FR3081531A1 - 3-WAY VALVE - Google Patents

Abstract

The invention relates to a 3-way valve (35b) arranged to be actuated by an electric motor, this valve being arranged to define an input channel and two output channels, namely a first and a second output channel, this valve being of the plug type, this valve comprising: - a plug (205) having a conduit (206) in particular of cylindrical shape, arranged to define a fluid passage between the inlet channel (201) and the first outlet channel (202), this duct having a section allowing a complete opening of the valve between this inlet channel and this first outlet channel, this section of the duct preferably being substantially equal to the respective sections of the inlet duct and the first way out

Description

3-way valve

The invention relates to a 3-way valve arranged to be actuated by an electric motor

Currently, ventilation, heating and / or air conditioning devices for the passenger compartment of a motor vehicle generally comprise a closed thermodynamic loop comprising at least, depending on the direction of circulation of a refrigerant, an evaporator on the air, a compressor, condenser and expansion valve or device. In this configuration, the air is cooled by passing it through the evaporator before being expelled to the passenger compartment by pipes.

These ventilation devices operate thanks to the air conditioning compressor drive by the internal combustion engine, the efficiency of which varies greatly depending on its speed and load (low efficiency at idle, good acceleration efficiency and no deceleration consumption ); thus for a given charge to the air conditioning compressor, the motor vehicle will consume more or less fuel

Also, when the vehicle is stopped, the ventilation devices are inefficient or even do not work at all.

In addition, in recent vehicles that are equipped with an engine management system called "Stop and Go", that is to say stop the internal combustion engine when the vehicle is at neutral, for example at a light or a stop, then restarting it when the advance of the vehicle is again desired, thanks to an alternator-starter, the engine can no longer drive the compressor when the engine is stopped. Air conditioning is therefore frequently interrupted, which affects the overall comfort of passengers.

Generally speaking, there is a need to be able to manage the air conditioning while minimizing the fuel consumption of the vehicle.

It is known from patent application US20100018231 to store frigories in an evaporator of the air conditioning system.

However storing frigories in the evaporator of the ventilation device (HVAC) implies the presence of phase change materials (PCM) which reduces its performance, increases its size accordingly and does not allow to control the desired moment for the restitution of frigories.

The invention aims in particular to allow, in this type of circuit, a regulation of the flow between different channels of a 3-way valve.

In the state of the art, 3-way T-valves allowing the opening onto one of the two outlet channels exist, as described in patent and patent applications EP1519090 and US5810326.

The invention aims in particular to propose a 3-way ball valve which ensures both a complete bypass on a first outlet and a regulation on a second outlet in an air conditioning circuit.

The subject of the invention is therefore a 3-way valve arranged to be actuated by an electric motor, this valve being arranged to define an inlet channel and two outlet channels, namely a first and a second outlet channel, this valve being of the plug type, this valve comprising:

a plug having a conduit, in particular of cylindrical shape, arranged to define a fluid passage between the inlet channel and the first outlet channel, this conduit having a section allowing complete opening of the valve between this inlet channel and this first outlet channel, this section of the duct preferably being substantially equal to the respective sections of the inlet channel and of the first outlet channel, this allowing a minimum of pressure drops, o a pressure drop regulation channel arranged to regulate the pressure drop of a passage between the inlet channel and the second outlet channel, this inlet channel and this second outlet channel being in particular oriented relative to one another according to a angle between 45 ° and 110 °.

According to one aspect of the invention, the pressure drop regulating channel has a passage section at least two times smaller, in particular 5 or 10 times smaller than that of said conduit.

According to one aspect of the invention, the inlet path and the first outlet path of the valve are arranged diametrically opposite.

According to one aspect of the invention, the valve is arranged to allow the inlet channel and the second outlet channel to be placed in fluid communication via the pressure drop control channel, while closing the first outlet channel.

This mode corresponds to a refrigerant expansion mode which allows the storage of frigories in a storage unit.

According to one aspect of the invention, the valve is arranged to allow the inlet channel and the second outlet channel to be placed in fluid communication via an enlarged passage allowing with a minimum pressure drop, while closing the first outlet channel . This mode allows the return of frigories from the storage unit.

According to one aspect of the invention, the valve is arranged to allow the inlet channel and the first outlet channel to be placed in fluid communication via said conduit with minimum pressure drop, while closing the second outlet channel.

According to one aspect of the invention, the plug is of the spherical type.

As a variant, the plug is of the cylindrical type or of the conical type.

According to one aspect of the invention, the sealing of the second outlet path is ensured via a seal.

According to one aspect of the invention, the sealing of the inlet channel can be weak or even eliminated in order to ensure correct positioning of the plug.

According to one aspect of the invention, the sealing of the second outlet channel is ensured in part by calibrated tightening of a mounting plug.

According to one aspect of the invention, there is a small pressure drop in the valve during the passage of the fluid between the inlet channel and the first outlet channel.

According to one aspect of the invention, a position of the plug allows the closure of the two outlet channels simultaneously.

According to one aspect of the invention, the position of the closed outlet channels can be prohibited by a stop, this prohibition could be useful for protecting the compressor.

The invention also relates to a thermal system of a motor vehicle, in particular a motor vehicle air conditioning system, this system comprising:

a main thermal circuit comprising a compressor arranged to compress a refrigerant circulating in this circuit and an evaporator arranged to cool an air flow which circulates in contact with the evaporator, this cooling being obtained by heat exchange between the air flow to cooling and the refrigerant circulating in this evaporator, a secondary thermal device comprising a cold storage unit, a device creating an expansion between the outlet of the evaporator and the inlet of the cold storage unit, and a pump, this secondary device being arranged so:

o to establish a pressure in the cold storage unit at a level lower than the pressure in the evaporator when the system is in storage mode, o to regulate the pressure difference between the cold storage unit and the evaporator depending on the conditions of use, o prevent the exchange of refrigerant between the storage unit and the main thermal circuit when the system is in normal mode.

o be connected, preferably in series, to the evaporator of the main thermal circuit when the compressor of the main thermal circuit is stopped or operating at low speed so that refrigerant from the cold storage unit is sent , by means of the pump, through the evaporator of the main thermal circuit, in which the secondary thermal device comprises a bypass valve arranged to be selectively traversed by refrigerant which circulates from the evaporator 10 of the main thermal circuit to the cold storage unit 22 for transferring cold from the refrigerant to the cold storage unit by means of an expansion in this valve, this second bypass valve being a 3-way valve.

According to one aspect of the invention, the mounting of the valve is advantageously made with the plug in the position in expansion or storage mode in order to release the seals when it enters. This plug is located on the face opposite to the second exit route.

The invention will be better understood and other details, characteristics and advantages of the invention will appear on reading the following description given by way of nonlimiting examples with reference to the appended drawing in which:

- Figure 1 illustrates, schematically and partially, a first embodiment of the system according to the invention,

- Figures 2 to 4 illustrate the system of Figure 1 during different operating modes,

FIG. 5 illustrates, diagrammatically and partially, a second embodiment of the system according to the invention,

- Figure 6 illustrates, schematically and partially, a third embodiment of the system according to the invention, Figure 7 illustrates an operation of the system of Figure 6, Figures 2a, 3a and 4a are Mollier diagrams corresponding to the phases of operation of FIGS. 2, 3 and 4, respectively,

- Figures 4b, 5a-5c illustrate other embodiments of the invention,

- Figures 8 to 10 illustrate a 3-way valve in several operating configurations.

FIG. 1 represents an air conditioning system 1 which comprises, according to the direction of circulation in a closed circuit of a refrigerant fluid such as R134A: a compressor 2, a condenser 3, a storage bottle 4, an internal heat exchanger 5, an expansion or expansion device 6 and an air evaporator 10. These components form a main thermal circuit 20.

The evaporator 10 is placed in an air circulation pipe leading to different zones of the passenger compartment to be cooled or heated such as a zone for the demisting of the windshield, a ventilation zone and a foot zone. .

The compressor 2 is arranged to compress the refrigerant circulating in this circuit 20 and the evaporator 10 is arranged to cool an air flow which circulates in contact with the evaporator, this cooling being obtained by heat exchange between the air flow to cool and the refrigerant circulating in this evaporator.

The system 1 further comprises a secondary thermal device 21 comprising a cold storage unit 22, an expansion or pressure drop device 27 and a pump 23, this secondary device being arranged so:

o to establish a pressure in the storage unit 22 at a level lower than the pressure in the evaporator 10 when the system is in storage mode (see FIGS. 3 and 3a), o to regulate the pressure difference between l storage unit 22 and the evaporator depending on the conditions of use, o prevent the exchange of refrigerant between the storage unit and the main thermal circuit 20 when the system is in normal mode, say when the compressor 2 is running and the evaporator 10 cools the air flow (see Figures 2 and 2a). Thus the storage unit 22 can be maintained at a pressure lower than that of the evaporator when it is filled with frigories, o to be connected in series to the evaporator 10 of the main thermal circuit 20 when the compressor 2 of the main thermal circuit is stopped (restitution mode) so that the refrigerant from the cold storage unit 22 is sent, using the pump 23, through the evaporator 10 of the main thermal circuit 20 or else (storage mode) that refrigerant from the evaporator be sent to the cold storage unit 22 (see FIGS. 4 and 4a), o to be in parallel with the compressor in “cold boost” mode as illustrated in Figure 4b.

Figures 2a, 3a and 4a are Mollier diagrams corresponding to the operating phases of Figures 2, 3 and 4, respectively.

The secondary thermal device 21 comprises a first bypass valve 25 or 35 or 37, arranged to selectively prevent the circulation of refrigerant between the cold storage unit 22 and the main thermal circuit 20, in normal mode.

The secondary thermal device 21 is arranged so that:

- In operating mode of the main thermal circuit 20 without using the secondary thermal device 21 (see FIG. 2), the cold storage unit 22 is bypassed and the pump 23 is stopped,

- In operating mode of the main thermal circuit 20 with recharging in frigories of the frigories storage unit 22 of the secondary thermal device21 (see FIG. 3), the frigories storage unit 22 is traversed by refrigerant and the pump 23 is stopped,

- In operating mode of the secondary thermal device 21 for restoring frigories to the evaporator of the main thermal circuit 20 (see FIG. 4), the compressor 2 of which is stopped, the frigory storage unit 22 is traversed by refrigerant and pump 23 is running,

- In so-called “cold boost” mode, namely in operating mode of the secondary thermal device to restore frigories to the evaporator of the main thermal circuit, whose compressor operates at low or high load, the frigory storage unit is traversed by refrigerant and the pump is running (see figure 4b).

In the cold storage phase in the cold storage unit 22 (FIG. 3), the pump 23 is arranged so as to be bypassed and is then stopped.

The secondary thermal device 21 is arranged so that the direction of circulation of the refrigerant in the cold storage unit 22 is reversed respectively:

when this frigory storage unit 22 receives frigories from the refrigerant passing through it (frigory storage phase illustrated in FIG. 3) and

- When this frigories storage unit 22 restores frigories to the refrigerant which passes through it (frigories restitution phase illustrated in FIG. 4).

In this system, the circuit is bypassed by the valve 36, the expansion in the cold storage unit 22 by the valve 35 and the insulation of the cold storage unit 22 by the valve 35 and the valve. non-return 37.

The first bypass valve 25 is a 3-way valve disposed at a junction between the secondary thermal device 21 and the main thermal circuit 20.

In the phase of FIG. 2, the valve 25 prevents circulation to the secondary thermal device 21 which is not used.

In the phase of FIG. 3, the valve 25 allows circulation of the cold storage unit 22 towards the compressor 2.

In the phase of FIG. 3, the valve 25 allows circulation of the evaporator 10 towards the cold storage unit 22.

The secondary thermal device 21 includes a second bypass valve 27, which is a two-way valve, arranged to be selectively traversed by refrigerant which circulates from the evaporator 10 of the main thermal circuit to the frigory storage unit 22 to allow to transfer frigories from the refrigerant to the frigories storage unit by means of an expansion in this valve.

The valve 27 is blocking in the operating phases of FIGS. 2 and 4, and passing in the operating phase of FIG. 3.

The second bypass valve 27 is arranged to generate two pressure levels respectively for the evaporator 10 and the storage unit 22.

This second bypass valve can be a variable passage section valve, a single passage section valve or a 3-way valve (35b).

The secondary thermal device 21 comprises a secondary branch 28 on which is disposed this second bypass valve 27, this branch 28 forming a fluid junction 30 with a primary branch 29 on which are arranged the frigory storage unit 22 and the pump 23.

This junction 30 between the primary branch 28 and the secondary branch 29 is arranged between the cold storage unit 22 and the pump 23.

The secondary thermal device 21 comprises a non-return valve 31 disposed on the primary branch 29 downstream of the pump 23.

Of course, the invention is not limited to the example which has just been described.

For example, as illustrated in FIG. 5, the secondary thermal device 21 is arranged so that the direction of circulation of the refrigerant in the cold storage unit 22 is the same respectively:

when this storage unit 22 of frigories receives frigories from the refrigerant which passes through it and

- When this frigories storage unit 22 returns frigories to the refrigerant which passes through it.

Two bypass valves 35 and 36 are provided as explained below.

One of the bypass and expansion valves 35 is arranged at the entrance to the cold storage unit 22, on a primary branch 29.

The other bypass valves 36 is disposed between the evaporator 10 and the pump 23, on a secondary branch 28.

According to one aspect of the invention, the valves 35 and 36 can be replaced by a 3-way valve 35b (see Figure 5a).

A non-return valve 37 is arranged at the outlet of the cold storage unit 22.

In the above examples, the cold storage unit 22 is arranged to be at a pressure lower than that of the evaporator.

An expansion device 39, either thermostatic or electric, is arranged upstream of the evaporator 10 to generate an expansion of the refrigerant before it passes through the evaporator 10.

The cold storage unit 22 is arranged inside an HVAC or outside an HVAC.

According to a variant illustrated in FIGS. 6 and 7, the system comprises an air path 40 arranged parallel to the evaporator 10, a path through which air can circulate bypassing the evaporator 10, and this air being able, at the outlet in this way, mix with the air coming from the evaporator. Thus the position of the valve 27 downstream of the evaporator can help to adjust the temperature of the air leaving the evaporator by mixing the cold air coming from the evaporator and the warmer air coming from the see above air. This is advantageous during the cold storage phase. The valve can for example be a simple closing valve with a fixed diameter. The 2-way valve referenced 27 is for example arranged to generate a fixed pressure drop so as to protect the evaporator from ice formation.

The refrigerant can be a material, here a fluid, with phase change to work in latent heat in order to reduce the mass required and limit the temperature variations of the storage.

For example, the refrigerant is a two-phase fluid type R134a or 1234yf.

The storage device may contain a phase change material to limit temperature variations.

In the examples above, the valves 27 or 35 provide an intermediate expansion so that the pressure of the compressor and that of the storage unit are different.

The pressure and the temperature of the refrigerant being linked, so to continue blowing air at the right temperature for passengers, it is necessary to limit the pressure variation.

However to store, it is necessary to lower the temperature therefore the pressure.

Intermediate expansion by the valves mentioned above makes it possible to have two pressure levels then two temperature levels.

According to one aspect of the invention, the conduit leading the flow of refrigerant from the cold storage unit 22 to the pump 23 can be located downstream or upstream of the check valve 37 or Check valve 37 thus allowing the refrigerant pump to be placed directly at the outlet of the cold storage unit.

The difference between the mode of Figure 5b and that of Figure 5c is that, in the mode of Figure 5c, the 3-way valve of Figure 5b is replaced by two 2-way valves (see box in Figure 5c).

As illustrated in FIGS. 8 to 10, the 3-way valve 35b described in connection with FIG. 5a is arranged to be actuated by an electric motor 200, this valve 35b being arranged to define an inlet channel 201 coming from the evaporator 10 and two outlet channels, namely a first 202 and a second 203 outlet channels, this valve being of the plug type, this valve comprising:

a plug 205 housed in a valve body 300 having a conduit 206 (see FIG. 10) in particular of cylindrical shape, arranged to define a fluid passage 207 between the inlet channel 201 and the first outlet channel 202, this conduit having a section allowing complete opening of the valve between this inlet channel and this first outlet channel, this section of the duct preferably being substantially equal to the respective sections of the inlet channel and of the first outlet channel, o a pressure drop regulating channel 220 (see FIG. 8) arranged to regulate the pressure drop of a passage 221 between the inlet channel 201 and the second outlet channel 203, this inlet channel and this second exit route being in particular oriented relative to each other at an angle between 45 ° and 110 °.

Channel 202 is connected to pump 23.

Channel 20 is connected to the cold storage unit 22.

A bearing 301 of the valve is provided.

The pressure drop regulating channel 220 has a passage section at least two times smaller, in particular 5 or 10 times smaller than that of said conduit.

The inlet channel 201 and the first outlet channel 202 of the valve are preferably arranged diametrically opposite.

The valve is arranged to allow the inlet channel 201 and the second outlet channel 203 to be placed in fluid communication via the pressure drop control channel, while closing the first outlet channel 202. These are: an expansion mode for storing frigories in the storage unit, illustrated in FIG. 8.

The valve is arranged to allow fluid communication between the inlet channel 201 and the second outlet channel 203 via an enlarged passage 260 allowing with minimum pressure drop, while closing the first outlet channel, as illustrated in the figure 9 where the valve is in restitution mode.

The valve 35b is arranged to allow the inlet channel 201 and the first outlet channel 202 to be placed in fluid communication via said enlarged conduit 260 with minimum pressure drop, while closing the second outlet channel 203.

According to one aspect of the invention, the plug is of the spherical type.

According to one aspect of the invention, the sealing of the second outlet channel 203 is ensured via a seal 270 as illustrated in FIG. 9.

According to one aspect of the invention, the sealing of the inlet channel can be weak or even eliminated in order to ensure correct positioning of the plug.

According to one aspect of the invention, a position of the plug allows the closure of the two outlet channels simultaneously.

According to one aspect of the invention, the position of the closed outlet channels can be prohibited by a stop, this prohibition could be useful for protecting the compressor.

Claims (10)

1. 3-way valve (35b) arranged to be actuated by an electric motor, this valve being arranged to define an inlet channel and two outlet channels, namely a first and a second outlet channel, this valve being of valve type, this valve comprising: a valve (205) having o a conduit (206) in particular of cylindrical shape, arranged to define a fluid passage between the inlet channel (201) and the first outlet channel (202) , this conduit having a section allowing complete opening of the valve between this inlet channel and this first outlet channel, this section of the conduit preferably being substantially equal to the respective sections of the inlet channel and of the first channel of outlet, o a pressure drop regulating channel (220) arranged to regulate the pressure drop of a passage between the inlet channel and the second outlet channel, this inlet channel and this second outlet channel and ant notably oriented one relative to the other at an angle between 45 ° and 110 °. 2. Valve according to the preceding claim, wherein the pressure drop regulating channel (220) has a passage section at least two times smaller, in particular 5 or 10 times less than that of said conduit. 3. Valve according to one of the preceding claims, in which the inlet channel and the first valve outlet channel are arranged diametrically opposite. 4. Valve according to one of the preceding claims, in which the valve is arranged to allow the inlet channel and the second outlet channel to be placed in fluid communication via the pressure drop regulation channel, while closing the first exit route. 5. Valve according to one of the preceding claims, in which the valve is arranged to allow the inlet channel and the second outlet channel to be placed in fluid communication via an enlarged passage allowing with minimum pressure drop, while closing the first exit route. 6. Valve according to one of the preceding claims, in which the valve is arranged to allow the inlet channel and the first outlet channel to be placed in fluid communication via said conduit with minimum pressure drop, while closing the second channel. Release. 7. Valve according to one of the preceding claims, in which the plug (205) is of the spherical type. 8. Valve according to one of the preceding claims, in which the sealing of the second outlet channel is ensured via a seal. 9. Valve according to one of the preceding claims, in which the sealing of the second outlet channel is ensured in part by calibrated tightening of a mounting plug. 10. Motor vehicle thermal system, in particular a motor vehicle air conditioning system, this system comprising: a main thermal circuit comprising a compressor arranged to compress a refrigerant circulating in this circuit and an evaporator arranged to cool an air flow which circulates in contact with the evaporator, this cooling 5 being obtained by heat exchange between the air flow to be cooled and the refrigerant circulating in this evaporator, a secondary thermal device comprising a frigory storage unit, a device creating an expansion between the outlet of the evaporator and the inlet of the frigory storage unit, and a pump, this secondary device being arranged so: o to establish a pressure in the cold storage unit at a level lower than the pressure in the evaporator when the system is in storage mode, o to regulate the pressure difference between the cold storage unit and the evaporator according to the conditions of use, o to prevent the exchange of coolant between the storage unit 20 and the main thermal circuit when the system is in normal mode. be connected, preferably in series, to the evaporator of the main thermal circuit when the compressor of the main thermal circuit is stopped or operating at low speed so that the refrigerant coming from the cold storage unit is sent, by means of the pump, through the evaporator of the main thermal circuit, in which the secondary thermal device (21) comprises a bypass valve (27) arranged to be selectively traversed by refrigerant which circulates from the evaporator 10 from the main thermal circuit to the cold storage unit 22 to allow transfer of cold from the refrigerant to the cold storage unit by means of an expansion in this valve, this second bypass valve being a 3-way valve (35b) according to one of the preceding claims.