FR2937411A1 - HEAT PUMP. - Google Patents

Abstract

The invention relates to a compressor protection kit (400) (7) for a heat pump (1) comprising a condenser (4), said kit (400) being upstream of the suction (30) of said compressor (7). ), and downstream of a regulator downstream of said condenser (4). It is characterized in that it comprises a circuit (400), passing through an evaporator (402), an exchange zone (408A) with a fan (408), and a condenser (401), before returning to the suction (30), and a secondary circuit (400B) of a fluid driven by a compressor (436), to the discharge (438) of which it successively traverses a branch (407) of exchange with said main circuit (400A), at level of said condenser (401), then an expander (405) controlled by a temperature sensor (406) at the suction (437) of said compressor (436), then passes through said evaporator (402) before returning to the suction of the compressor (436). The invention relates to a heat pump equipped with such a kit. The invention relates to a method for controlling the latter.

Description

The invention relates to a compressor protection kit, for air conditioning or heat pump system comprising, downstream of at least one such compressor, at least one condenser, at least one expander and at least one evaporator, said kit being designed adapted to be positioned upstream of the suction of said compressor, and downstream of a pressure reducer itself located downstream of said condenser. The invention also relates to a heat pump comprising such a kit and comprising, downstream of at least one compressor, at least one condenser, at least one expander and at least one evaporator. The invention also relates to a method for managing such a heat pump. The invention relates to the field of air conditioning by the use of a heat pump, in particular for buildings or ancillary equipment such as swimming pools or the like. In known manner, a heat pump is a thermodynamic device, which carries in closed circuit a fluid that will be called here heat transfer, generally consisting of a refrigerant, such as brine, CFC, HCHC, HFC such as R134a, HC such that propane R290 or isobutane R600A, or the like. The state change properties of this fluid are used, which, depending on its position in the circuit, changes from the liquid state to the gaseous state, or vice versa, and whose pressure also varies according to its position. The heat pump comprises means for setting the fluid in motion, which at the same time facilitates its change of state, in particular its pressure level: these means for moving the fluid generally consist of a compressor, receiving a fluid in the gaseous state and setting it in motion by increasing its pressure. These means for moving the fluid consume most of the energy provided by the user, mainly in electrical form, to operate the heat pump. The means for moving the fluid, in this case the discharge of the compressor, bring it to an exchanger called condenser, to which the circuit yields energy, and wherein the gaseous fluid put under high pressure under the action the compressor reaches its boiling temperature and condenses at high temperature by dissipation of heat, at constant pressure and temperatures, the temperature drop being then stopped. The latent heat of change of state is transmitted to the receiving medium, generally the useful volume of a building or dwelling, by the condenser.

The fluid is, at the outlet of the condenser, condensed entirely in liquid form under constant high pressure, at a so-called subcooling temperature. The fluid then circulates in an expansion circuit, which comprises in particular an expansion valve, which regulates the flow of the fluid downstream. Part of this fluid returns to the gaseous state, this transformation consumes energy and results in a lowering of the temperature of the fluid, conjugated with the lowering of its pressure. The expansion is at constant enthalpy, until the fluid enters another exchanger called evaporator, and whose circuit takes energy. It is again a transformation at constant pressure, this time at low pressure, unlike the exchange made at the condenser. The fluid absorbs the heat contained in the external medium, and boils, and the liquid vaporizes in gaseous form, in a state change process at constant pressure and temperature. When all of the fluid is evaporated, the latter is at a so-called overheating temperature. It is at constant low pressure and at this temperature of overheating that the fluid is brought to the suction of the compressor, and the cycle starts again indefinitely. We understand that the heat pump is a reversible tool, able to heat a room as well as cool: in the latter case we take energy from the building, we recede to the external environment with which the pump works. heat, air, water, soil, or other.

The coefficient of performance of a heat pump, or COP, is the ratio between the heat output collected at the user level at the condenser, and the power consumed.

The COP of a conventional heat pump is good, generally of the order of 3 to 5 at temperatures above 0 ° C., hereinafter referred to as positive, compared with 0.7 to 0.8 for an oil or gas boiler. gas. However, the efficiency varies according to the internal regulation of the heat pump, in particular the circulation parameters. The coefficient of performance also depends on the external temperature, that is to say on the source from which energy is taken. In case of very low external temperature, from -5 ° C to -15 ° C for example, the COP of a normal heat pump is strongly degraded. In fact, icing phenomena occur, which cause untimely stops, and require energy for deicing, both at the evaporator and the lower part of the compressor, causing further collateral corrosion damage and accelerated wear of equipment. At very low temperatures, the compression ratio decreases, the discharge temperature too, and the COP is degraded. In fact, the compressor motor always rotates at the same speed, and the mass flow rate of the fluid decreases at the discharge. This explains why, on such systems, a COP of a value of 3.5 under optimum conditions falls, for example for an outside temperature of -15 ° C, to values between 1 and 1.6 only. The limit of heat pumps is generally related to the compressor, which works in all or nothing: the heat pump necessarily operates in batch mode. During the operating periods of the compressor, the efficiency is good, the heating power produced and recoverable at the condenser increases with the outside temperature, with a COP that can be high, especially close to 6 for an outside temperature of 20 ° C, or 3 for an outside temperature of 7 ° C, during the operating range of the heat pump.

It must be stopped for periods longer or shorter, so as not to provide the use, that is to say, the condenser, more energy than the latter requires. On a day, the energy diagram produced as a function of time is therefore a histogram with many zero energy energy ranges. Thus, if the instantaneous COP is good, the smoothed COP over a period of operation is greatly degraded, for example of the order of 1 over a day, hardly better than a conventional fuel boiler.

Various attempts have been made to ensure stability of the COP, in particular to avoid peak power consumption of the compressor during startup: a known technology consists in varying the speed of the compressor, without ever stopping the latter. It is also known to convert direct current into alternating current, to convert it back into direct current during a transformation in which voltage and frequency are modulated in order to adapt the speed of rotation of the compressor, while avoiding variations in temperature at use. , and to regulate the energy output of the heat pump. Such a system currently has a COP greater than 4. However, the electronics is highly stressed and aging is fast, may require replacement in less than five years. At low temperature, the compression ratio rises, the discharge temperature increases, and the mass flow rate of the fluid is reduced, and the performance decreases. To cope with low outdoor temperature ranges, the known systems provide a heating supplement, or are oversized, which alters their profitability and performance. It is still known to inject, at the suction of the compressor, either a gas phase fluid, but a liquid-gas mixture, which makes it possible to obtain a lower discharge temperature, with a good COP level. However, the life of the compressor, which is the most expensive element of the heat pump, can not be equivalent to that of a gas-gas compressor, working in better conditions. All known devices incorporate a defrost cycle, which is essential especially for negative outside temperatures, of the order of -15 ° C for example. The present invention proposes to solve the problems of the state of the art, by proposing a heat pump capable of operating with good performance at low temperatures, insensitive to the phenomenon of icing and to reduce or even eliminate the cycles of defrost. By a design using conventional components, used in their usual operating range, the life of the heat pump according to the invention is optimized over the prior art. The invention consists in particular in optimizing the temperature differences between the inlet and the outlet of the evaporator, on the one hand, and the condenser, on the other hand, which, in the prior art, are not subject to a particular attention: it can thus have, in known systems, 10 to 15 ° C difference between input and output to the evaporator, and 10 to 15 ° C difference between input and output to the condenser, for example. However, such deviations are harmful, it can indeed be estimated that a difference of 1 ° C between the heat transfer fluid in gaseous form and the use fluid, generally constituted by water, at the condenser, results in an increase in energy consumption of the heat pump by around 2.5%. For this purpose, the invention relates to a compressor protection kit, for an air conditioning or heat pump installation comprising, downstream of at least one such compressor, at least one condenser, at least one expander and at least one evaporator, said kit being designed capable of being positioned upstream of the suction of said compressor, and downstream of a pressure reducer itself located downstream of said condenser, characterized in that it comprises a main circuit, which passes successively through at least one evaporator, at least one exchange zone with a fan, and at least one condenser, before returning to said suction, and that it comprises a secondary circuit, in which circulates a heat transfer fluid, set in motion by secondary means of set in motion constituted by at least one compressor, the discharge of which said secondary circuit successively traverses a heat exchange branch with said main circuit, at said condenser, and a pressure regulator controlled by a temperature sensor located at the suction of said compressor, then through said evaporator, which it recovers excess energy, before returning to the suction of the compressor. The invention also relates to a heat pump comprising such a kit and comprising, downstream of at least one compressor, at least one condenser, at least one expander and at least one evaporator, characterized in that it comprises first means heat exchanger located on another section than that separating said compressor from said condenser, for regulating the difference between the superheating temperature and the inlet temperature in said first evaporator on the one hand, and between the subcooling temperature and the inlet temperature in said condenser on the other hand. The invention also relates to a method for controlling such a heat pump.

Other features and advantages of the invention will appear on reading the description which follows, with reference to the appended figures in which: - Figure 1 shows, in schematic form, the main circuit of a heat pump according to l invention; FIG. 2 represents, in schematic form, a circuit complementary to the heat pump of FIG. 1; FIG. 3 represents a curve with the calorific power produced on the ordinate and the outside temperature on the abscissa; - Figure 4 shows, in schematic form similar to Figure 1, the main circuit of a heat pump in another embodiment; FIG. 5 illustrates, in schematic and partial form, a variant for preventing icing; - Figure 6 illustrates, in schematic and partial form, a variant with a heat exchanger contiguous with an evaporator that includes the heat pump according to the invention; - Figure 7 illustrates, in schematic and partial form, another variant with a heat exchanger contiguous with an evaporator that includes the heat pump according to the invention; - Figure 8 illustrates, in schematic and partial form, an exchange circuit upstream of a compressor that includes the heat pump according to the invention; FIG. 9 illustrates, in schematic and partial form, a compressor protection kit according to the invention; - Figure 10 illustrates, in schematic and partial form, a heat pump air conditioning circuit designed to be connected to the compressor protection kit of Figure 10, and in a first normal heating cycle position; FIG. 11 illustrates, in schematic and partial form, the circuit of FIG. 10 in a second deicing position; FIG. 12 illustrates, in schematic and partial form, an auxiliary circuit for energy recovery according to the invention; FIG. 13 illustrates, in schematic and partial form, a heating circuit designed capable of cooperating with the auxiliary circuit of FIG. 12; - Figure 14 illustrates, in schematic form, a dual circuit evaporator according to the invention. The invention relates to the field of air conditioning by the use of a heat pump. The air conditioning of a volume is provided by a circuit designed to operate reversibly, that is to say, both to bring thermal energy to the volume to be air-conditioned, than to extract. This description describes only one mode of operation, but it should be understood that all the features are applicable to reverse operation. It will be understood that an evaporator used to effect the change of state of a fluid from the liquid state to the gaseous state can reversibly operate in the reverse mode in the manner of a condenser. to effect the change of state from the gaseous state to the liquid state. It is the same for a condenser. The invention relates to a heat pump 1. This comprises a main circuit 2. The heat pump 1 comprises means for setting in motion 3 by suction and discharge, between a suction 30 and a discharge 31, a fluid coolant in a closed circuit circulation loop. The heat pump 1 further comprises, downstream of the discharge, and in this order, at least a first condenser 4, at least a first expander 5, and at least a first evaporator 6, before the return of the fluid to the suction 30 3. The means for setting in motion 3 consist of at least a first compressor 7, to push the fluid in the gaseous state and at high pressure towards at least the first condenser 4 where it enters an inlet temperature T1. The fluid leaves the first condenser 4 in the liquid state under constant high pressure, at a so-called subcooling temperature T2. This first condenser 4 exchanges the energy of the main circuit 2 which circulates there, with a first use circuit 8, for example a heating mixture bottle or a buffer tank. The first condenser is for example a plate heat exchanger, through which energy is transferred without contact from one circuit to another. The temperature of the first use circuit 8 at the inlet of the first exchanger 4 is T4, the outlet temperature is T3. Preferably, the first use circuit 8 comprises a circulator 9, designed capable of being controlled by control means 10, preferably constituted by a programmable controller or the like. The heat transfer fluid enters the first condenser 4 in the gaseous state, as will be explained later. At the outlet of the condenser 4, it is in the liquid state, or constituted by a liquid-gas mixture, and at the outlet temperature which is the temperature of change of state, that is to say the temperature of T2 subcooling. It should be noted that if, at this stage, the coolant consists of a liquid-gas mixture, this does not prevent the operation, but alters the efficiency of the installation. The control of the heat pump is done using temperature sensors, which act, upstream of the first condenser 4, on the control of a solenoid valve 13 whose operation will be explained later.

The pressure then brings the fluid, after passing through a filter 14, into an expansion circuit, which comprises at least the first expander 5 lowering the pressure and the temperature of the fluid, followed by a non-return valve 15, and a visual phase control indicator 16. The first expander 5 is a thermostatic expansion valve, controlled, mechanically and / or electronically by control means 10, by the temperature measured at a temperature sensor 5A located at or slightly downstream of a confluence 41 with a circuit of second heat exchange means 80 which will be explained later. The first expander 5 could also be controlled by the pressure instead of being controlled by the temperature. The fluid is then conveyed to at least the first evaporator 6, where the fluid enters the temperature T7, vaporizes and from which it comes out at low pressure and at a temperature T8 called overheating in gaseous form. The fluid is finally returned to the suction 30 of the means for setting in motion 3. Downstream of the expander 5, the coolant can be at a very low temperature, and it is important to avoid icing, both the pipes and the water. evaporator 6 located downstream.

The object of the invention is to obtain the best possible COP at any temperature, while preventing the icing of the evaporator 6, and in particular in case of very cold external temperatures, of the order of -15 ° C. In order to obtain a good yield, it is known that the temperature difference between the inlet temperature T4 and the outlet temperature T3 of the first condenser 4 must be on the primary circuit of use 8. less than 5 ° C, preferably less than or equal to 4 ° C. Optimally, the difference on the main circuit 2, between the inlet temperature T1 and the outlet temperature T2 of the first condenser 4, is of the same order. The ideal is to get T1 = T4, and T2 = T3. If this theoretical principle is known, its application is never satisfactorily performed in the prior art, and the invention proposes to provide the means to allow this optimal regulation. Similarly, the temperature difference between the inlet temperature T7 and the outlet temperature T8 of the first evaporator 6 should be maintained, if possible, less than 5 ° C, preferably less than or equal to 4 ° C. After passing through the expander 5, downstream of the indicator 16, the fluid reaches a bifurcation 17 distributing two branches, one of which comprises a solenoid valve 22, the object will be explained later. When the latter is closed, the flow of fluid passes entirely into the other branch, which comprises, advantageously but optionally, a fluid-proof bottle 18 essentially used to avoid noise when there is expansion of the gas in the case of the presence of a liquid-gas mixture in the pipe, then a filter 19, and essentially a second thermostatic expansion valve 20 controlled, mechanically and / or electronically by the control means 10, by the superheating temperature T8. Preferably, the expansion temperatures are adjusted at the first expander 5 and at the second expander 20, so that the first expander is greater than the second, by about 5 ° C. in a preferred heat pump setting. according to the invention.

If the temperature of the fluid at the inlet of the second thermostatic expansion valve 20 is less than T8, the latter remains closed, and does not allow the passage of the fluid. As a result, it rises in pressure. As soon as the temperature of the fluid reaches T8, the second expander 20 opens, the flow of fluid flows, downstream of the second expander 20, into a pipe branch, preferably provided with a non-return valve 21 and a pressure sensor 42, a branch that conveys the first fluid in the liquid state, or in the form of a liquid-gas mixture, and the energy that it carries, to the evaporator 6. The coolant is then liquid before entering the evaporator 6, or may comprise a gaseous fraction mixed with the liquid. The outside air, at a temperature T13, is sucked through a fan, and passes through the evaporator 6, from which it emerges at a temperature T14. In a preferred embodiment, the evaporator 6 is associated with a battery 27, that is to say a heat exchanger in which circulates another coolant or coolant, battery 27 which is disposed in the vicinity of the evaporator 6 and between which air flows through the fan 26 and charges thermal energy, or discharges, as appropriate. In this case, the outside temperature is the temperature T15 upstream of the battery 27, the passage on this battery 27 makes it possible to modify the temperature of the air flow to bring it to the temperature T13. The use of a battery 27 is advantageous in cold regions, for example for passing external air at a temperature T15 of -15 ° C to a temperature T13 of -10 ° C. An air temperature sensor associated with a probe and the management means 10 advantageously allows the control of the fan 26 and the battery 27. The fan 26 can be stopped or disengaged if necessary. The management means 10, associated with means for measuring the inlet temperature T7 and the outlet temperature T8 of the evaporator 6, make it possible in particular to regulate the fan 26 to maintain the difference between T8 and T7 less than 4 ° C.

In a particular embodiment, directly upstream of the evaporator 6, the circuit has an inlet 51, connected to a hot gas supplement circuit 52 to prevent icing of the evaporator 6 in very cold weather. Again, it is possible to insert a valve, not shown in the figures, controlled by the management means 10, to allow or not an energy supplement from the booster circuit 52. In an alternative or in addition, heating means 33, such as a resistor, can be implanted on the tubing. The booster circuit 52 can convey hot gas, or even liquid, and preferably the same heat transfer fluid as circulating in the heat pump, and from a reservoir or an external production means. Thus, downstream of the inlet 51, the vehicle circuit of the liquid fluid, or a liquid-gas mixture, at a temperature sufficient to prevent any icing downstream. The energy input makes it possible to act on the difference T8-T7, so as to limit it below the threshold of 5 ° C, preferably 4 ° C. This supplement made by the booster circuit 52 is useful, in particular, if the action on the fan 26 is not sufficient. In an alternative embodiment, the assembly consisting of a battery and a fan may be replaced by a plate heat exchanger, or the like. If, despite the regulation of the fan 26, and the back-up of the booster circuit 52 which might be insufficient or failing, the difference T8-T7 retains a value that is too high, it is still possible to incorporate, advantageously, a quilting 36 on the circuit between the moving means 3 and the first condenser 4, in a branch where the heat transfer fluid is in the gaseous state. This tapping 36 serves a solenoid valve 61 to discharge the fluid circuit, or on the contrary reload fluid by a booster circuit 62. The control of this solenoid valve can be made by the pressure level, or by the temperature level , measured at the tapping point 36. This provision provides another possible way to prevent icing. Preferably, a pressure sensor 63 is installed downstream of the stitching 36.

It may be advantageous to integrate in the circuit at least one evaporation pressure regulator 102, downstream of the evaporator 6. A solenoid valve 101 controlled by the temperature difference T7 - T8 allows the passage of fluid, either live if this temperature difference is less than 5 ° C, in which case the solenoid valve 101 is through, or in a branch with the evaporation pressure regulator 102, if this temperature difference is greater than 5 ° C, to which case the solenoid valve 101 is closed. The evaporation pressure regulator 102 is adjustable mechanically and / or electronically, typically 0.1 to 0.6 MPa, and keeps the evaporation pressure constant at this set value. According to the invention, the heat pump 1 also comprises first heat exchange means 11. These are situated on another section other than that separating the moving means 3 from the first condenser 4. These first means of heat exchange 11 are used to regulate the difference between the superheating temperature T8 at the outlet of the first evaporator 6, and the inlet temperature T7 in this first evaporator 6. These first heat exchange means 11 are still used to regulate the temperature. the difference between the subcooling temperature T2 at the outlet of the first condenser 4, and the inlet temperature T1 in the latter.

Indeed, the first heat exchange means 11 are designed to be able to bring or, on the contrary, remove energy from the main circuit 2. Different implantations of these first heat exchange means 11 are possible, and of course cumulative: - Preferably, between the first evaporator 6 and the moving means 3; between the first condenser 4 and the first evaporator 6; between the moving means 3 and the first condenser 4.

These first heat exchange means 11 can, in a preferred embodiment, exchange energy with complementary heat exchange means designed capable of exchanging energy with the moving means 3.

They can still exchange energy with complementary heat exchange means designed capable of exchanging energy with an auxiliary source or external discharge. In a preferred embodiment of the invention, the first heat exchange means 11 exchange energy with at least one element of the heat pump 1, and therefore do not require any external energy input. In particular, in a preferred variant, the first heat exchange means 11 exchange energy with means 12 for energy recovery at the level of the moving means 3. Advantageously, the means 12 of recovery of energy energy are constituted by an exchanger recovering the energy diffused at least by the first compressor 7. In other embodiments, these first heat exchange 11 exchange, at least partially, energy with external sources, preferably solar or the like. Downstream of the evaporator 6 at the superheating temperature T8, the fluid is in the gaseous state. In the embodiment of FIG. 2, the first heat exchange means 11 consist of an exchanger 70, preferably a double-flux plate heat exchanger, which allows a heat exchange between the main circuit 2 and a second circuit 71. a second heat transfer fluid. This second circuit 71 passes through the exchanger 70.

The variant of FIG. 6 incorporates a second heat exchanger 6A, incorporated between the heat exchanger 6 and a fan 26, and belonging to a secondary exchange circuit, comprising a circulator and also exchanging with the heat exchanger 11. The variant of FIG. 7 comprises the exchanger 11 contiguous with the evaporator 6, between the latter and a fan 26.

The main circuit 2 passes through the exchanger 70 and has, between its output and its input of the latter, a temperature difference ΔT, which is positive when the second circuit 71 brings thermal energy into the exchanger 70. can not obtain less than 5 ° C of gradient at the evaporator 6, it is necessary, for optimum operation, to obtain them between the inlet and the outlet of the exchanger 70. The further difference AT is high, and the power output of the first condenser 4 is high. However, the difference AT must remain less than or equal to 5 ° C, otherwise there is a risk of automatic safety high pressure of the compressor 7 that comprises the means of setting 3. It can indeed move into high pressure if the compressor discharge temperature is higher than the boiling temperature. The supply of energy by the second circuit 71 to the exchanger 70 is correlated with the temperature difference between the inlet and the outlet of the exchanger 70 at the second circuit 71. Different means of energy supply are possible: by energy recovery on the main circuit 2 itself, and / or by an external input by an intermediate booster circuit 72. In the latter case, a secondary energy source 73 is used, which can be of any kind, and preferentially solar, or consisting of a hydrogen battery, or classically electric or similar. This secondary source 73 advantageously supplies, through an exchanger 74 for heating a coolant, passing through the intermediate booster circuit 72, or feeds the latter directly in energy.

In an alternative embodiment, as shown in Figure 8, it is possible to replace the exchanger 74 with a hot water coil. Advantageously, a single flow VMC 74A is then used, with a fan whose piloting is not necessary. The water then recovers the energy of the ambient air.

In the auxiliary circuit, at the level of the exchanger 74, it is possible to use a hydrogen battery constituting the secondary source 73: by means of a frequency converter of the ac current of the sector, the frequency is increased to 33. kHz and the water molecules of a tank are exploded, generating hydrogen gas and gaseous oxygen, which can be burned by a burner 73A, generating a flame, such as that of a wall-mounted boiler gas for example. The use of such additional sources of energy makes it possible to envisage the production of electric current to power the compressor (s) 7.

The second circuit 71 may also include heat exchange means 75, with one or more members of the main circuit 2. Advantageously, according to the invention, these exchange means 75 cooperate with the means 12 for energy recovery. at the level of the moving means 3, consisting of one or more compressors 7, 7A, 7B, .... The intermediate booster circuit 72 and the exchange means 75 are advantageously connected according to the invention. 1 to the other, as shown in Figure 2. Preferably, since the exchanger 74, the fluid in the circuit 72 passes through, if the fluid is a liquid a circulator 76, then a three-way valve 77 which is controlled by a regulator, in particular the control means 10, the regulator itself controlled by the temperature difference between the inlet and the outlet of the exchanger 70 at the second circuit 71 and the external temperature of the building according to the law of water, p Uis crosses the exchanger 71. At the outlet of the latter, the secondary circuit 72 is divided into a branch connected to the valve 77, and in another a branch, designed able to communicate with the exchange means 75.

If the coolant in the secondary circuit 72 is a liquid, it is advantageously interchangeable, there is, in branch of the branch joining the exchange means 75, an expansion vessel 77. After crossing the exchange means 75, the secondary circuit 72 joins the exchanger 74.

In a preferred version of this alternative, the heat transfer fluid in the circuit 72 is compatible with the first heat transfer fluid, or even, in a preferred embodiment, is of the same nature as the latter. In this case, at the outlet of the exchange means 75, it is still possible to install a pipe communicating with the main circuit 2 and joining it between the exchanger 71 and the moving means 3. This energy recovery at the level of the means of setting in motion 3 makes it possible to prevent the passage of the first compressor 7 which comprises the latter in high pressure, as well as the associated degradation of the COP of the installation, which is defined as the ratio between the energy collected and the energy provided, which usually occur in such a case. Downstream of the exchanger 71, it is preferable, before the return to the suction 30 of the means of setting in motion 3, an anti-blow bottle of liquid 32 which makes it possible to avoid returning liquid to the compressor 7 , an activated carbon filter and dehydrator 33, as can be all the filters installed on the branches of the heat pump 1 where the fluid is in the gaseous state, and a visual control indicator 34 of state of the fluid .

In order to control at best the temperature T1 entering the fluid in the gaseous state into the first condenser 4, it is important to be able to bring it as close as possible to the inlet temperature T4 of the first use circuit 8 in the first condenser 4.

For this purpose, in a preferred embodiment, the heat pump 1 according to the invention comprises means for diverting a portion of the fluid flow, downstream of the moving means 3, and preferably downstream of the a pressure sensor 63, and upstream of the first condenser 4, to second heat exchange means 80. For this purpose, the heat pump 1 comprises at least two condensers arranged in parallel. In the example of Figure 1, used in the following description, they are two in number, and consist of the first condenser 4 and a second condenser 40. It is understood that it is possible, by implementing the same principle, to use a number of exchangers greater than two. A bypass, in the form of the thermostatic expansion valve 5, is implanted between the first condenser 4 and the second condenser 40. In the case where a bad exchange occurs in the condenser 4, the delivery pressure 31 of the delivery means in motion 3 increases. The second exchange means 80 allow the exchange of heat energy through the second condenser 40, between the main circuit 2 and a second use circuit 38, for example a hot water tank. The heat transfer fluid of the main circuit 2 enters the second condenser 40 in the gaseous state, at an inlet temperature T11, and leaves it in the liquid state, at the outlet temperature T12 equal to the subcooling temperature T2. Downstream or at a pressure sensor 63 itself located downstream of the moving means 3, and, if appropriate downstream of the tapping 36 for the connection of a booster circuit 62, the The temperature of the fluid, in the gaseous state, is measured by a temperature sensor 64. If the quality of the heat exchange at the first condenser 4 is poor, the pressure rises in the discharge circuit. A solenoid valve 13, controlled by a temperature sensor, makes it possible to divide the main circuit 2 into at least two branches, one through the first condenser 4, and one through the second condenser 40, to which the fluid preferably arrives after Crossed by a filter 37. Different temperature sensors can drive the solenoid valve 13, in particular the temperature sensor 64 drives the solenoid valve 13, to distribute the flow between the condensers 4 and 40. A preferred mode of control consists of preferentially load a branch of fluid, for example the branch serving the first condenser 4, and unload a portion of the flow to the second condenser 40, if the exchange in the first condenser 4 is poor. The piloting threshold chosen for the solenoid valve 13 is then the temperature in the circuit of the first condenser 4, and the activation threshold of the solenoid valve 13 is the condensation temperature Tc of the first heat transfer fluid: as long as the temperature in the the branch of the first condenser 4 is less than Tc, the flow passes entirely, and if this temperature is greater than Tc, the flow is shared in both branches. Preferably, the solenoid valve 13 is controlled by the difference between the temperatures T1 and T4, and remains closed as long as T1 is greater than T4.

Control means for controlling the solenoid valve 13 also make it possible to regulate the relative distribution of the flow between the branches of the first 4 and the second 40 condensers so that, in each of them, the temperature difference between the branch the outlet pipe of the condenser concerned and the corresponding input branch, is kept below 5 ° C, and preferably less than or equal to 4 ° C. Thus, in a manner analogous to the driving of the first condenser 4, the second condenser 40 is controlled so that the difference between the exit and exit temperatures T12 and T11 on the main circuit 2 of a on the other hand, and the difference between the outlet temperature T10 and input T5 on the exchange circuit with the second utilization circuit 38, on the other hand, is kept below 5 ° C., and preferably below or equal to 4 ° C. Preferably, it is arranged to adjust the temperatures so that T11 = T5, and T12 = T10. Preferably, the second utilization circuit 38 comprises a circulator 39, designed capable of being controlled by the control means 10. In the case where the solenoid valve 13 is open and allows the passage of fluid through the second condenser 40, the fluid in this branch joins, at the outlet of the latter, the confluence 41, and does not pass through the first thermostatic expansion valve 5, unlike the portion of the flow which has passed through the first condenser 4.

Advantageously, as can be seen in FIGS. 4 and 5, it is possible to incorporate a condensation pressure regulator 103, downstream of the second condenser 40, to maintain a constant and sufficiently high pressure in the second condenser 40 and in the associated reservoir 38. The condensation pressure regulator 103 is mechanically adjustable, typically 0.1 to 0.3 MPa. In short, the fluid is blocked between the second condenser 40 and the pressure regulator 103 until its pressure reaches the control set point level. In a variant, as can be seen in FIG. 5, a solenoid valve 104 is added directly downstream of the second condenser 40. This solenoid valve 104 makes it possible to prevent icing at the evaporator 6. The difference between the temperature of the evaporator 6 is measured. overheating T8 and the air outlet temperature T14, and it is compared with an adjustable threshold, preferably chosen from a value of 5 ° C: if the difference is smaller than this adjustable threshold, the solenoid valve 104 is closed, and if the difference is greater than this value, the solenoid valve 104 is passing. It is also possible, advantageously, to add downstream of this solenoid valve 104 an adjustable flow restrictor 105.

Downstream of the bifurcation 17, the solenoid valve 22 is closed during normal operation. In the event of risk of icing at the level of the pipes and / or the evaporator 6, its opening makes it possible to inject hot gas, without passing it through the thermostatic expansion valve 5. For this purpose, the solenoid valve 22 is controlled, mechanically and / or electronically, by the value of the difference T8-T7. If this difference is greater than 4 ° C, the solenoid valve 22 is opened. Downstream of the solenoid valve 22, a bifurcation 90 serves a first branch which joins the evaporator 6 after passing through a nonreturn valve 23, and a second branch comprising a solenoid valve 24. The latter makes it possible to shunt the evaporator 6 in case of malfunction of the latter, and the flow to join the main circuit at a confluence 91, downstream of the evaporator 6. The solenoid valve is controlled, preferably, by the value of the difference T9-T8. It can also be opened if one finds that T8 = T7, or that T4 = T3, which indicates anomalies on the circuit. The degradation of the COP of known heat pumps, in some areas of work, is due to the fact that either the compressor is continuously powered, or it is stopped and restarted, consuming energy peaks at restart. To improve this, according to the invention, the moving means 3 comprise at least two compressors arranged in parallel, including the first compressor 7.

These compressors 7, 7A, 7B, in the example of Figure 1, are connected in parallel, to avoid starting current peaks, only the first compressor 7 operating permanently. The operation is done in stages according to the demand, the flow control, that is to say the number of compressors, being made according to the temperature differences monitored, in particular T2-T1, T8-T7, T13- T14, T3-T4, T10-T5. For safety reasons, in order to avoid the passage of one of the compressors at high pressure, the gas temperature is kept below the operating limit threshold displayed by the compressor manufacturer, which is generally of the order of 100 ° C, and is safety advantageously kept below 15 ° C at this manufacturer's limit temperature. The compressor battery is advantageously surrounded by the energy recovery means 12. Circulation in the circuit or circuits exchanging energy with these energy recovery means 12 is regulated by the management means 10 so that the temperature at the compressors is higher than the critical temperature of condensation, to prevent any condensation in one of the compressors.

Downstream of each compressor, 7, 7A, 7B, on the discharge side, a check valve 35, 35A, 35B is advantageously installed, to avoid a thermal boiler effect of the compressor battery in the event of non-operation. from one of them. Preferably, the tubular diameter at the discharge 31 is greater than the suction diameter of the compressor battery.

According to a particular characteristic of the invention, at least one permanent magnet 95 is disposed on the path of the fluid to ionize it, between the means of movement 3 and the first condenser 4 and / or between the first expander 5 and the first evaporator 6. Preferably, the fluid is then selected or made electrically conductive. The management means 10 are designed able to regulate the fan 26, and / or circulation valves on the circuit of the first heat exchange means 11. They are still designed able to regulate the flow valves on the circuit of the means of heat exchange. complementary heat exchange. Figure 3 illustrates the advantages of the invention, for an example of installed power of 3.1 kVA at the compressor.

A conventional heat pump of the state of the art obeys, during its operating ranges, an increasing curve of the heating power supplied as a function of the external temperature, according to the EDT curve in broken lines. Obviously, the power supplied is zero when the compressor is stopped. The power supplied is maximum and the COP is maximum, of the order of 6, when the external temperature is too, but the need for power to use is felt when the external temperatures are low. Such a conventional heat pump still has a good COP, of the order of 3, at 7 ° C, but the situation deteriorates at -20 ° C, where the COP is very slightly greater than 1. The heat pump according to the invention has a heat supply curve supplied PCF, supplied to the first condenser 4 and the second condenser 40, which decreases as the temperature increases. The power consumed PC is the total, on the one hand of the power consumed at the level of the compressors 7, 7A, 7B, which decreases when the temperature increases since it is possible to reduce the number of compressors used, while keeping in motion that the first compressor 7 when the external temperature is at maximum, and secondly the extra power PA, the need is no longer felt beyond 7 ° C. Thus, the COP values are respectively close to 5 to 20 ° C, 4 to 7 ° C and 0 ° C, and between 3 and 4 to -20 ° C, and this continuously, the heat pump 1 according to the invention never being interrupted. It is found that the heating power supplied is maximum at very low temperatures, where the needs of use are the strongest. This curve shows a normal operation, based on the control by the management means 10, on the fan, the circulators and the solenoid valves, to maintain the temperature differences to the condensers as well as to the evaporator under 4 ° C., and to prevent icing of the evaporator and the pipe upstream of it. The COP can be further improved by an optimization of the bypass constituted by the solenoid valves 13, 22, 24, to favor particular circulations of fluid, in particular to allow the injection without expansion of gas, through a filter, on suction of the compressors. The optimization is still through the management of the supplements, at the level of the circuits 52 and 62, the resistor 53, and the good control of the energy recovery of the compressors. Of course, the add-ons can be selected from freely available sources of energy, such as solar, wind, or by the use of temperature differences between several branches of the main circuit 2 itself.

The overall efficiency is further improved by a rational use of the energy collected in the circuits of use. The circuit can be further optimized by judiciously staggering the pipe diameters of the coolant. In particular, avoid sending very hot gases to the evaporator, in which case there is a risk of condensing instead of evaporating. Preferably, the smaller pipe diameters are chosen in the branches 201 and 202, downstream of the bifurcation 17, which respectively contain the solenoid valves 22 and 24, so as to allow direct expansion. The largest pipe diameter of the installation concerns the branch 206 between the evaporator 6 and the compressor 7. Pipes of intermediate diameter are used in the branches 205 downstream of the compressor 7, 203 upstream of the second thermostatic expansion valve 20, 204 downstream of the latter.

The diameter of these pipes is chosen as a function of the flow rate of the compressor 7. At least one pressure switch can be used to increase the speed of the circulator 9 of the hydraulic circuit of use, when the discharge pressure of the compressor 7 increases. It is also possible to vary the pressure of the makeup circuit of FIG. 2 with a regulation of the speed of this circuit by increasing it when the pressure measured at the suction of the compressor 7 decreases. Indeed, it is necessary to avoid thermal losses at the first 8 and / or the second 38 operating circuits, which occur if the temperature in the latter is greater than that of the gas in the heat pump circuit at the the exchange between them, for example if the temperature of the gas is 30 ° C while that of the use is 40 ° C. The slowing of the traffic makes it possible to find the optimal situation where the temperature of the gas is higher than that of the circuit of use. It is important, in a heat pump circuit, to ensure the best possible operation of the compressor 7, or the compressors 7, 7A, and others, which constitute the means of setting in motion 3. This good operation is guaranteed if, d on the one hand, care is taken to prohibit any entry of liquid into the compressor or compressors, and, on the other hand, care is taken to optimize the operation of the compressor, which is the largest consumer of energy in the circuit. In particular, it is desirable to avoid restarting the compressor with high pressure in the circuit. To this end, the invention relates to a compressor protection kit 400, which can also be used alone, interposed in a pre-existing air conditioning installation, or installed with a commercial heat pump comprising, downstream of at least one such compressor, at least one condenser, at least one expander and at least one evaporator, that, preferably, in combination with the heat pump 1 described here to further increase the performance of which it was designed and developed.

The kit 400 is positioned upstream of the suction 30 of the compressor or compressors 7, and downstream of the expander 20 itself located downstream of the first condenser 4 and / or the second condenser 40. Downstream of the latter, the kit 400, as visible in Figure 9, comprises a main circuit 400A, which passes successively at least one evaporator 402, at least one exchange zone 408A with a fan 408, and at least one condenser 401, with an output branch 410, before the return to the suction 30 of the compressor 7. The kit 400 comprises a secondary circuit 400B, in which circulates a heat transfer fluid, set in motion by secondary means of movement 435, which are preferably constituted by minus a compressor 436. At the discharge 438 at high pressure of the latter, the secondary circuit enters a heat exchange branch 407 with the main circuit 400A, at the condenser 401. Downstream of the latter, the secondary circuit 400B passes throughadvantageously a filter, a sight, and a pressure reducer 405. This can be of thermostatic expansion type or direct expansion. It is advantageously temperature controlled by a temperature sensor 406 located at the suction 437 of the compressor 436. The secondary circuit 400B then passes through the evaporator 402, which it recovers the excess energy, before returning to the suction of the compressor 436, either directly or by passing through at least one secondary evaporator 439 connected in series on the circuit. Such a secondary evaporator 439 is advantageously double-circuited, as can be seen in FIG. 14, and comprises, within a well or a column, a coil 478, or a bundle of tubes, mounted coaxially from another coil 477, or bundle of tubes, that comprises the evaporator 6 of the heat pump 1. A fan 480, or a turbine, mounted on the same axis, optimizes the heat exchange. The return of the coil 478 leads to the auxiliary compressor 435, pressure-controlled by a suction pressure sensor 30 of the compressor 7 in the main circuit of the heat pump 1, before passing through the first heat exchange means 11, constituted by the condenser 201, from where the circuit goes to a thermostatic expansion valve 479, controlled by a suction temperature of the suction compressor 435. Preferably, the kit 400 further comprises, from other secondary means 435 for setting in motion, that is to say compressor 436, pressure balancing means 403, which are advantageously constituted by a single capillary. These pressure balancing means 403 may also include a 4-way valve, organizing the circulation upstream and downstream of the compressor 436 and in the condenser 401. In the case of the capillary as shown in the figure, when fluid crosses from its connection point 403B downstream of the compressor to its connection point 403A upstream of the latter, this results in an increase in temperature and suction at the compressor 436. It is understood that in the main circuit 400A, the coolant, which is in the form of a mixture of liquid and vapor phases downstream of the expander 20, is cooled through the passage in the evaporator 402 where it gives energy to the secondary circuit 400B, and is liquefied at a temperature below the outside temperature at its point of entry 430 in zone 408A; it is then vaporized in the exchange zone 408A with the fan 408, at its exit point 431 of the latter; if at this stage there remains a liquid phase, it is completely vaporized in the passage of the condenser 401, which ensures the absence of liquid phase in the output branch 410 which is connected to the suction 30 of the compressor 7. It is naturally possible to interpose, at an intermediate point 409 between the exit point 431 of the exchange zone 408A and the condenser 401, a branch towards a branch equipped with one or more regulators, in particular thermostatic expansion valves, joining the circuit main only just upstream or just downstream of the expander 20. The kit 400 ensures the absence of liquid phase at the suction 30 of the compressor 7, and increase the efficiency of the latter. It lowers the energy loss inherent in the evaporator. It makes it possible to lower the pressure at the discharge 31 of the compressor 30, and thus, combined with the circuit 1 designed to limit unnecessary restarting of the compressor, it guarantees restarts at a much lower pressure, for example 7 bar instead of 30 , and thus avoids large peaks of intensity expensive and detrimental to the life of the compressor. This lifetime is naturally increased by the use of the kit 400 to reduce the necessary compression ratio. The kit 400 allows the energy recovery at the evaporator 402. In the most common use of air conditioning of a house or a building, a heat pump is used to provide all or part of the heating energy and / or domestic hot water, as shown in Figure 10. The main circuit of the installation, downstream of the compressor 7, passes through, between an entry point 420 and an exit point 418 an exchanger 424, by which it transmits energy to a hot water circuit, for example a balloon 456 between an inlet 454 and a start 453. The part relating to the heating is articulated around a condenser 423, that the main circuit passes between a start 451 and an inlet 452, the heating circuit being fed by a start 409 and an inlet 409A.

For the remainder of the talk, the normal heating cycle without defrosting and the cycle with defrost are distinguished. In the first case of the normal heating cycle without defrosting, the usual rule of operation is advantageously chosen according to which the supply of the balloon 456 always has priority over the other circuits, and even over the deicing function. The condenser 424 does indeed work as a condenser. The coolant flows from the compressor 7 in the main circuit, first in gaseous form in the first branch 441 entering 420 in the condenser 424, from which it exits in the form of a mixture of liquid and gaseous phases, in the circuit branch 421, where it reaches a 4-way valve 411. In the present configuration, as shown in Figure 10, the valve 411 directs the fluid, by a branch 419, to the exchanger 423 of the heating circuit . The fluid leaves at point 452 in liquid form, before passing through the expander 422, which makes it iron in the form of a liquid-gas mixture. The implementation of the kit 400 then allows to recover, at the exchanger 202, a portion of the energy. In the second case of the defrosting cycle of the fan 408, as seen in FIG. 11, triggered when the temperature difference between the outside air inlet 433 in the fan 408 and the outside air outlet 432 thereof same evaporator is below a predetermined threshold, for example 7K, or when the difference between the temperature of the fluid between its point of entry 430 and its exit point 431 with respect to this fan 408 is less than such a threshold . Circulation in the 4-way valve 411 then imposes inverted circulation, so that the condenser 423 operates as an evaporator, and the evaporator 402 operates as a condenser. We can then double the power available for defrosting. According to the invention, as soon as the observation of icing of the fan 408, the management means 10 of the installation, preferably constituted by an automaton, start by triggering the cutting of the compressor or compressors 7, preferably in sequence. After this stop and the respect of a delay, the 4-way valve 411 is actuated, which makes it possible to establish a pressure equalization on either side of the compressor 7. This preliminary stop of the compressor 7 is important, because prevents any stroke of liquid that would not fail to occur if the 4-way valve was operated while the compressor was running. Balancing the pressures also makes it possible to be sure that the restart of the compressor 7 will be at a relatively low pressure, for example of the order of 7 bar, which is favorable to its service life. It is understood in FIG. 11 that the flow in the kit 400 is then reversed, therefore in the evaporator 402, as well as in the condenser 423. However, even in the evaporator defrosting situation, it is necessary to provide the user with domestic hot water at the required temperature, for example 60 ° C.

As can be seen in FIG. 12, an auxiliary energy recovery circuit can advantageously be installed. A probe 450 equips the discharge circuit downstream of the compressor 7. The purpose of the installation is to prevent the temperature being too high in the tank 456, in comparison with a set value, for example 60 ° C. and to recover the portion of energy that would lead to a too high temperature, this always in order to improve the efficiency of the compressor 7, adapting its use to the bare necessities. The condenser 424 benefits from the heat exchange with the main circuit 420, between its entry points 420 and exit 418. The secondary circuit, on the side of the balloon 456, conveys water or another liquid heat transfer fluid and arrives, through the inlet 453 in the upper part of the balloon 456, in which it pours. The contents of the flask 456 are described as dead water and constitute a volume of liquid in which at least one exchanger for heating domestic hot water is immersed at a tertiary circuit, comprising a thermostatic mixer to prevent burns if the temperature in the flask is too high, the latter can indeed reach for example 80 ° C. A temperature sensor 457 is installed at the bottom of the tank 456. at the bottom, a water intake allows the sampling by at least one circulator 455, triggered by the temperature measured at the probe 450 downstream of the compressor 7, and reducing the fluid through the junction 454 to the exchanger 424. The startup of this circulator 455 prevents any loss of load.

Another exchanger immersed in the flask 456 allows circulation, this time in an exchange circuit with a buffer tank 459 of a heating circuit. A circulator 477 controlled by the temperature sensor 457 immersed in the balloon 456 circulates the liquid contained in this exchange circuit, via a non-return valve, at a branch 458, through which it arrives in the buffer tank 459, the circuit of which runs through a demister and a filter, before joining the exchanger immersed in the balloon 456. In its passage in the buffer tank 459, this circuit exchanges some of its energy with the heating circuit itself , between an inlet 472 and an outlet 473. The inlet 472 is connected downstream and at the outlet of the secondary of the exchanger 423, through a controlled circulator 471 and a non-return valve. The output 473 arrives, via a branch 467, on a 4-way valve 465 which, as shown in FIG. 13, makes it possible to connect a boiler 466 to the circuit, and, downstream of this 4-way valve 465, in a first branch 467A a bypass 474, and in another branch 468, a motorized 3-way valve 464. The 4-way valve 465 makes it possible to overcome a possible failure of the heat pump, thus involving the boiler 466. In fact, if the heat pump is correctly sized, and if the installer makes sure to recover the energy wherever it could be wasted, that is to say rejected to the environment without being exchanged, and if it ensures the optimal operation of the compressor or compressors 7, including through to a kit 400, the boiler 466 serves very little, and serves only backup or backup circuit. The 3-way valve 264 is controlled by a temperature sensor 463 located in a room at a radiator 468. The 3-way valve 464 orients the fluid, either in a branch 462 where it joins a portion derived in the branch 467A to through the bypass 474, either in a branch 460, which comprises a temperature sensor S10, a circulator 475 and a non-return valve, upstream of at least one radiator 468. Downstream of the latter, the circuit borrows a branch 461, having a temperature tap S10, and which converges at a point 469 with the branch 462 from the bypass 474, to form a return branch 470, via a filter and a demister, to the exchanger 423. This heating circuit is designed so as to ensure the comfort of users, not by favoring the attainment of high temperatures, but rather by gradually reaching the desired temperature, without meeting the heat and cold strokes so characteristic of the installation s heating in poorly insulated buildings.

It is therefore a question of continuously calculating the temperature difference S10-S11, of comparing it with a reference value, of raising the temperature 463 in the room where the temperature is to be regulated in order to control the 4-way valve 464, and of to raise the outside temperature 433 upstream of the evaporator 408. It is then necessary to manage the exchange circuits and the circulation of the water of the heating circuit so that the latter is not, unnecessarily, higher than that desired for the room. . The recovery of the energy supplied by the heat pump circuit, in favor of the heating circuit, is at the exchanger 423, preferably a plate heat exchanger. The circulator 471 operates when the heat pump rotates, and pushes the heating fluid from the bottom of the buffer tank 459 to its upper end from which it emerges from the branch 473. In the upper part of the balloon 459 is a set point 476 The management is done, either according to the law of water, or by comparison with a preset value; in the latter case, corresponding to a room temperature, it constitutes a set point limit, is not exceeded, and is reached by gradual rise in temperature.

If there is no heating demand in the use constituted by the radiator or radiators 468, the 3-way valve 464 orients the fluid in the branch 462, shunting the branch 460 of the radiators. Conversely, in case of heating demand, the fluid is oriented in the branch 460, and the circulator 475 is operated to suck a portion of the flow of the circulator 471, and therefore a portion of the heat exchanger 423 The circulator 471 is necessarily more powerful than the circulator 475. If the room temperature is not reached, the controller triggers the operation of the 4-way valve 465 to put the heat pump in series with the boiler 466. In order to obtain a stepped rise, it is regulated on the basis of a small temperature difference, for example 7 ° C., which allows a gradual rise, and a feeling of total comfort.

Claims (9)

REVENDICATIONS1. 1 Kit (400) for compressor protection (7), for an air-conditioning system or heat pump (1) comprising, downstream of at least one such compressor (7), at least one condenser (4), at least one expansion valve (5) and at least one evaporator (6), said kit (400) being designed capable of being positioned upstream of the suction (30) of said compressor (7), and downstream of a pressure reducer itself downstream of said condenser (4), characterized in that it comprises a main circuit (400), which passes successively through at least one evaporator (402), at least one exchange zone (408A) with a fan (408), and at least one condenser (401), before returning to said suction (30), and that it comprises a secondary circuit (400B), in which circulates a heat transfer fluid, set in motion by secondary means of movement ( 435) constituted by at least one compressor (436), at the discharge (438) of which said secondary circuit (400B) successively traverses a branch ( 407) with said main circuit (400A), at said condenser (401), then a temperature controlled expander (405) by a temperature sensor (406) located at the suction (437) of said compressor ( 436), then passes through said evaporator (402), from which it recovers the excess energy, before returning to the suction of the compressor (436). 2. Kit (400) compressor protection (7) according to claim 1, characterized in that it comprises on either side of said compressor (436) pressure balancing means (403) constituted by a capillary or by a 4-way valve, organizing the flow upstream and downstream of said compressor (436) and in said condenser (401). 3. Heat pump (1) comprising a kit (400) according to one of the preceding claims and comprising, downstream of at least one compressor (7), at least one condenser (4), at least one expander (5). and at least one evaporator (6), characterized in that it comprises first heat exchange means (11) located on another section that separating said compressor (7) from said condenser (4), to regulate the difference between the superheat temperature (T8) and the inlet temperature (T7) in said first evaporator (6) on the one hand, and between the subcooling temperature (T2) and the inlet temperature (T1) in said condenser (4) on the other hand. 4. Heat pump (1) according to one of the preceding claims, characterized in that said first heat exchange means (11) are interposed between said first evaporator (6) and said compressor (7) 5. Heat pump (1) according to one of claims 3 to 4, characterized in that its main circuit, downstream of said compressor (7), passes between an entry point (420) and an exit point (418), an exchanger (424), by which it transmits energy to a hot water circuit comprising at least one balloon (456) between an inlet (454) and a start (453), then passes through a valve 4-way (411), which directs the flow, or in a first heating mode without defrosting, to a condenser (423) crossed between a start (451) and an inlet (452), said condenser (423) exchanging its energy with a heating circuit supplied between a start (409) and an inlet (409A), or in a second mode with defrosting to said evaporator (402) then operating as a condenser, then to said condenser (423) then operating as an evaporator . 6. Heat pump (1) according to the preceding claim, characterized in that it comprises management means (10) designed capable of triggering the cutting of the compressor or compressors (7) during an observation of icing said fan ( 408). 7. Heat pump (1) according to one of claims 5 to 6, characterized in that it comprises an auxiliary energy recovery circuit, comprising a probe (450) equips the discharge circuit downstream of said compressor ( 7), and a secondary circuit, on the side of said balloon (456), conveying a liquid coolant fluid, and arriving, by an inlet (453) in the upper part of said balloon (456), into which it flows, and comprising, at the bottom said balloon (456), a temperature sensor (457), and a water intake allowing the sampling by at least one circulator (455), triggered by the temperature measured at said probe (450) and reducing the fluid by a junction (454) to said exchanger (424), starting said circulator (455) to prevent any loss of load. 8. Heat pump (1) according to one of claims 5 to 7, characterized in that it comprises another exchanger immersed in said balloon (456) so as to allow circulation in an exchange circuit with a buffer tank (459) of a heating circuit, under the effect of a circulator (477) controlled by a temperature sensor (457) immersed in said flask (456) circulates the liquid contained in this exchange circuit via a non-return valve, at a branch (458), through which it arrives in said buffer tank (459), the circuit of which flows through a de-mopper and a filter, before joining a heat exchanger immersed in said balloon (456), said exchange circuit exchanging, during its passage through the buffer tank (459), a portion of its energy with the heating circuit itself, between an inlet (472) and an outlet (473), said input (472) being connected downstream and at the output of the secondary of said exchange ur (423), through a controlled circulator (471) and a check valve, said outlet (473) arriving, by a limb (467), on a 4-way valve (465) designed adapted to connect to the circuit a boiler (466), and, downstream of said 4-way valve (465), in a first branch (467A) a bypass (474), and in another branch (468), a 3-way valve (464). ) motorized, said 4-way valve (465) to overcome a possible failure of the heat pump (1) by involving said boiler (466). 9. Heat pump (1) according to the preceding claim, characterized in that said 3-way valve (464) is temperature-controlled by a sensor (463) located in a room at a radiator (468), said valve 3 channels (464) directing the fluid, either in a branch (462) where it joins a portion derived in the branch (467A) through said bypass (474), or in a branch (460), which comprises a temperature (S10), a circulator (475) of power lower than that of said circulator (471), and a check valve, upstream of at least one radiator (468), downstream of which the circuit borrows a branch (461), having a temperature tap (S10), and which converges at a point (469) with the branch (462) from the bypass (474), to form a return branch (470), via a filter and a defogger, to the exchanger (423). 1O.Procédé piloting a heat pump (1) according to the preceding claim, characterized in that the recovery of the energy supplied by the heat pump circuit, in favor of the heating circuit, is at the level of l heat exchanger (423), said circulator (471) operating when the heat pump rotates, and pushing the heating fluid from then down the buffer tank (459) to its upper end from which it emerges from the branch (473) in the upper part of the balloon (459) contained a deposit (476), and in that the management is done, either according to the law of water, or by comparison with a preset value, and that, if there is has no heating demand at the level of the use constituted by the radiator or radiators (468), the 3-way valve (464) orients the fluid in the branch (462), shunting the branch (460) of the radiators, and conversely, in case of heating demand, the fluid is oriented in the branch (460), and the circulator (475 ) is operated to suck a portion of the flow of the circulator (471), and therefore a portion of the heat exchanger (423).