively.Then, through in the setting-out heat exchanger 40 second medium voltage sides fork stream 67b and be warming up to secondary refrigerant about 65 ℃ and flow to through the 3rd medium voltage side fork stream 67c and heat junction of two streams Y.

Flow into second high-pressure side fork stream 68b in the second water under high pressure heat exchanger 52 from the secondary refrigerant that heats bifurcation point X fork stream 68 side flow via first high-pressure side fork stream 68a towards the high-pressure side.The secondary refrigerant that flows among second high-pressure side fork stream 68b in the second water under high pressure heat exchanger 52 passes through to be heated by the primary coolant through the 4th high-voltage tube 27d as described above, and the temperature of the secondary refrigerant about 30 ℃ is risen to about 65 ℃.In addition; As stated; Because primary coolant in the second water under high pressure heat exchanger 52 and secondary refrigerant are to flow to streamed; Therefore; Near the outlet of second high-pressure side fork stream 68b in the second water under high pressure heat exchanger 52, secondary refrigerant is heated by about 85 ℃ higher primary coolant of temperature effectively.Then, being warming up to secondary refrigerant about 65 ℃ through the fork stream 68b of second high-pressure sides in the second water under high pressure heat exchanger 52 flow to through the 3rd high-pressure side fork stream 68c and heats junction of two streams Y.

Heating on the junction of two streams Y, in the 3rd, pressing fork stream 67c and secondary refrigerant that comes and the secondary refrigerant interflow of coming through the 3rd high-pressure side fork stream 68c.In addition; Control part 11 heats valve opening and the valve opening of high-pressure side fork stream 68 sides of medium voltage side fork stream 67 sides of mixing valve 64 through adjusting, can be adjusted in the flow of secondary refrigerant of flow and stream 68 side flow that diverge in the high-pressure side of the secondary refrigerant of medium voltage side fork stream 67 side flow.By this; The secondary refrigerant of control part 11 through being adjusted on one side circulation in the heating loop 60 is at heated degree of middle setting-out heat exchanger 40 sides and ratio in the heated degree of the second water under high pressure heat exchanger, 52 sides; Regulate the flow through the secondary refrigerant that heats pump 63 on one side, the temperature that is controlled to the secondary refrigerant that on heating junction of two streams Y, collaborates is a desired temperature in the radiator 61.

Like this, be supplied to radiator 61 via heating heating the secondary refrigerant that is heated to about 65 ℃ that collaborates on the junction of two streams Y toward road pipe 65.In heating loop 60, make the secondary refrigerant circulation as described above.

The running of < 1-4>heat supply water loop 90

The flow-control that control part 11 carries out heat supply water pump 92 accumulates in the heat storage water tank 91 can make the hot water about 90 ℃.

Below, the temperature distribution state of lifting the water that an object lesson uses heat supply water describes.

The water that the temperature of the below of the heat storage water tank 91 that running water flows into is lower is mobile towards heat supply hydro-thermal pump line 95 with about 20 ℃ temperature.

The water of using through about 20 ℃ the heat supply water of the first heat supply hydro-thermal pump line 95a and the second heat supply hydro-thermal pump line 95b flows into the 3rd heat supply hydro-thermal pump line 95c in the 3rd water under high pressure heat exchanger 53.The water that the heat supply water that flows among the 3rd heat supply hydro-thermal pump line 95c in the 3rd water under high pressure heat exchanger 53 is used is through being heated by about 35 ℃ primary coolant through the 6th high-voltage tube 27f the 3rd water under high pressure heat exchanger 53 in as described above, and the temperature of the water that the heat supply water about 20 ℃ uses is risen to about 30 ℃.In addition; As stated; Because primary coolant in the 3rd water under high pressure heat exchanger 53 and secondary refrigerant are to flow to streamed; Therefore; Near the outlet of the 3rd heat supply hydro-thermal pump line 95c in the 3rd water under high pressure heat exchanger 53, secondary refrigerant is heated by about 35 ℃ higher primary coolant of temperature effectively.

In the 3rd water under high pressure heat exchanger 53, be warming up to the water that the heat supply water about 30 ℃ uses and flow into the 5th heat supply hydro-thermal pump line 95e in the first water under high pressure heat exchanger 51 through the 4th heat supply hydro-thermal pump line 95d.The water that the heat supply water that flows among the 5th heat supply hydro-thermal pump line 95e in the first water under high pressure heat exchanger 51 is used is through being heated by about 90 ℃ primary coolant through the second high-voltage tube 27b the first water under high pressure heat exchanger 51 in as described above, and the temperature of the water that the heat supply water about 30 ℃ uses is risen to about 90 ℃.In addition; As stated; Because primary coolant in the first water under high pressure heat exchanger 51 and secondary refrigerant are to flow to streamed; Therefore; Near the outlet of the 5th heat supply hydro-thermal pump line 95e in the first water under high pressure heat exchanger 51, secondary refrigerant is heated by about 90 ℃ higher primary coolant of temperature effectively.

In the first water under high pressure heat exchanger 51, be heated to water that the heat supply water about 90 ℃ uses through the 6th heat supply hydro-thermal pump line 95f flow into heat storage water tank 91 above.

Like this, in heat supply water loop 90, circulate, just can improve the temperature that accumulates in the water that heat storage water tank 91 interior heat supply water use through the water that heat supply water is used.

The unified control of < 1-5>secondary refrigerant temperature

As stated; For heat pump circuit 10; Control part 11 is controlled to and can be supplied to each loop corresponding to the heat of the heat supply water load that heats load and heat supply water loop 90 of heating loop 60, and turns round cycle efficieny can be remained good as far as possible mode.In addition; For heating loop 60; Specifically; Control part 11 carries out rudimentary side compressor 21; The control of senior side compressor 25 and expansion valve 5a etc. is so that the temperature of the primary coolant of setting-out heat exchanger 40 is higher than the temperature of the secondary refrigerant that heats usefulness of setting-out heat exchanger 40 in flowing in flowing into; Make the temperature of the primary coolant that flows into the second water under high pressure heat exchanger 52 higher than the temperature of the secondary refrigerant that heats usefulness that flows into the second water under high pressure heat exchanger 52; The temperature of the primary coolant of setting-out heat exchanger 40 and to flow into the temperature of primary coolant of the second water under high pressure heat exchanger 52 all high than desired temperature in the radiator 61 in the inflow.

Then; Control part 11 is controlled, so that the target discharge temperature of rudimentary side compressor 21 is higher than desired temperature in the radiator 61, the temperature after the heat of when the target discharge temperature of senior side compressor 25 deducts through the first water under high pressure heat exchanger 51, emitting is higher than desired temperature the radiator 61.In addition, control part 11 is controlled, the compression ratio of compression ratio and senior side compressor 25 that environment makes rudimentary side compressor 21 after confirming evaporating temperature to be set for as far as possible little compression ratio and equate according to evaporimeter 4.In order to follow these purposes, specifically, control part 11 carries out the rudimentary side compressor 21, senior side compressor 25, expansion valve 5a of heat pump circuit 10, the control of injecting expansion valve 73, bypass expansion valve 5b and fan 4f.In addition; When the temperature of primary coolant is too high; Scale (hot water dirt) may appear on the inside pipe wall face of the water flows that inside pipe wall face that the secondary refrigerant that heats usefulness that supplies to carry out heat exchange flows and the heat supply water that supplies to carry out heat exchange are used; Therefore; Control part 11 is controlled, so that below the high temperature limit value of the temperature of primary coolant for regulation.

In the good operating condition of the cycle efficieny that realizes keeping as far as possible above-mentioned heat pump circuit 10 sides; Control part 11 also carries out the unified control of secondary refrigerant temperature, so that the temperature of the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c of heating loop 60, flows and the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows is identical temperature.In addition; Control part 11 is not only controlled so that the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows is unified with the temperature of the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows, also control so that in this unified temperature and the radiator 61 desired temperature consistent.Specifically; Control part 11 utilizes blending ratio control and flow-control to make temperature be unified into desired temperature in the radiator 61; In above-mentioned blending ratio control; The blending ratio that heats mixing valve 64 through control is adjusted in the flow of the secondary refrigerant that heats usefulness that flows in the medium voltage side fork stream 67 and the ratio of the flow of the secondary refrigerant that heats usefulness that in the fork stream 68 of high-pressure side, flows; In above-mentioned flow-control, the flow that heats pump 63 through control is regulated the flow of the secondary refrigerant that heats usefulness that is supplied to radiator 61.

For the temperature of the temperature that makes the secondary refrigerant that heats use that in the 3rd medium voltage side fork stream 67c, flows and the secondary refrigerant that heats use mobile in the fork stream 68c of the 3rd high-pressure side is identical temperature; Control part 11 heats the control of mixing valve 64, so that the flow of the secondary refrigerant of the low temperature side in medium voltage side fork stream detected temperature of temperature sensor 67T and the detected temperature of high-pressure side fork stream temperature sensor 68T reduces and the flow of the secondary refrigerant of high temperature side is increased.By this,, make flow velocity slack-off, can increase secondary refrigerant time from primary coolant acquisition heat when carrying out heat exchange, thereby temperature is risen with primary coolant through reducing flow for the secondary refrigerant of low temperature side.On the contrary,, flow velocity is accelerated, can shorten secondary refrigerant time from primary coolant acquisition heat when carrying out heat exchange, thereby temperature is reduced with primary coolant through increasing flow for the secondary refrigerant of high temperature side.Like this, the temperature that can make the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows diminishes with the difference of the temperature of the secondary refrigerant that heats usefulness that in the fork stream 68c of the 3rd high-pressure side, flows.

In addition, at this, desired temperature is meant the temperature value with certain amplitude as described below in the radiator 61.

In heating loop 60, can set heating of user's needs through input with the thermal discharge of secondary refrigerant in radiator 61.In addition, 11 pairs of control parts heat mixing valve 64 and heat pump 63 and control, with the thermal discharge in radiator 61 that can guarantee that the user requires.Specifically; As the control of guaranteeing desired thermal discharge in the radiator 61; The situation etc. of temperature of the secondary refrigerant that heats usefulness raises when the situation that the temperature that when flow through the secondary refrigerant that heats usefulness that heats pump 63 is increased, will heat the secondary refrigerant of usefulness suppresses lowlyer being arranged and flow through the secondary refrigerant that heats usefulness that heats pump 63 is reduced.Promptly; Under the situation of guaranteeing identical heat, when making the flow that heats pump 63 increase to certain value, heat the required temperature that reaches of the secondary refrigerant of usefulness than the flow that heats pump 63 is reduced to hour heat the required temperature that reaches of secondary refrigerant of usefulness than above-mentioned certain value low.On the contrary; Under the situation of guaranteeing identical heat, when making the flow that heats pump 63 reduce to another value, heat the required temperature that reaches of the secondary refrigerant of usefulness than the flow that heats pump 63 is increased to be worth the required temperature that reaches of secondary refrigerant that heats usefulness when big than above-mentioned another high.And, in order to make the atmosphere temperature rising of the surrounding space that is provided with radiator 61, need make environment temperature (by the radiator temperature sensor 61T detected temperature) height of the temperature of the secondary refrigerant that is supplied to radiator 61 than radiator 61.Desired temperature is as stated than by the high temperature of the detected temperature of radiator temperature sensor 61T in the radiator 61, and has and can guarantee the corresponding temperature amplitude of range of flow of desired thermal discharge in the radiator 61.In addition, can also come the limiting temperature amplitude through the exothermicity of reflection radiator 61 self.

Heating in the road pipe 65 temperature towards the secondary refrigerant that heats usefulness that radiator 61 flows is in medium voltage side fork stream 67, to flow and the secondary refrigerant that heats usefulness that the secondary refrigerant that heats usefulness that comes comes with in the fork stream 68 of high-pressure side, flowing is heating the temperature behind the interflow on the junction of two streams Y.

Therefore; When the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows and the temperature of secondary refrigerant mobile in the fork stream 68c of the 3rd high-pressure side are identical temperature; The temperature of the secondary refrigerant on heating junction of two streams Y behind the interflow also with the interflow before temperature be identical temperature, it becomes the temperature to the secondary refrigerant that heats usefulness of radiator 61 supplies.

(heat increases processing)

When carrying out the unified control of above-mentioned secondary refrigerant temperature, by in the not enough radiator 61 of the unified control of secondary refrigerant temperature temperature after reunification during desired temperature, the heat that control part 11 reduces the flow that heats pump 63 increases control.

By this, can make the flow velocity of the secondary refrigerant that in medium voltage side fork stream 67, flows and the flow velocity of the secondary refrigerant that in the fork stream 68 of high-pressure side, flows all reduces.Thereby, can make the secondary refrigerant that in medium voltage side fork stream 67, flows obtain the time of heat and the secondary refrigerant that the fork stream 68 of high-pressure side, flows all increased from the time that primary coolant obtains heat from primary coolant.By this; The temperature of the secondary refrigerant that heats usefulness that can make the temperature of the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows and in the fork stream 68c of the 3rd high-pressure side, flow is unified into desired temperature in the radiator 61, thus can be corresponding with the heat load in the radiator 61.

(heat reduces processing)

When carrying out the unified control of above-mentioned secondary refrigerant temperature, when surpassing in the radiator 61 desired temperature by the unified control of secondary refrigerant temperature temperature after reunification, the heat that control part 11 increases the flow that heats pump 63 reduces control.

By this, can make the flow velocity of the secondary refrigerant that in medium voltage side fork stream 67, flows and the flow velocity of the secondary refrigerant that in the fork stream 68 of high-pressure side, flows all raises.Thereby, can make the secondary refrigerant that in medium voltage side fork stream 67, flows obtain the time of heat and the secondary refrigerant that the fork stream 68 of high-pressure side, flows all is suppressed to shorter from the time that primary coolant obtains heat from primary coolant.By this; The temperature of the secondary refrigerant that heats usefulness that can make the temperature of the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows and in the fork stream 68c of the 3rd high-pressure side, flow is unified into desired temperature in the radiator 61, thus can be corresponding with the heat load in the radiator 61.

The characteristic of < 1-6>first embodiment

In the heat pump 1 of first embodiment, control part 11 is controlled, so that the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows is unified with the temperature of the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows.At this, mobile secondary refrigerant reaches the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows and all arrives lower to the temperature before heat release on every side of radiator 61 in the 3rd medium voltage side fork stream 67c, and produces the heat release loss.Yet; In the heat pump 1 of first embodiment; The temperature of the secondary refrigerant that can not only avoid in the 3rd medium voltage side fork stream 67c, flowing becomes too high temperature; The temperature of the secondary refrigerant that also can avoid in the 3rd high-pressure side fork stream 68c, flowing becomes too high temperature, and gets the difference limit of itself and environment temperature less.Therefore, the temperature of the secondary refrigerant that just in the 3rd medium voltage side fork stream 67c, flows on the temperature of the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows, can not limit peripherad heat release loss less yet.

And control part 11 is controlled, so that the temperature of the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows and the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows is unified into desired temperature in the radiator 61.Therefore, need not carry out adjustment, so that the temperature of the secondary refrigerant that heats usefulness behind the interflow becomes desired temperature in the radiator 61 on heating junction of two streams Y through heating or cooling.By this, can not need this temperature regulating heater or cooler.

In addition; In the heat pump circuit 10 of the heat pump 1 of first embodiment; Supply primary coolant that senior side compressor 25 sucks in process, to be heated the secondary refrigerant cooling of usefulness during setting-out heat exchanger 40, and by the primary coolants that come are further cooled off injecting that stream 70 flows.Therefore, can improve the density of the primary coolant of senior side compressor 25 suctions, and the efficient of heat pump circuit 10 is improved.

And the secondary refrigerant that heats usefulness cools off the primary coolant that is inhaled into senior side compressor 25 and the heat energy utilization that obtains heats load in radiator 61.

In addition; Even obtained to the water that heat supply water is used is warming up under the situation of the heat that desired water temperature needs from the primary coolant that water under high pressure heat exchanger 50, flows, the temperature of the primary coolant that in water under high pressure heat exchanger 50, flows still is in the temperature range of the secondary refrigerant that the ability heating uses.Therefore; In the good scope of the running efficiency that can make heat pump circuit 10; The heat of the primary coolant that can in as the second water under high pressure heat exchanger 52 of the part of water under high pressure heat exchanger 50, flow effectively utilizes, so that the secondary refrigerant that heats usefulness is heated.By this, when the running efficiency that makes heat pump circuit 10 is good, can effectively be utilized in the heat of the primary coolant that flows in the water under high pressure heat exchanger 50.

In addition; For example; If the water that secondary refrigerant that further heating is used in water under high pressure heat exchanger 50 after wanting in middle setting-out heat exchanger 40, to heat or heat supply water are used; Then, therefore can't fully effectively utilize the heat that primary coolant had that in water under high pressure heat exchanger 50, flows owing to will flow into the secondary refrigerant that heats usefulness of water under high pressure heat exchanger 50 or water that heat supply water is used is heated.That is, can't on mollier diagram, fully obtain enthalpy change in the exothermic process of primary coolant.Likewise; When the water of wanting in water under high pressure heat exchanger 50 heating back secondary refrigerant that heating is used in middle setting-out heat exchanger 40 or heat supply water to use, the water that the secondary refrigerant that heats usefulness of setting-out heat exchanger 40 or heat supply water are used in flowing into is heated.Therefore, the heat that primary coolant had that flows in the setting-out heat exchanger 40 in can't being utilized in fully sometimes, and the feasible running efficiency that improves the heat pump circuit 10 of multi-stage compression form becomes difficult.

Relative therewith; In the heat pump 1 of first embodiment; In heat pump circuit 10; Secondary refrigerant in radiator 61, being cooled is cut apart, to be divided into heating of in through medium voltage side fork stream 67, in middle setting-out heat exchanger 40, carrying out and the heating of in through high-pressure side fork stream 68, in the second water under high pressure heat exchanger 52, carrying out.By this, the setting-out heat exchanger 40 and the second water under high pressure heat exchanger 52 during not heated as yet secondary refrigerant was supplied to after ability will be cooled in radiator 61.By this, when the cooling effect of the primary coolant that senior side compressor 25 is sucked improves, can fully effectively utilize the heat of the primary coolant that in middle pressure pipe 23, flows.

< 2>second embodiments

As shown in Figure 4; The heat pump 201 of second embodiment is that bypass pipe 80 (the 14 high-voltage tube 27n, bypass expansion valve 5b, the 6th low-voltage tube 20f) is not set in the heat pump 1 of first embodiment, but makes the primary coolant of circulation all pass through the system of heat exchanger 8 between primary coolant.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

When being in the primary coolant that makes in heat pump circuit 10 circulation and all between primary coolant, carrying out heat exchange in the heat exchanger 8 and also be not easy the environment for use of the problem on generation ability and the efficient; Can not only reduce component count, also need not control bypass expansion valve 5b one time.

< 3>the 3rd embodiments

As shown in Figure 5, the heat pump 301 of the 3rd embodiment be do not carry out primary coolant to the injection of middle pressure pipe 23 but the cooling that makes the primary coolant that flows at pressure pipe 23 all in system that setting-out heat exchanger 40 carries out.Promptly; The heat pump 301 of the 3rd embodiment be economizer heat exchanger 7 be not set, inject stream 70 (injecting expansion valve 73, first ascending pipe 72, second ascending pipe 74, the 3rd ascending pipe 75, the 4th ascending pipe 76), the 8th high-voltage tube 27h, the 9th high-voltage tube 27i in the heat pump 1 of first embodiment, the tenth high-voltage tube 27j, the 3rd presses pipe 23e and the 4th to press pipe 23d, but the system that presses pipe 323c and the 38 high-voltage tube 327h in the 33 is set.Press pipe 323c to press pipe 23b to be connected in second in the middle setting-out heat exchanger 40 in the 33 with the suction side of senior side compressor 25.The 38 high-voltage tube 327h is connected the 6th high-voltage tube 27f in the 3rd water under high pressure heat exchanger 53 with the 4th high pressure spot I.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 301, the cold-producing medium that can avoid senior side compressor 25 to suck is cooled into the such state of dampness, and component count can be controlled to such an extent that reduce and loop structure is oversimplified.

In addition; In above-mentioned heat pump 301; Do not inject stream 70 owing to be provided with; Therefore; Even through in the temperature of primary coolant of setting-out heat exchanger 40 excessively reduce because of the unified control of secondary refrigerant temperature, can not become in the scope of dampness yet the amount of the primary coolant that flows towards water under high pressure heat exchanger 50 is increased at the primary coolant that advanced compression machine 25 sucks.

< 4>the 4th embodiments

As shown in Figure 6, the heat pump 401 of the 4th embodiment is to be configured in the system in economizer heat exchanger 7 downstreams to the fork that injects stream 70 sides.Promptly; The heat pump 401 of the 4th embodiment is in the heat pump 1 of first embodiment, the 43 high pressure spot 4H, the 47 high-voltage tube 427g, the 48 high-voltage tube 427h, the 49 high-voltage tube 427i, the 410 high-voltage tube 427j to be set respectively, to replace the system of the 3rd high pressure spot H, the 7th high-voltage tube 27g, the 8th high-voltage tube 27h, the 9th high-voltage tube 27i, the tenth high-voltage tube 27j.The 43 high pressure spot 4H is set in place in economizer heat exchanger 7 downstreams on the flow direction of the primary coolant of heat pump circuit 10 and is positioned at the position of the 4th high pressure spot I upstream side, and injection stream 70 diverges out on the 43 high pressure spot 4H.The 47 high-voltage tube 427g is connected the 6th high-voltage tube 27f in the 3rd water under high pressure heat exchanger 53 with economizer heat exchanger 7 the 48 interior high-voltage tube 427h.The 49 high-voltage tube 427i is connected the 48 high-voltage tube 427h in the economizer heat exchanger 7 with the 43 high pressure spot 4H.The 410 high-voltage tube 427j is connected the 43 high pressure spot 4H with the 4th high pressure spot I.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 401; Compare with the primary coolants that injection stream 70 at the heat pump 1 of first embodiment flows; Can make the temperature of the primary coolant that flows at injection stream 70 be in lower temperature, therefore, can make at the cooling effect that injects on the junction of two streams D and improve.

< 5-1>the 5th embodiment

As shown in Figure 7, the heat pump 501 of the 5th embodiment is a system of from the heat pump 1 of first embodiment, removing the 3rd water under high pressure heat exchanger 53.Promptly; The heat pump 501 of the 5th embodiment is the 52 heat supply hydro-thermal pump line 595b to be set replace the second heat supply hydro-thermal pump line 95b, the 3rd heat supply hydro-thermal pump line 95c, the 4th heat supply hydro-thermal pump line 95d in the heat pump 1 of first embodiment, and the system that the 55 high-voltage tube 527e replaces the 5th high-voltage tube 27e, the 6th high-voltage tube 27f, the 7th high-voltage tube 27g is set.At this, need be in the heat pump 1 of first embodiment employed heat supply water medium temperature sensor 95T.In addition, the 52 heat supply hydro-thermal pump line 595b is connected the upstream-side-end on the flowing of water that heat supply water is used of the 5th heat supply hydro-thermal pump line 95e in heat supply water pump 92 and the first water under high pressure heat exchanger 51.The 55 high-voltage tube 527e is connected the end of downstream side on the flow direction of primary coolant of the 4th high-voltage tube 27d in the second water under high pressure heat exchanger 52 with the 3rd high pressure spot H.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 501; For example; Even if being accumulated in the temperature of the water that the heat supply water in the heat storage water tank 91 use rises; The temperature ratio of the water that the detected heat supply water of heat supply water inflow temperature sensor 94T is used is through the high situation of temperature of the primary coolant of the outlet of the 4th high-voltage tube 27d in the second water under high pressure heat exchanger 52; Can be with the primary coolant heating of flowing, the not water cooling that heat supply water can be used towards the 3rd high pressure spot H yet.Therefore, under the less situation of heat supply water load, also can carry out efficient and turn round preferably.

The variation of < 5-2>the 5th embodiment

(A)

As shown in Figure 8; Can be on the basis of the heat pump 501 of above-mentioned the 5th embodiment; In the injection stream 470 that in using the 4th embodiment, illustrates, use above-mentioned the 55 high-voltage tube 527e to replace the 47 high-voltage tube 427g, to form heat pump 501A.

Under above-mentioned situation, can also obtain heat pump 401 similar effects with the 4th embodiment.

(B)

As shown in Figure 9; Also can be on the basis of the heat pump 501 of above-mentioned the 5th embodiment; As illustrated in the 3rd embodiment, remove and inject stream 70, and with the tie point of the 4th high pressure spot I as above-mentioned the 55 high-voltage tube 527e, to form heat pump 501B.

Under above-mentioned situation, can also obtain heat pump 301 similar effects with the 3rd embodiment.

(C)

As shown in figure 10, also can from the heat pump 501B of the variation (B) of above-mentioned the 5th embodiment, as second embodiment is illustrated, remove a bypass pipe 80, to form heat pump 501C.

Under above-mentioned situation, can also obtain heat pump 201 similar effects with second embodiment.

< 6-1>the 6th embodiment

As shown in figure 11, the heat pump 601 of the 6th embodiment is the system that stream 630 is injected in gas-liquid separation that on the basis of the heat pump 301 that does not have the 3rd embodiment that injects stream 70, is provided with.Gas-liquid separation inject stream 630 have separate before gas-liquid pipe 631, gas-liquid separator 632, separate back liquid line 633, separate back flue 634, separate back flue open and close valve 635 and gas-liquid separation expansion valve 605.Gas-liquid pipe 631 extends to the gas-phase space of gas-liquid separator 632 tops before separating from the 3rd low pressure point M.Gas-liquid separator 632 will separate into the vapor phase areas that is in superjacent air space and be in the liquid phase zone of side space down from the primary coolant that separates preceding gas-liquid pipe 631 inflows.The primary coolant that separation back liquid line 633 will be present in the liquid phase zone of gas-liquid separator 632 guides to gas-liquid separation expansion valve 605.In gas-liquid separation expansion valve 605, the pressure of the primary coolant of process is further descended.The primary coolant that separation back flue 634 will be present in the vapor phase areas of gas-liquid separator 632 guides to injection junction of two streams D.Separating back flue open and close valve 635 can switch between the state that allows to separate the primary coolant process in the flue 634 of back and the state that does not allow to separate the primary coolant process in the flue 634 of back.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 601, the decompression of the primary coolant among expansion valve 5a and/or the bypass expansion valve 5b be reduced to flow through in press the primary coolant of pipe 23 to equate the low pressure of ratio critical pressure, thereby become the gas-liquid two-phase state.Wherein, aqueous primary coolant is reduced to the pressure of the primary coolant that in low-voltage tube 20, flows in gas-liquid separation expansion valve 605.In addition, extend from the vapor phase areas of gas-liquid separator 632 owing to separate back flue 634, therefore liquid primary coolant is difficult for sneaking into and separates back flue 634, flow therein be the primary coolant of gaseous state.By this, injecting on the junction of two streams D and after the primary coolants interflow that pressure pipe 23 flows, supplying the primary coolant of senior side compressor 25 suctions to be difficult for becoming moisture state.By this, the refrigerant density that can not only increase senior side compressor 25 suctions is raised the efficiency, and can also prevent in senior side compressor 25, liquid to be compressed.In addition, in the decompression of the primary coolant in expansion valve 5a, can not drop to the pressure of the primary coolant that in low-voltage tube 20, flows, and only can drop to the degree of the pressure of the primary coolant that in middle pressure pipe 23, flows.Therefore, can suppress to reduce situation about possibly in senior side compressor 25, compress to liquid because of the excessive temperature of primary coolant mobile in the flue after separation 634.In addition; Even through in the temperature of primary coolant of setting-out heat exchanger 40 excessively reduce because of the unified control of secondary refrigerant temperature, can in the primary coolant that supplies senior side compressor 25 to suck can not become the scope of moisture state, the amount of the primary coolant that flows towards water under high pressure heat exchanger 50 be increased yet.

The variation of < 6-2>the 6th embodiment

(A)

As shown in figure 12, also can be the heat pump 601A that forms as illustrated in the 5th embodiment, removing the 3rd water under high pressure heat exchanger 53 in the heat pump 601 of above-mentioned the 6th embodiment.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

< 7>the 7th embodiments

As shown in figure 13, the heat pump 701 of the 7th embodiment is that the position that in the heat pump 1 of first embodiment 1, will inject junction of two streams D changes the discharge side of the rudimentary side compressor 21 of connection and second first system of promptly injecting junction of two streams 7D midway that presses pipe 23a that presses the end of downstream side of pipe 23b in the setting-out heat exchanger 40 into.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 701; For example; When will be at the compression ratio that improves senior side compressor 25 so that when the discharging refrigerant temperature of senior side compressor 25 becomes target temperature; The compression ratio that equates with the compression ratio with this senior side compressor 25 improves when driving efficient rudimentary side compressor 25 runnings, and the discharging refrigerant temperature that has a rudimentary side compressor 21 is for heating too high situation for the secondary refrigerant of usefulness heated in the middle setting-out heat exchanger 40.Even if this situation is arranged on the first pressure pipe 23a midway through injecting junction of two streams 7D, just can heat excessive rising with the temperature of secondary refrigerant.

In addition; In above-mentioned heat pump 701; After the primary coolant that comes through injecting stream 70 collaborates on injection junction of two streams D; Through in temperature and the pressure of senior side compressor 25 behind the setting-out heat exchanger 40 primary coolant that will suck hold by control part 11 as senior suction pressure sensor 24P and the senior detected value of inlet temperature sensor 24T; Thereby can control, be in moisture state with the primary coolant that suppresses senior side compressor 25 suctions.

< 8>the 8th embodiments

As shown in figure 14, the heat pump 801 of the 8th embodiment is the system with the reversed of heat exchanger 8 between economizer heat exchanger 7 in the heat pump 1 of first embodiment and primary coolant.Promptly; The heat pump 801 of the 8th embodiment is the 83 pressure point 8H that is arranged in the 3rd low pressure point M downstream to be set replace the 3rd high pressure spot H of the heat pump 1 of first embodiment, and makes the system of stream 870 from the 83 pressure point 8H fork of injecting.The 810 high-voltage tube 827j is connected the end of downstream side of the 6th high-voltage tube 27f in the 3rd water under high pressure heat exchanger 53 with the 4th high pressure spot I.The 87 high-voltage tube 827g is connected pressure point 8H among the 3rd low pressure point M and the 83.The 88 high-voltage tube 827h is connected the upstream-side-end of the 89 high-voltage tube 827i in pressure point 8H in the 83 and the economizer heat exchanger 7.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 801, between primary coolant, in the heat exchanger 8, can utilize by the primary coolant of the comparative heat before economizer heat exchanger 7 coolings primary coolant that supplies rudimentary side compressor 21 to suck is heated.By this; Even through in the temperature of primary coolant of setting-out heat exchanger 40 excessively reduce because of the unified control of secondary refrigerant temperature, can not become in the scope of moisture state yet the amount of the primary coolant that flows towards water under high pressure heat exchanger 50 is increased at the primary coolant that senior side compressor 25 sucks.

< 9>the 9th embodiments

As shown in figure 15, the heat pump 901 of the 9th embodiment is the system that the water in the second water under high pressure heat exchanger 52 of the heat pump 1 of first embodiment, also heat supply water used heats.Promptly; The heat pump 901 of the 9th embodiment is the 4th heat supply hydro-thermal pump line 95d that is provided with respectively in the heat pump 1 that the 95 upper reaches tube connector 995x, the 95 heat supply hydro-thermal pump line 995d and the 95 downstream tube connector 995y replace first embodiment, and is provided with that the upper reaches that the temperature to the water used through the heat supply water of the 95 upper reaches tube connector 995x detects connect temperature sensor 95Tx and the downstream that the temperature of the water used through the heat supply water of the 95 downstream tube connector 995y detects is connected the system of temperature sensor 95Ty.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 901; For example; In the second water under high pressure heat exchanger 52; Because the water that the heat supply water that in the 95 heat supply hydro-thermal pump line 995d, flows is used can absorb the heat that the secondary refrigerant of pining for that heats usefulness that among the fork stream 68b of second high-pressure side, flows of emitting from the 4th high-voltage tube 27d can't absorb fully, so the loss of the heat that will emit from the 4th high-voltage tube 27d of ability suppresses to such an extent that lessly effectively utilize.In addition, owing to be provided with the part of the heat that water that the secondary refrigerant that heats usefulness and heat supply water uses obtains primary coolant simultaneously and had, therefore can make the water that heat supply water is used be heated to the size compactness of the required heat exchanger of desired water temperature.

< 10>the tenth embodiments

As shown in figure 16, the heat pump 1x of the tenth embodiment removes heat supply water loop 90 and the system of formation from the heat pump 1 of first embodiment.Promptly; The heat pump 5x of the 14 embodiment is the first water under high pressure heat exchanger 51, the 3rd water under high pressure heat exchanger 53 and the heat supply water loop 90 of removing in the heat pump 1 of first embodiment; The 14 upper reaches high-voltage tube 127a is set replaces the first high-voltage tube 27a, the second high-voltage tube 27b and the 3rd high-voltage tube 27c, and the system that the 14 downstream high-voltage tube 127e replaces the 5th high-voltage tube 27e, the 6th high-voltage tube 27f and the 7th high-voltage tube 27g is set.The 14 upper reaches high-voltage tube 127a is connected the upstream-side-end of the 4th high-voltage tube 27d in the discharge side of senior side compressor 25 and the second water under high pressure heat exchanger 52.The 14 downstream high-voltage tube 127e is connected the end of downstream side of the 4th high-voltage tube 27d in the second water under high pressure heat exchanger 52 with the 3rd high pressure spot H.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 5x,, also can obtain and the identical effect of above-mentioned first embodiment even without heat supply water loop 90 is set.

< 11-1>the 11 embodiment

As shown in figure 17; The heat pump 2x of the 11 embodiment makes the water that mobile heat supply water is used in heat supply water loop 90 in the heat pump 1 of first embodiment the same with the secondary refrigerant that heats usefulness; Not only carry out heat exchange, in middle setting-out heat exchanger 40, also carry out the system of heat exchange with primary coolant in water under high pressure heat exchanger 50 sides and primary coolant.That is, the heat pump 2x of the 11 embodiment comprise make through in primary coolant and the water that heat supply water is used of setting-out heat exchanger 40 carry out each other heat exchange second in setting-out heat exchanger 153.The second fork heat supply hydro-thermal pump line 195b extends to the end of downstream side of setting-out heat exchanger 153 in second after the fork midway of the second heat supply hydro-thermal pump line 95b.In second in the setting-out heat exchanger 153, make via the second fork heat supply hydro-thermal pump line 195b flow into water that the heat supply water of the 3rd fork heat supply hydro-thermal pump line 195c uses with through in setting-out heat exchanger 40 backs flow into as a part of pressing pipe 23c in the 3rd the 11 in press the primary coolant of pipe 123c to carry out heat exchange each other.The water of using through the heat supply water of the 3rd fork heat supply hydro-thermal pump line 195c in the setting-out heat exchanger in second 153 flow to fork heat supply water mixing valve 193 through the 4th fork heat supply hydro-thermal pump line 195d, and with through the 4th heat supply hydro-thermal pump line 95d and the hydration that the heat supply water that comes is used stream.The 5th heat supply hydro-thermal pump line 95e that the water that the heat supply water at interflow is used in fork heat supply water mixing valve 193 flowed in the first water under high pressure heat exchanger 51 through interflow heat supply water communicating pipe 196.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 2x; For example; When the temperature of the water that the heat supply water that goes out when 10 effluents from heat storage water tank 91 towards heat pump circuit is used is in temperature with running water and is the approaching state of normal temperature; Have following situation: even the primary coolant after in process, being cooled in the pressure pipe 23b in second in the setting-out heat exchanger 40; So long as in the scope that senior side compressor 25 can liquid towards compress, then its further cooling just can make the efficient raising.In this case; In the heat pump 2x of the 11 embodiment; Can not only heat at the cold water that water under high pressure heat exchanger 50 sides are used heat supply water, the heat of the primary coolant that flows between the suction side of the downstream of setting-out heat exchanger 40 and senior side compressor 25 in can also being utilized in comes the cold water that heat supply water is used is heated.

Through like this; Even there is the cycle efficieny such situation of variation a little that makes heat pump circuit 10 because of the unified control of above-mentioned secondary refrigerant temperature; Control part 11 also can be regulated the flow of the 4th fork heat supply hydro-thermal pump line 195d and the flow of the 4th heat supply hydro-thermal pump line 95d through further control fork heat supply water mixing valve 193, and suppresses the variation of the cycle efficieny of heat pump circuit 10 less.

For example; Thereby unified control reduces the cycle efficieny a little under the situation of variation that makes heat pump circuit 10 because of above-mentioned secondary refrigerant temperature at the flow of the medium voltage side of heating loop 60 fork stream 67; Control part 11 increases the flow of the 4th fork heat supply hydro-thermal pump line 195d through control fork heat supply water mixing valve 193, can suppress the variation of the cycle efficieny of heat pump circuit 10 less.

The variation of < 11-2>the 11 embodiment

(A)

In the heat pump 2x of above-mentioned the 11 embodiment; For example understand following situation: primary coolant from rudimentary side compressor 21 towards senior side compressor 25 flow in the pressure pipe 23; Not only carry out primary coolant and heat the heat exchange (middle setting-out heat exchanger 40) between the secondary refrigerant of usefulness, also carry out the heat exchange (setting-out heat exchanger 153 in second) between the water that primary coolant and heat supply water uses.

But the present invention is not limited to this, also can be the heat pump that can in the scope that does not change thought of the present invention, carry out following heat exchange.

For example; Also can adopt following mode: primary coolant from rudimentary side compressor 21 towards senior side compressor 25 flow in the pressure pipe 23; Primary coolant in the water under high pressure heat exchanger 50 of first embodiment and heat the secondary refrigerant of usefulness and water that heat supply water is used between heat exchange, carry out heat exchange in place, three places.In this case; Comparatively it is desirable to; The same with water under high pressure heat exchanger 50, the heat exchange that makes water that heat supply water uses and the primary coolant that in middle pressure pipe 23, flows separates in upstream side and these two places, downstream that secondary refrigerant that heats usefulness and primary coolant carry out heat exchange to be carried out.

(B)

In addition,, also can not carry out in the water under high pressure heat exchanger 50 and heat exchange primary coolant for the water that heat supply water is used, but primary coolant from rudimentary side compressor 21 towards senior side compressor 25 flow carry out heat exchange in the pressure pipe 23.

< 12>the 12 embodiments

As shown in figure 18, the heat pump 3x of the 12 embodiment is on the basis of the heat pump 1 of first embodiment, in heating loop 60, is provided with the system of bypass flow path.Promptly; The heat pump 3x of the 12 embodiment further is provided with to connect in the heating loop 60 of the heat pump 1 of first embodiment to heat the heating bypass bifurcation point Z midway that returns road pipe 66 and heat the heating bypass stream 69 of junction of two streams Y, and the 12 system that heats mixing valve 64 that heats in mixing valve 164 replacements first embodiment is set.Heat in the mixing valve 164 the 12, according to the indication of control part 11 regulate from heating bypass stream 69 flow the cold secondary refrigerant that heats usefulness that radiator 61, has just finished heat release that comes, via medium voltage side fork stream 67 flow come be heated after the secondary refrigerant that heats usefulness, via the high-pressure side diverge stream 68 mobile come be heated after the blending ratio of the secondary refrigerant that heats usefulness.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In the heat pump 1 of above-mentioned first embodiment, have following situation: even carried out the unified control of above-mentioned secondary refrigerant temperature, and carried out heat reduce handle after, still have heat above desired heat in the radiator 61 to radiator 61.In the heat pump 3x of the 12 embodiment; Even under the situation that the aforesaid heat that radiator 61 is applied will become superfluous, control part 11 also can heat mixing valve 164 and comes regulating towards heating junction of two streams Y the heating with the flow of secondary refrigerant of coming of flowing in the heating bypass stream 69 through operating the 12.By this, can make temperature surpass the secondary refrigerant of desired temperature in the radiator 61 and finish in radiator 61 after the heat release that the secondary refrigerant of desired temperature mixes in the not enough radiator 61 of temperature.Heat in the mixing valve 164 the 12, control part 11 is regulated through the blending ratio of regulating them, so that the temperature of mixed secondary refrigerant becomes desired temperature in the radiator 61.

By this, can not only suppress 25 pairs of liquid of senior side compressor and compress, can also be to the secondary refrigerant of desired temperature in the radiator 61 supply radiators 61.

< 13>the 13 embodiments

As shown in figure 19; The heat pump 4x of the 13 embodiment is in the heat pump 1 of first embodiment, constitutes to make economizer heat exchanger 7 and the 3rd high pressure spot H be in the 3rd low pressure point and be bifurcated into flowing and system between the part that flows of a bypass pipe 80 to heat exchanger between primary coolant 8.That is, the heat pump 4x of the 13 embodiment be change the 4th high pressure spot I in the heat pump 1 of first embodiment into be positioned at the 3rd high pressure spot H upstream side and more lean on than the 3rd water under high pressure heat exchanger 53 downstream the 13 high pressure spot 13I, comprise No. the 13 bypass pipe 80x and the 13 system of injecting stream 70x.The 7th high-voltage tube 127g is connected the end of downstream side of the 6th high-voltage tube 27f in the 3rd water under high pressure heat exchanger 53 with the 13 high pressure spot 13I.Bypass upper reaches energy-saving and high-pressure pipe 127n is connected the 13 high pressure spot 13I with the 3rd high pressure spot H.Bypass downstream energy-saving and high-pressure pipe 127j is connected to each other end of downstream side and a bypass expansion valve 5b of the 9th high-voltage tube 27i in the economizer heat exchanger 7.Because other structure is identical with the structure of above-mentioned first embodiment, therefore omit its explanation.

In above-mentioned heat pump 3x; For example; Because will be divided into the stream that cools off through economizer heat exchanger 7 towards the primary coolant that expansion valve 5a flows and through primary coolant between the stream that cools off of heat exchanger 8, therefore can regulate which stream to make primary coolant be cooled to which kind of degree with.

< 14>can be applicable to the variation of above-mentioned each embodiment

In above-mentioned first embodiment to the, 13 embodiments, each heat pump is specified.But the present invention is not limited to this, and the heat pump that in the scope of the thought that does not change invention, makes the heat pump of each embodiment become form as described below is also included among the present invention.

<14-1>

In above-mentioned each embodiment, for example understand the situation of carbon dioxide of using as primary coolant.

But in above-mentioned arbitrary embodiment, all can adopt the cold-producing medium outside the carbon dioxide is that ethene, ethane or nitrogen oxide etc. are as primary coolant.At this moment,, comparatively it is desirable to as the cold-producing medium that is adopted, use the discharging refrigerant pressure of senior side compressor 25 to surpass critical pressure and the driving force of each compressor can be suppressed less cold-producing medium.

<14-2>

In above-mentioned each embodiment, for example understand situation about in heating loop 60, making as the water circulation of secondary refrigerant.

But in above-mentioned arbitrary embodiment, secondary refrigerant is not limited to water, also can use salt solution as other thermal medium etc.

<14-3>

In above-mentioned each embodiment, for example understand the situation that is respectively equipped with rudimentary side compressor 21 and senior side compressor 25.

But, in above-mentioned arbitrary embodiment, also can be arranged on and adopt shared driving shaft in rudimentary side compressor 21 and the senior side compressor 25, be the compressing mechanism of a so-called two-stage or a multi-stage type.At this moment, through the phase difference of 180 degree is set, can improve driving efficient in each compressing mechanism.

<14-4>

In above-mentioned each embodiment, for example understand the situation that rudimentary side compressor 21 and senior side compressor 25 are connected in series.

But, also can in above-mentioned arbitrary embodiment, adopt the form that the compressing mechanism more than three is connected in series.At this moment, also can use the heat of the primary coolant that between each compressing mechanism, flows to carry out the heat load processing.In addition, as long as compressing mechanism is provided with the plural loop that is connected in series, further parallel connection or series connection are provided with other compressing mechanism.

<14-5>

In above-mentioned each embodiment, for example understand so that the situation that the consistent mode of desired temperature is controlled in the temperature of the secondary refrigerant that in the medium voltage side fork stream 67 of heating loop 60 and high-pressure side fork stream 68, flows and the radiator 61.

But, also can in above-mentioned arbitrary embodiment, optimization first priority desired heat in radiator 61 of the cycle efficieny in the heat pump circuit 10 be supplied with.In this case, can produce the situation of heat that make for the cycle efficieny of keeping heat pump circuit 10 well to the undersupply of radiator 61.At this moment; Also can be as shown in figure 20, be employed in from the downstream that comprises the 3rd high-pressure side fork stream 68c of heating loop 60 or comprise having the heat pump 5x that is used for the 60A of external heat source portion that the secondary refrigerant that heats usefulness to process heats between downstream to the radiator 61 of the 3rd medium voltage side fork stream 67c.At this moment; Even the variation of the variation that environment is set of evaporimeter 4, the variation that heats load or heat supply water load occurs; Can't be for the cycle efficieny of keeping heat pump circuit 10 well with to heat load corresponding; Also can be in the cycle efficieny of keeping heat pump circuit 10 well, with to heat load corresponding.Both the heat supply portion identical with the said external thermal source 60A of portion only can be arranged in the heat supply water loop 90, also it can be arranged on heating loop 60 and heat supply water loop 90 among both.

In addition, may produce the situation of heat that make for the cycle efficieny of keeping heat pump circuit 10 well to the excess supply of radiator 61.At this moment; Also can be as shown in figure 21, be employed in from the downstream that comprises the 3rd high-pressure side fork stream 68c of heating loop 60 or comprise having the heat pump 6x that is used for the external refrigeration source 60B of portion that the secondary refrigerant that heats usefulness to process cools off between downstream to the radiator 61 of the 3rd medium voltage side fork stream 67c.As the said external cooling source 60B of portion; For example also can utilize supply water fork valve 94B and 194 pairs of the fork streams that supply water to supply the part of the feed pipe 94 that the running water of outside normal temperature flows to establish bypass; And the running water through making normal temperature with carry out heat exchange each other heating the secondary refrigerant that heats usefulness that flows in the road pipe 65, carry out the cooling of managing secondary refrigerant mobile in 65 toward the road heating.At this moment; Even the variation of the variation that environment is set of evaporimeter 4, the variation that heats load or heat supply water load occurs; Can't be for the cycle efficieny of keeping heat pump circuit 10 well with to heat load corresponding; Also can be in the cycle efficieny of keeping heat pump circuit 10 well, with to heat load corresponding.In addition, under the situation of fork valve 94B that use to supply water, the heat that the hotwork that excessively applies through the secondary refrigerant with 10 pairs of heating loop 60 of heat pump circuit is used for heat supply water reclaims, and can also improve the efficient as heat pump.Both the heat supply portion identical with the said external cooling source 60B of portion only can be arranged in the heat supply water loop 90, also it can be arranged on heating loop 60 and heat supply water loop 90 among both.

<14-6>

In above-mentioned each embodiment, understand that for example the relation between the temperature of the desired temperature of water that the heat supply water that in the 6th heat supply hydro-thermal pump line 95f, flows that flows into heat accumulation water receptacle 91 in the radiator 61 of heating loop 60 in desired temperature, the heat supply water loop 90 uses and the primary coolant that in the middle setting-out heat exchanger 40 of heat pump circuit 10 or water under high pressure heat exchanger 50, flows not have the situation of qualification especially.

But; Also can be in above-mentioned arbitrary embodiment; The driving frequency of the valve opening of 11 couples of expansion valve 5a of control part, rudimentary side compressor 21 or the driving frequency of senior side compressor 25 etc. are controlled so that the temperature of the primary coolant that in middle setting-out heat exchanger 40, flows surpasses desired temperature in the radiator 61 of heating loop 60; And, realize the raising of the cycle efficieny of heat pump circuit 10 under the condition of prerequisite.In this case, setting-out heat exchanger 40 sides were the secondary refrigerant that heat that the secondary refrigerant of medium voltage side fork stream 67 1 side flow obtains produces desired temperature in the radiator 61 during heating loop 60 can only be utilized in.

<14-7>

In above-mentioned each embodiment, for example understand the situation that the compression ratio of rudimentary side compressor 21 is equated for the cycle efficieny that improves heat pump circuit 10 with the compression ratio of senior side compressor 25.

But, in above-mentioned arbitrary embodiment, be not necessarily limited to the compression ratio situation identical of rudimentary side compressor 21 with the compression ratio of senior side compressor 25, for example, also comprise the situation that the difference that is controlled to the compression ratio that makes both diminishes.

<14-8>

For example; Under the situation of the unified control of the secondary refrigerant temperature that in carrying out above-mentioned embodiment, illustrates; When being surpassed in the radiator 61 desired temperature by unified temperature, control part 11 is controlled to sometimes and increases the flow that heats pump 63 and shorten the time that can carry out heat exchange.But; Increase the flow that heats pump 63 in case be controlled to as stated; Primary coolant in the then middle setting-out heat exchanger 40 can be further cooled, and therefore, the degree of superheat of the primary coolant that senior side compressor 25 sucks is reduced or is in dampness.

In this case; Control part 11 for example can not change the target discharge temperature of rudimentary side compressor 21; Do not change the target discharge temperature of senior side compressor 25 yet, but the rudimentary suction degree of superheat control that the degree of superheat of the primary coolant that rudimentary side compressor 21 sucks is increased.

For example, shown in the dotted line in the mollier diagram of Figure 22, carry out the circulation of heat pump circuit 10, and the flow that heats pump 63 is increased.At this; Control part 11 is through carrying out rudimentary suction degree of superheat control; Do not changing the target discharge temperature of rudimentary side compressor 21, also do not changing under the situation of target discharge temperature of senior side compressor 25, the degree of superheat of the primary coolant that rudimentary side compressor 21 sucks is increased.By this, can shown in the solid line in the mollier diagram of Figure 22, carry out the circulation of heat pump circuit 10.At this, in the mollier diagram of Figure 22, suck on the point of primary coolant at senior side compressor 25, the circulation of dotted line is compared with the circulation of solid line, and the circulation of solid line is moved towards the direction away from saturated vaporline, and the degree of superheat increases.By this; Though the suction refrigerant density of rudimentary side compressor 21 reduces slightly; But; Even diminish because of the variation of the increase isoperimetric foxing spare that heats load makes the degree of superheat of the primary coolant that senior side compressor 25 sucks, the state of the primary coolant that senior side compressor 25 sucks also can be because of moving the state that the degree of superheat increases that is in towards the direction away from saturated vaporline.Therefore, in senior side compressor 25, be difficult for producing the situation that liquid is compressed.In addition, even carry out the circulation that solid line is represented in the Mollier line of Figure 22 as stated, the target discharge temperature of rudimentary side compressor 21 and the target discharge temperature of senior side compressor 25 do not change yet.Therefore, can also fully utilize in heating of carrying out of heat exchange in the setting-out heat exchanger 40 with the heating of secondary refrigerant and utilize the heating that heats that heat exchange in the water under high pressure heat exchanger 50 carries out with secondary refrigerant.In addition, owing to can reduce the compression ratio of the when senior side compressor 25 of compression of rudimentary side compressor 21 simultaneously, the efficient of heat pump circuit 10 is improved.

In addition; For example; In the heat pump circuit 10 with a bypass pipe 80 and a bypass expansion valve 5b in the heat pump shown in above-mentioned embodiment and the variation, above-mentioned rudimentary suction degree of superheat control is controlled through the valve opening of 11 couples of these bypass expansion valve 5b of control part and the degree that can regulate the heat exchange in the heat exchanger 8 between primary coolant.Like this, just can regulate the degree of superheat of the primary coolant of rudimentary side compressor 21 suctions.

<14-9>

In above-mentioned each embodiment, for example understand situation that the target discharge temperature of rudimentary side compressor 21 is identical with the target discharge temperature of senior side compressor 25 etc.

But; Also can be in above-mentioned arbitrary embodiment; The driving frequency of the driving frequency of 11 pairs of rudimentary side compressors 21 of control part, senior side compressor 25 and the valve opening of expansion valve 5a etc. are controlled, so that the target discharge temperature of rudimentary side compressor 21 is different with the target discharge temperature of senior side compressor 25.At this moment, also can make the rudimentary discharge temperature of the target discharge temperature reduction of rudimentary side compressor 21 reduce control.

For example, shown in the dotted line in the mollier diagram of Figure 23, carry out the circulation of heat pump circuit 10, and the flow that heats pump 63 is increased.At this; Control part 11 reduces control through carrying out rudimentary discharge temperature; The target discharge temperature of rudimentary side compressor 21 is descended; Thereby under the situation of the target discharge temperature that does not change senior side compressor 25; The flow of the secondary refrigerant that heats usefulness that in middle setting-out heat exchanger 40, flows is descended; Meanwhile, the flow of the secondary refrigerant that heats usefulness that in the second water under high pressure heat exchanger 52, flows is increased.At this, the target discharge temperature of rudimentary side compressor 21 is arranged in the radiator 61 of heating loop 60, below the desired temperature, for example, not be set to 65 ℃.By this, can shown in the solid line in the mollier diagram of Figure 23, carry out the circulation of heat pump circuit 10.At this, in the mollier diagram of Figure 23, suck on the point of primary coolant at senior side compressor 25, the circulation of dotted line is compared with the circulation of solid line, and the circulation of solid line is more moved towards the direction away from saturated vaporline, and the degree of superheat increases.By this; Even increase the degree of superheat of the primary coolant that makes senior side compressor 25 suctions diminishes because of the flow that heats pump 63; Because therefore the state of the primary coolant that senior side compressor 25 sucks also is difficult for producing the situation that liquid is compressed because of move the state that the degree of superheat increases that is in towards the direction away from saturated vaporline in senior side compressor 25.In addition, even carry out the circulation that solid line is represented in the Mollier line of Figure 23 as stated, the target discharge temperature of senior side compressor 25 does not change yet.In addition, though the target discharge temperature of rudimentary side compressor 21 descends, because the flow of the secondary refrigerant that heats usefulness of setting-out heat exchanger 40 descends too in the process, therefore can keep can the situation corresponding with load.In addition, owing to can reduce the compression ratio of the when senior side compressor 25 of compression of rudimentary side compressor 21 simultaneously, the efficient of heat pump circuit 10 is improved.

In addition, can for example valve opening, the driving frequency of rudimentary side compressor 21 and the driving frequency of senior side compressor 25 etc. of expansion valve 5a control and realize that above-mentioned rudimentary discharge temperature reduces control through 11 pairs of control parts.

<14-10>

In above-mentioned each embodiment, understand that for example the condition of the environment temperature environment of the employed radiator 61 of heat pump does not have special situation about limiting.

But; Also can be in above-mentioned arbitrary embodiment, will be in radiator 61 temperature of the secondary refrigerant after the heat release be in as the critical-temperature of the carbon dioxide of primary coolant and be the environment for use condition of heat pump than the such term restriction of temperature range condition between the lower temperature about low 5 degree of critical-temperature.

When under this environment for use, using heat pump, can be lower than as the heat load of the critical-temperature of the carbon dioxide of primary coolant with temperature and use accordingly.Therefore; Can in water under high pressure heat exchanger 50, be in above the primary coolant of critical pressure state and temperature than the heat exchange between the low secondary refrigerant of critical-temperature, carry out heat release in the zone that the isothermal inclination of primary coolant that can be on mollier diagram eases up and handle.Therefore, the exothermic process of primary coolant is begun and running that the enthalpy difference of exothermic process between finishing increases.

<14-11>

In above-mentioned each embodiment, even the flow-control that heats mixing valve 64 based on medium voltage side fork stream temperature sensor 67T and the high-pressure side detected temperature of fork stream temperature sensor 68T or heat pump 63 with control part 11 can't hold the 3rd medium voltage side fork stream 67c of heating loop 60 and the flow system that also it doesn't matter of the secondary refrigerant among the fork stream 68c of the 3rd high-pressure side is that example is illustrated.

But; Also can be in above-mentioned arbitrary embodiment; As shown in figure 24, adopt the heat pump 7x medium voltage side fork stream flowmeter 67Q that the flow of the secondary refrigerant that heats usefulness that in medium voltage side fork stream 67, flows is held is set respectively and the high-pressure side fork stream flowmeter 68Q that the flow of the secondary refrigerant that heats usefulness that in the fork stream 68 of high-pressure side, flows is held is replaced medium voltage side fork stream temperature sensor 67T and high-pressure side fork stream temperature sensor 68T.

In above-mentioned heat pump 7x; The flow that flow that control part 11 is held based on medium voltage side fork stream flowmeter 67Q and high-pressure side fork stream flowmeter 68Q are held; Come the flow that heats mixing valve 64 and/or heat pump 63 is controlled, so that the difference of the temperature of the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows and the temperature of the secondary refrigerant that heats usefulness that in the fork stream 68c of the 3rd high-pressure side, flows diminishes.In addition; Control part 11 is controlled, so that the temperature of the temperature of the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows and the secondary refrigerant that heats usefulness that in the fork stream 68c of the 3rd high-pressure side, flows becomes uniform temp.

Control part 11 comes the temperature of the primary coolant that flows in the setting-out heat exchanger 40 in being held in through middle pressure temperature sensor 23T, and comes the flow of the primary coolant that flows in the setting-out heat exchanger 40 in being held in through the detected temperatures of the driving frequency of rudimentary side compressor 21, middle pressure temperature sensor 23T and the detected pressures of senior suction pressure sensor 24P.In addition, control part 11 returns the road detected temperature of temperature sensor 66T and holds the temperature through the secondary refrigerant that heats usefulness of first medium voltage side fork stream 67a through heating.Control part 11 also comes the flow that is held in the secondary refrigerant that flows in the medium voltage side fork stream 67 through medium voltage side fork stream flowmeter 67Q.By this; Control part 11 is based on the primary coolant in the middle setting-out heat exchanger 40 and heat temperature difference and each flow between the secondary refrigerant of usefulness; Calculate the heat that secondary refrigerant obtained that heats usefulness, thereby calculate the value of anticipation as the temperature of the secondary refrigerant that heats usefulness of the stream 67c that diverges through the 3rd medium voltage side.

Control part 11 comes the temperature and the flow that are held in the primary coolant that flows in the second water under high pressure heat exchanger 52 according to the flow of the driving frequency of high pressure temperature sensor 27T, high-pressure sensor 27P and senior side compressor 25 etc. and heat supply water medium temperature sensor 95T and heat supply water pump 92 etc.In addition, control part 11 returns the road detected temperature of temperature sensor 66T and holds the temperature through the secondary refrigerant that heats usefulness of first high-pressure side fork stream 68a through heating.Control part 11 also comes the flow that is held in the secondary refrigerant that flows in the fork stream 68 of high-pressure side through high-pressure side fork stream flowmeter 68Q.By this; Control part 11 is based on the primary coolant in the second water under high pressure heat exchanger 52 and heat temperature difference and each flow between the secondary refrigerant of usefulness; Calculate the heat that secondary refrigerant obtained that heats usefulness, thereby calculate the value of anticipation as the temperature of the secondary refrigerant that heats usefulness of the stream 68c that diverges through the 3rd high-pressure side.

11 pairs of control parts heat mixing valve 64 and/or heat pump 63 and control, so that diminishing through the temperature of the secondary refrigerant that heats usefulness of the 3rd medium voltage side fork stream 67c and difference through the temperature of the secondary refrigerant that heats usefulness of the 3rd high-pressure side fork stream 68c of calculating as stated.As for here use calculated through the temperature of the secondary refrigerant that heats usefulness of the 3rd medium voltage side fork stream 67c with through the concrete control content of the temperature of the secondary refrigerant that heats usefulness of the 3rd high-pressure side fork stream 68c, then the content with explanation in the above-described embodiment is identical.

Like this; Even if the heat pump 7x of medium voltage side fork stream temperature sensor 67T and high-pressure side fork stream temperature sensor 68T is not set, also can make through the temperature of the secondary refrigerant that heats usefulness of the 3rd medium voltage side fork stream 67c and difference to diminish through the temperature of the secondary refrigerant that heats usefulness of the 3rd high-pressure side fork stream 68c.

<14-12>

In addition, as shown in figure 25, also can be that the heat pump 8x that high-pressure side fork stream flowmeter 68Q is set toward road flowmeter for pipe 65Q rather than as explanation in the above-mentioned variation < 14-11>is set.

Can hold through heating the flow of the secondary refrigerant that heats usefulness of pipe 65 toward road flowmeter for pipe 65Q toward the road.Even utilize above-mentioned medium voltage side fork stream flowmeter 67Q and past road flowmeter for pipe 65Q; Through deduct the flow that medium voltage side fork stream flowmeter 67Q is held from the flow that heats pipe 65 that can hold toward road flowmeter for pipe 65Q toward the road, just can be the flow that is held in the secondary refrigerant that heats usefulness that flows in the fork stream 68 of high-pressure side.Other control method and computational methods can be identical with above-mentioned variation < 14-11 >.

In addition, also can not be used for replacing high-pressure side fork stream flowmeter 68Q, but establish for replacing that low-pressure side fork stream flowmeter 67Q is set toward road flowmeter for pipe 65Q.

<14-13>

In addition, as shown in figure 26, also can be the heat pump 9x that the high-pressure side fork stream temperature sensor 68T that replaces in above-mentioned each embodiment, illustrating toward road pipe temperature sensor 65T is set.

Pipe temperature sensor 65T can hold through heating the temperature of the secondary refrigerant that heats usefulness of pipe 65 toward the road toward the road.Even if utilize above-mentioned medium voltage side fork stream temperature sensor 67T and pipe temperature sensor 65T toward the road; Calculate heating and manage the heat that secondary refrigerant had that heats usefulness mobile in 65 by manage 65 temperature toward the road according to heating of can holding toward road pipe temperature sensor 65T toward the road; And deduct the heat that secondary refrigerant had that heats usefulness that in medium voltage side fork stream 67, flows that the temperature held according to medium voltage side fork stream temperature sensor 67T obtains, just can be the heat that is held in the secondary refrigerant that heats usefulness mobile in the fork stream 68 of high-pressure side.In addition; When coming a temperature that is held in the secondary refrigerant that flows in the fork stream 68 of high-pressure side according to the heat of the secondary refrigerant of holding as stated that heats usefulness that in the fork stream 68 of high-pressure side, flows when being held in the flow of the secondary refrigerant that heats usefulness that flows in the high-pressure side fork stream 68.As for the control after the temperature of the temperature of having held the secondary refrigerant that heats usefulness that in medium voltage side fork stream 67, flows like this and the secondary refrigerant that heats usefulness that in the fork stream 68 of high-pressure side, flows, then can be identical with the content that in above-mentioned each embodiment, illustrates.

In addition, pipe temperature sensor 65T also can not be used for replacing high-pressure side fork stream temperature sensor 68T toward the road, but establishes for replacing that low-pressure side fork stream temperature sensor 67T is set.

In addition; Manage under the situation of temperature sensor 65T such being provided with as stated toward the road; Control part 11 can be to heating mixing valve 64 and heat pump 63 and control, so that the difference of the temperature of the secondary refrigerant that heats usefulness that the temperature of the detected secondary refrigerant that heats usefulness of pipe temperature sensor 65T and other temperature sensor (for example medium voltage side diverge stream temperature sensor 67T) are held toward the road diminishes.Even if this situation also can obtain and the identical effect of above-mentioned each embodiment.

<14-14>

In above-mentioned each embodiment, for example understand the unified situation of temperature that in the unified control of secondary refrigerant temperature, makes the secondary refrigerant that in the 3rd medium voltage side fork stream 67c and the 3rd high-pressure side fork stream 68c, flows.

But; The present invention all is not limited to the situation of completely unifying into identical temperature in above-mentioned arbitrary embodiment, also can be only to make the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows and the control that the difference of the temperature of mobile secondary refrigerant diminishes in stream 68c is diverged in the 3rd high-pressure side.

In addition; The difference of the temperature of the secondary refrigerant that also can not make the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows and in the fork stream 68c of the 3rd high-pressure side, flow diminishes; But control, be the condition below the setting to satisfy this temperature difference.

<14-15>

In above-mentioned each embodiment, for example understand situation about when carrying out the unified control of secondary refrigerant temperature, the flow rate ratio that heats in the mixing valve 64 being controlled.

But; In above-mentioned arbitrary embodiment; The difference that all is not limited to the temperature of utilizing the control heat the flow rate ratio in the mixing valve 64 to make the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows and the temperature of the secondary refrigerant that heats usefulness that in the fork stream 68c of the 3rd high-pressure side, flows such control that diminishes; For example, the present invention comprises that also control part 11 is by making the flow increase that heats pump 63 or the flow that heats pump 63 is reduced temperature that makes the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows and the situation that the difference of the temperature of the mobile secondary refrigerant that heats usefulness diminishes in the fork stream 68c of the 3rd high-pressure side.

For example; If the temperature of the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows is lower than the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows; And the primary coolant that in the second water under high pressure heat exchanger 52, carries out heat exchange is big with the temperature difference of the secondary refrigerant that heats usefulness with the temperature difference of the secondary refrigerant that heats usefulness is carried out heat exchange than in middle setting-out heat exchanger 40 primary coolant; Then control part 11 can also reduce temperature difference through reducing the control of the flow that heats pump 63.This is because following cause: at this moment; Though heating the flow of pump 63 because of reduction makes in any one heat exchanger all elongated from the time of primary coolant acquisition heat; But aspect the elongated temperature rising that causes of this time, what effect was bigger is the secondary refrigerant that heats usefulness through the bigger second water under high pressure heat exchanger, 52 1 sides of the temperature difference of primary coolant and secondary refrigerant.

In addition; If the temperature of the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows is higher than the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows; And the primary coolant that in the second water under high pressure heat exchanger 52, carries out heat exchange is big with the temperature difference of the secondary refrigerant that heats usefulness with the temperature difference of the secondary refrigerant that heats usefulness is carried out heat exchange than in middle setting-out heat exchanger 40 primary coolant; Then control part 11 can also reduce temperature difference through increasing the control of the flow that heats pump 63.This is because following cause: at this moment; Though the flow that heats pump 63 because of increase makes in any one heat exchanger from the time that primary coolant obtains heat and all shortens; But shorten aspect the temperature decline that causes in this time, what effect was bigger is the secondary refrigerant that heats usefulness through the bigger second water under high pressure heat exchanger, 52 1 sides of the temperature difference of primary coolant and secondary refrigerant.

In addition; If the temperature of the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows is lower than the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows; And the primary coolant that in the second water under high pressure heat exchanger 52, carries out heat exchange is little with the temperature difference of the secondary refrigerant that heats usefulness with the temperature difference of the secondary refrigerant that heats usefulness is carried out heat exchange than in middle setting-out heat exchanger 40 primary coolant; Then control part 11 can also reduce temperature difference through increasing the control of the flow that heats pump 63.This is because following cause: at this moment; Though the flow that heats pump 63 because of increase makes in any one heat exchanger from the time that primary coolant obtains heat and all shortens; But shorten aspect the temperature decline that causes in this time, what effect was bigger is the secondary refrigerant that heats usefulness through bigger middle setting-out heat exchanger 40 1 sides of the temperature difference of primary coolant and secondary refrigerant.

In addition; If the temperature of the secondary refrigerant that in the fork stream 68c of the 3rd high-pressure side, flows is higher than the temperature of the secondary refrigerant that in the 3rd medium voltage side fork stream 67c, flows; And the primary coolant that in the second water under high pressure heat exchanger 52, carries out heat exchange is little with the temperature difference of the secondary refrigerant that heats usefulness with the temperature difference of the secondary refrigerant that heats usefulness is carried out heat exchange than in middle setting-out heat exchanger 40 primary coolant; Then control part 11 can also reduce temperature difference through reducing the control of the flow that heats pump 63.This is because following cause: at this moment; Though heating the flow of pump 63 because of reduction makes in any one heat exchanger all elongated from the time of primary coolant acquisition heat; But aspect the elongated temperature rising that causes of this time, what effect was bigger is the secondary refrigerant that heats usefulness through bigger middle setting-out heat exchanger 40 1 sides of the temperature difference of primary coolant and secondary refrigerant.

<14-16>

In above-mentioned each embodiment, the situation that the relation between the temperature of the for example clear primary coolant that is not directed against the temperature of the primary coolant that in middle setting-out heat exchanger 40, flows especially and in the second water under high pressure heat exchanger 52, flows is controlled.

But; In above-mentioned arbitrary embodiment; For example; 11 pairs of heat supply water pumps 92 of control part are controlled; Thereby the temperature of regulating the primary coolant that flows into the second water under high pressure heat exchanger 52 through the flow of regulating the water of using through the heat supply water of the first water under high pressure heat exchanger 51 so that its with flow in the temperature of primary coolant of setting-out heat exchanger 40 approaching.

For example; The target discharge temperature of senior side compressor 25 is set than the high situation of the target discharge temperature of rudimentary side compressor 21 under; If do not reduce from the temperature of the primary coolant of senior side compressor 25 discharges, the inlet temperature of the primary coolant of the inlet temperature of the primary coolant of setting-out heat exchanger 40 and the second water under high pressure heat exchanger 52 is approaching in just can't making.In this case, control part 11 can be controlled heat supply water pump 92 based on the detected temperature of heat supply water medium temperature sensor 95T, to supply with the water that the required heat supply water of primary coolant cooling is used.

In this case; Near the temperature that is equivalent to heat near the inlet of temperature and the primary coolant of the second water under high pressure heat exchanger 52 of the outlet of the secondary refrigerant that is equivalent to heat the use inlet of primary coolant of middle setting-out heat exchanger 40 of outlet side of secondary refrigerant of use is close value; Therefore, make the temperature of the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows approaching easily with the temperature of the secondary refrigerant that heats usefulness that in the fork stream 68c of the 3rd high-pressure side, flows.For example, the flow that heats pump 63 is reduced under such situation, it is more easy that the unification of temperature becomes.In addition; Owing to make the temperature of the secondary refrigerant that heats usefulness that in the 3rd medium voltage side fork stream 67c, flows approaching easily, therefore can suppress lowlyer because of the unified degree of deterioration of controlling the cycle efficieny in the heat pump circuit 10 that causes of secondary refrigerant temperature with the temperature of the secondary refrigerant that heats usefulness that in stream 68c is diverged in the 3rd high-pressure side, flows.

<14-17>

In above-mentioned each embodiment, for example understand the situation of the control of not showing heat pump circuit 10 sides especially clearly.

Yet, unify control operational situation is changed though carry out secondary refrigerant temperature in the heating loop 60, also can suppress the variation of heat pump circuit 10 cycle efficienies sometimes or improve the cycle efficieny of heat pump circuit 10.

At this, for example, shown in the mollier diagram of Figure 27, for the situation of the target discharge temperature that heats the corresponding rudimentary side compressor 21 that raises of load under, the compression ratio in the rudimentary side compressor 21 have the tendency that becomes big (with reference to from dotted line to dashdotted variation).In addition, thereupon, want to make the compression ratio of the consistent senior side compressor 25 of compression ratio also can become big.Therefore, required driving force is increased, thereby make consumed energy increase.

To this, for example, shown in the mollier diagram of Figure 28, it is the circulation (with reference to from the variation of dotted line to solid line) of solid line from the varying cyclically of dotted line that control part 11 also can make operational situation.That is, when the target discharge temperature of rudimentary side compressor 21 rises, also can make the degree of superheat of the primary coolant of rudimentary side compressor 21 suctions become big rudimentary suction degree of superheat control.By this, can suppress lessly for the compression ratio of the needed rudimentary side compressor 21 of target discharge temperature of realizing rudimentary side compressor 21.Thereupon, also the compression ratio of senior side compressor 25 can be suppressed less.Thereby, can suppress required driving force littler.

In addition, so that the mode that the target discharge temperature of rudimentary side compressor 21 descends changes under the situation of recurrent state the rudimentary suction degree of superheat control that the degree of superheat of the primary coolant that rudimentary side compressor 21 sucks is diminished.By this, can not only increase the compression ratio that suppresses senior side compressor 25 through the compression ratio that suppresses rudimentary side compressor 21 and increase, can also reduce the specific volume of the primary coolant of rudimentary side compressor 21 suctions.Therefore, when suppressing the compression ratio increase, can also guarantee internal circulating load, thereby ability is increased.

In addition; For example; In the heat pump circuit 10 with a bypass pipe 80 and a bypass expansion valve 5b in the heat pump shown in above-mentioned embodiment and the variation, above-mentioned control is controlled through the valve opening of 11 couples of these bypass expansion valve 5b of control part and the degree that can regulate the heat exchange in the heat exchanger 8 between primary coolant.Like this, just can regulate the degree of superheat of the primary coolant of rudimentary side compressor 21 suctions.

<14-18>

At this; For example; Because of heating that load diminishes etc. that the temperature that makes the secondary refrigerant that in radiator 61, heats usefulness descends but under so much situation that do not descend, the temperature that has the primary coolant that in middle setting-out heat exchanger 40, flows need not become the situation of high temperature.

To this, for example, shown in the mollier diagram of Figure 29, it is the circulation (with reference to from the variation of dotted line to solid line) of solid line from the varying cyclically of dotted line that control part 11 also can make operational situation.That is, also can control, so that the reduction of the target discharge temperature of rudimentary side compressor 21, and the degree of superheat of the primary coolant of rudimentary side compressor 21 suctions is also reduced.By this, can make the compression ratio of senior side compressor 25 and the compression ratio of rudimentary side compressor 21 is same degree, thus can carry out driving force with low-pressure side compressor 21 and senior side compressor 25 suppress less so effective running.In addition, even the target discharge temperature of rudimentary side compressor 21 is descended, because desired heat load is less in radiator 61, therefore also can be corresponding with load.By this, can not only be corresponding with load change, compressible drive power is further reduced.

Utilizability in the industry

Heating combined equipment of the present invention be owing to can make cycle efficieny improve in the processing of the heat load of being undertaken by secondary refrigerant, and it is particularly useful that therefore the heat pump circuit that has a multi-stage compression formula compressing member for employing is handled the heat pump of heat load.

(symbol description)

1 heat pump

4 evaporimeters

The 4f fan

The 5a expansion valve

Bypass expansion valve of 5b

7? Economizer heat exchanger (Japanese: Eco Bruno ma イザ heat exchanger)

Heat exchanger between 8 primary coolants

10 heat pump circuit

20 low-voltage tubes

20a～20f first low-voltage tube～the 6th low-voltage tube

The 20P low-pressure sensor

20T low pressure temperature sensor

21 rudimentary side compressors

Press pipe in 23

Press among 23a～23d first and press pipe in the pipe～the four

Press temperature sensor among the 23T

The senior suction pressure sensor of 24P

The senior inlet temperature sensor of 24T

25 senior side compressors

27 high-voltage tubes

27a～27n first high-voltage tube～the 14 high-voltage tube

27P high-pressure sensor

27T high pressure temperature sensor

Setting-out heat exchanger in 40

50 water under high pressure heat exchangers

51～53 first water under high pressure heat exchangers～the 3rd water under high pressure heat exchanger

60 heating loop

61 radiators

61T radiator temperature sensor

62 diversion mechanisms (first flow governor motion)

63 heat pump (flow control division)

64 heat mixing valve

65 heat the pipe toward the road

65T is the pipe temperature sensor toward the road

65Q is flowmeter for pipe toward the road

66 heat and return road pipe

66T heats and returns the road temperature sensor

67 medium voltage sides fork stream

67T medium voltage side fork stream temperature sensor

67Q medium voltage side fork stream flowmeter

67a～67c first medium voltage side fork stream～the 4th medium voltage side fork stream

68 high-pressure sides fork stream

68T high-pressure side fork stream temperature sensor

68Q high-pressure side fork stream flowmeter

69 heating bypass streams (the first heat load bypass flow path)

70 inject stream

72 first ascending pipes

74 second ascending pipes

75 the 3rd ascending pipes

76 the 4th ascending pipes

73 inject expansion valve

No. 80 bypass pipes

90 heat supply water loops

91 heat storage water tanks

92 heat supply water pumps

93 heat supply water mixing valves

94 feed pipes

94T heat supply water inflow temperature sensor

95 heat supply hydro-thermal pump lines

95a～95f first heat supply hydro-thermal pump line～the 6th heat supply hydro-thermal pump line

95T heat supply water medium temperature sensor

98 heat supply water pipes

98T heat supply water leaving water temperature sensor

99 heat supply water bypass pipes

164 the 12 heat mixing valve (the first heat load bypass flow governor motion)

A sucks point

The rudimentary discharge point of B

The setting-out heat exchanger is through point among the C

D injects junction of two streams

The senior discharge point of E

F first high pressure spot

G second high pressure spot

H the 3rd high pressure spot

I the 4th high pressure spot

J the 5th high pressure spot

K first low pressure point

L second low pressure point

M the 3rd low pressure point

N the 4th low pressure point

Q injects pressure point

Point after the energy-conservation heat exchange of R

X heats bifurcation point

Y heats junction of two streams

W water supply bifurcation point

Z heat supply hydration flow point

The prior art document

Patent documentation

Patent documentation 1: Japanese Patent Laid is opened the 2004-177067 communique

Claims

1. a heat pump (1) is characterized in that, comprising:

Heat pump circuit (10), this heat pump circuit (10) supply the primary coolant circulation, and it has rudimentary side pressure contract mechanism (21), senior side pressure contract mechanism (25), expansion mechanism (5a, 5b) and evaporimeter (4) at least;

The first heat load loop (60); This first heat load loop (60) supplies first fluid circulation, and it has the first fork part (X), the second fork part (Y), connect the said first fork part (X) with the first fork stream (67) of the said second fork part (Y), be not connected the said first fork part (X) and second of the said second fork part (Y) diverge stream (68), the first heat load handling part (61) with said first fork stream (67) interflow;

First heat exchanger (40), this first heat exchanger (40) make from the contract discharge side of mechanism (21) of said rudimentary side pressure and carry out heat exchange each other towards contract the suction side said primary coolant that flows and the said first fluid that the said first fork stream (67), flows of mechanism (25) of said senior side pressure;

Second heat exchanger (52), this second heat exchanger (52) make from the said senior side pressure mechanism (25) of contracting and carry out heat exchange each other towards said primary coolant that said expansion mechanism (5) flows and the said first fluid that the said second fork stream (68), flows;

First flow governor motion (62), this first flow governor motion (62) can be regulated any at least side's in the flow of flow and the said first fluid in the said second fork stream (68) of the said first fluid in said first fork stream (67) flow; And

Control part (11), this control part (11) are operated the Flow-rate adjustment control of said first flow governor motion (62), thereby can;

Keep the state that satisfies the set point of temperature condition; Wherein, in the said set point of temperature condition temperature that comprises the said first fluid that in through the part of said first heat exchanger (40), flows in said first fork stream (67) and the said second fork stream (68) in through the part of said second heat exchanger (52) ratio of the temperature of mobile said first fluid be 1 situation; Or

In the temperature that makes the said first fluid that in through the part of said first heat exchanger (40), flows in said first fork stream (67) and the said second fork stream (68) in through the part of said second heat exchanger (52) difference of the temperature of mobile said first fluid diminish.

2. heat pump as claimed in claim 1 (1) is characterized in that,

Said control part (11) is controlled said rudimentary side pressure the contract output of mechanism (25) of mechanism (21) and said senior side pressure of contracting, thereby can:

Make the temperature of the said primary coolant that flows into said first heat exchanger (40) be the above temperature of the temperature of the said first fluid of said first heat exchanger of inflow (40); And,

Make the temperature of the said primary coolant that flows into said second heat exchanger (52) be the above temperature of the temperature of the said first fluid of said second heat exchanger of inflow (52); And,

Flow into said first heat exchanger (40) said primary coolant temperature and flow into said second heat exchanger (52) said primary coolant temperature both be the temperature more than the desired first heat load corresponding temperature in the said first heat load handling part (61).

3. heat pump as claimed in claim 2 (3x) is characterized in that,

The said first heat load loop (60) also has: the first heat load bypass circulation (69), and this first heat load bypass circulation (69) is connected the part between said first heat load handling part (61) and the said first fork part (X) with the said first heat load handling part (61) and said second part that diverges between the part (Y); And the first heat load bypass flow governor motion (164), this first heat load bypass flow governor motion (164) can be regulated the flow through the said first fluid of the said first heat load bypass circulation (69),

In said Flow-rate adjustment control; Said control part (11) is controlled; So that the desired value of the temperature of the said first fluid that in through the part of said second heat exchanger (52), flows in the desired value of the temperature of the said first fluid that in through the part of said first heat exchanger (40), flows in the said first fork stream (67) and the said second fork stream (68) is for surpassing the temperature of the said first heat load corresponding temperature

The said first heat load bypass flow governor motion (164) of said control part (11) operation is regulated the flow through the said first fluid of the said first heat load bypass circulation (69), is the said first heat load corresponding temperature so that be supplied to the temperature of the said first fluid of the said first heat load handling part (61).

4. heat pump as claimed in claim 2 (1) is characterized in that,

In said Flow-rate adjustment control; Said control part (11) is controlled, so that the desired value of the temperature of the said first fluid that in through the part of said second heat exchanger (52), flows in the desired value of the temperature of the said first fluid that in through the part of said first heat exchanger (40), flows in the said first fork stream (67) and the said second fork stream (68) is the said first heat load corresponding temperature.

5. like each described heat pump (1) in the claim 2 to 4, it is characterized in that,

In the control of said Flow-rate adjustment, said control part (11) to said rudimentary side pressure contract mechanism (21), said senior side pressure contract in mechanism (25) and the said expansion mechanism (5) any one is controlled at least, thereby can:

Keep the state that satisfies regulation compression ratio condition, wherein, said regulation compression ratio condition comprises that said rudimentary side pressure the contract ratio of the compression ratio in the mechanism (25) of compression ratio and said senior side pressure in the mechanism (21) that contracts is 1 situation; Or

Said rudimentary side pressure the contract difference of the compression ratio in the mechanism (25) of compression ratio and said senior side pressure in the mechanism (21) that contracts is diminished.

6. heat pump as claimed in claim 5 (1) is characterized in that,

Under the situation of carrying out said Flow-rate adjustment control; Contract the discharge temperature of said primary coolant of mechanism (21) when raising in said rudimentary side pressure, the rudimentary suction degree of superheat control that the degree of superheat of said control part (11) said rudimentary side pressure the is contracted said primary coolant that mechanism (21) sucks increases.

7. heat pump as claimed in claim 6 (1) is characterized in that,

Said heat pump circuit (10) also has heat exchanger between primary coolant (8); Heat exchanger between this primary coolant (8) said rudimentary side pressure is contracted said primary coolant that mechanism (21) sucks with carrying out heat exchange each other towards the said primary coolant that said expansion mechanism (5) flows afterwards through said second heat exchanger (52)

Heat exchanger (8) carries out said rudimentary suction degree of superheat control between the said primary coolant of said control part (11) use.

8. like each described heat pump (1) in the claim 5 to 7, it is characterized in that,

Under the situation of carrying out said Flow-rate adjustment control; When the temperature of the said first fluid that flows towards said first heat exchanger (40) and said second heat exchanger (52) from the said first heat load handling part (61) rises; Said control part (11) carries out controlling when load reduces; In when this load reduces, controlling; The contract desired value of discharge temperature of said primary coolant of mechanism (21) of said rudimentary side pressure is reduced, and reduce the contract degree of superheat of the said primary coolant that mechanism (21) sucks of said rudimentary side pressure.

9. heat pump as claimed in claim 8 (1) is characterized in that, also comprises:

The second heat load loop (90), this second heat load loop (90) supply the circulation of second fluid, and it has the said second heat load portion (91); And

The 3rd heat exchanger (51), the 3rd heat exchanger (51) make said second fluid of circulation in the said second heat load loop (90) and the said primary coolant of mechanism (25) towards said second heat exchanger (52) flows the way that contract from said senior side pressure carry out heat exchange each other.

10. heat pump as claimed in claim 9 (1) is characterized in that, also comprises:

The 4th heat exchanger (53), the 4th heat exchanger (53) make through in said second fluid in the said second heat load loop (90) from the said second heat load handling part (91) towards said second fluid that said the 3rd heat exchanger (51) flows with through said second heat exchanger (52) afterwards the said primary coolant towards said expansion mechanism (5) flows the way carry out heat exchange each other.

11. like claim 9 or 10 described heat pumps (1), it is characterized in that,

Contract than said senior side pressure under the low situation of the desired value of temperature of the said primary coolant that mechanism (25) discharges in the contract desired value of temperature of the said primary coolant that mechanism (21) discharges of said rudimentary side pressure; Said control part (11) is regulated the internal circulating load of said second fluid of circulation in the said second heat load loop (90), so that approach the contract desired value of temperature of the said primary coolant that mechanism (21) discharges of said rudimentary side pressure through the temperature of the said primary coolant of said the 3rd heat exchanger (51).

12. like each described heat pump (1) in the claim 9 to 11, it is characterized in that,

The said second heat load handling part (91) is the case (91) that heat supply water is used,

Said second fluid is the water that heat supply water is used.

13. like each described heat pump (1) in the claim 2 to 12, it is characterized in that,

In said Flow-rate adjustment control; Said control part (11) is through operation said first flow governor motion (62), makes that side's that temperature is lower among the temperature of the said first fluid that in through the part of said second heat exchanger (52), flows in temperature and the said second fork stream (68) of the said first fluid that in through the part of said first heat exchanger (40), flows in said first fork stream (67) flow decline.

14. heat pump as claimed in claim 13 (1) is characterized in that,

Said first flow governor motion (62) can be adjusted in the flow of the said first fluid that flows in the said first fork stream (67) and the ratio of the flow of the said first fluid that in the said second fork stream (68), flows,

In said Flow-rate adjustment control; Said control part (11) is through operation said first flow governor motion (62); Make the flow of the said first fluid that is supplied to the said first heat load handling part keep fixing, and make that side's that temperature is lower among the temperature of the said first fluid that in through the part of said second heat exchanger (52), flows in temperature and the said second fork stream (68) of the said first fluid that in through the part of said first heat exchanger (40), flows in the said first fork stream (67) flow rate ratio decline.

15. heat pump as claimed in claim 13 (1) is characterized in that,

Said first flow is regulated the flow that the said first fluid that is supplied to the said first heat load handling part (61) can be regulated in (62),

In said Flow-rate adjustment control; That side's that temperature is lower among the temperature of the said first fluid that in through the part of said second heat exchanger (52), flows in the temperature of the said first fluid that in through the part of said first heat exchanger (40), flows in said first fork stream (67) and the said second fork stream (68) flow rate ratio hour, said control part (11) is through operating the flow decline that said first flow governor motion (62) makes the said first fluid that is supplied to the said first heat load handling part (61).

16. heat pump as claimed in claim 13 (1) is characterized in that,

Said first flow governor motion (62) comprising: rate regulation portion (64), this rate regulation portion (64) are adjusted in the flow of the said first fluid that flows in the said first fork stream (67) and the ratio of the flow of the said first fluid that in the said second fork stream (68), flows; And flow control division (63), this flow control division (63) is regulated the flow of the said first fluid that is supplied to the said first heat load handling part (61),

In said Flow-rate adjustment control; Said control part; (11) through the said first flow governor motion of operation; (62); Make the said first fork stream; (67) passing through said first heat exchanger in; The temperature of the said first fluid that flows in the part (40) and the said second fork stream; (68) passing through said second heat exchanger in; The flow that surpasses that side of the said first heat load corresponding temperature among the temperature of the said first fluid that flows in the part (52) increases; And/or that side's of the not enough said first heat load corresponding temperature flow is reduced; And

Temperature at the said first fluid that is supplied to the said first heat load handling part (61) surpasses under the situation of the said first heat load corresponding temperature, and said control part (11) makes the flow of the said first fluid that is supplied to the said first heat load handling part (61) descend along with the rising of the temperature of the said first fluid that is supplied to the said first heat load handling part (61).

17. like each described heat pump (1) in the claim 1 to 16, it is characterized in that, also comprise:

The first fork stream detector unit (67T), this first fork stream detector unit (67T) is held the temperature of the said first fluid that in through the part of said first heat exchanger (40), flows in the said first fork stream (67); And

The second fork stream detector unit (68T), this second fork stream detector unit (68T) is held the temperature of the said first fluid that in through the part of said second heat exchanger (52), flows in the said second fork stream (68).

18. like each described heat pump (1) in the claim 1 to 16, it is characterized in that, also comprise:

Fork part detector unit (67T), any at least side in the temperature of the said first fluid that in the part of said second heat exchanger of process (52), flows in the temperature of the said first fluid that in through the part of said first heat exchanger (40), flows in the said first fork stream (67) of this fork part detector unit (67T) assurance and the said second fork stream (68); And

The temperature of the said first fluid that flows towards the said first heat load handling part (61) after interflow portion temperature detecting element (65T), this interflow portion temperature detecting element (65T) collaborate the said first fluid of the said second fork stream (68) of said first fluid that is held in the said first fork stream (67) of process and process.

19. like each described heat pump (1x) in the claim 1 to 16, it is characterized in that, also comprise:

The first fork stream flow detecting element (67Q), this first fork stream flow detecting element (67Q) is the flow that is held in the said first fluid that flows in the said first fork stream (67); And

The second fork stream flow detecting element (68Q), this second fork stream flow detecting element (68Q) is the flow that is held in the said first fluid that flows in the said second fork stream (68).

20. like each described heat pump (2x) in the claim 1 to 16, it is characterized in that, also comprise:

Branched portion shunt volume detecting element (67Q), this branched portion shunt volume detecting element (67Q) is any at least side in the flow of flow that is held in the said first fluid that flows in said first fork stream (67) and the said first fluid that in the said second fork stream (68), flows; And

Interflow partial discharge detecting element (65Q), this interflow partial discharge detecting element (65Q) is the flow that is held in after the said first fluid that flows in said first fork stream (67) and the said first fluid interflow of in the said second fork stream (68), the flowing towards the mobile said first fluid of the said first heat load handling part (61).

21. like each described heat pump (1) in the claim 1 to 20, it is characterized in that,

In said first heat exchanger (40); Be in flow relation towards contract the suction side said primary coolant that flows and the said first fluid that the said first fork stream (67), flows of mechanism (25) of said senior side pressure from the contract discharge side of mechanism (21) of said rudimentary side pressure

In said second heat exchanger (52), be in flow relation towards said primary coolant that said expansion mechanism (5) flows and the said first fluid that the said second fork stream (68), flows from the said senior side pressure mechanism (25) of contracting.

22. like each described heat pump (1) in the claim 1 to 21, it is characterized in that,

The said first heat load handling part (61) is heating with heat exchanger (61) of heating of the air to the object space that disposes this first heat load handling part (61),

Said first fluid is a secondary refrigerant.

23. like each described heat pump (1) in the claim 1 to 22, it is characterized in that,

Said rudimentary side pressure mechanism (21) and the said senior side pressure mechanism (25) of contracting of contracting has and is used for through driving said rudimentary side pressure mechanism (21) and the said senior side pressure shared rotating shaft that each spinning of mechanism (25) produces work done during compression of contracting of contracting.

24. like each described heat pump (1) in the claim 1 to 23, it is characterized in that,

In the control of said Flow-rate adjustment, will said senior side pressure the contract discharge pressure of mechanism (25) of said control part (11) is maintained the pressure more than the critical pressure of said primary coolant,

Said heat pump (1) is to use under the environment of the temperature below the critical-temperature of said primary coolant in the environment temperature of the said first heat load handling part (61).

25. like each described heat pump (1) in the claim 1 to 24, it is characterized in that,

Said primary coolant is a carbon dioxide.