WO2024023089A1 - Hydraulic unit for a refrigerant in a thermal management circuit - Google Patents

Abstract

The invention relates to a hydraulic unit (3) for a refrigerant in a thermal management circuit of a motor vehicle, said hydraulic unit (3) comprising within it at least one first refrigerant flow line (A) between a first port (A1) opening onto a face (3a, 3b, 3c) of the hydraulic unit (3) and a second port (A2) opening onto a face (3a, 3b, 3c) of the hydraulic unit (3), the first flow line (A) including a first auxiliary line (A') connecting said first flow line (A) to a third port (A3), the hydraulic unit (3) also comprising a first cavity (R1) machined and recessed into the first auxiliary line (A') from a first opening (O1) made on one face (3a, 3b, 3c) of the hydraulic unit (3), said hydraulic unit (3) comprising a first non-return valve (V1) inserted completely within said first cavity (R1) and configured to block the flow of the refrigerant between one of the ports (A1, A2, A3) of the first flow line (A) and another one of said ports (A1, A2, A3).

Description

HYDRAULIC BLOCK FOR REFRIGERANT FLUID IN A THERMAL MANAGEMENT CIRCUIT

[0001] The present invention relates to a hydraulic block for refrigerant fluid within a thermal management circuit. More particularly, the invention relates to a hydraulic block in which a refrigerant fluid is intended to circulate and intended to be integrated into a thermal management circuit for a motor vehicle, in particular for an electric and/or hybrid vehicle.

[0002] A thermal management circuit of a motor vehicle such as an air conditioning, cooling or heat pump circuit is generally a bulky device due to the different elements which compose it. Some of these elements such as the heat exchangers or the compressor cannot be reduced in order to gain compactness and allow the thermal management circuit to be installed in small spaces, for example within an electric or hybrid vehicle. in which it is necessary to conserve as much space as possible for the batteries and thus improve autonomy.

[0003] Elements of a thermal management circuit on which it is possible to influence to allow the thermal management circuit to be as compact as possible are the different pipes as well as the arrangement of the elements between them.

[0004] One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose a hydraulic block architecture allowing the integration of elements of a thermal management circuit so that the latter be as compact as possible.

[0005] The present invention therefore relates to a hydraulic block for refrigerant fluid of a thermal management circuit of a motor vehicle, said hydraulic block comprising within it at least a first refrigerant fluid circulation pipe between a first orifice opening onto one face of the hydraulic block and a second orifice opening onto one face of the hydraulic block, the first circulation pipe comprising a first annex pipe connecting said first circulation pipe to a third orifice, the hydraulic block further comprising a first machined housing and sinking within the first auxiliary pipe from a first opening made on one face of the hydraulic block, said hydraulic block comprising a first non-return valve inserted completely within said first housing and configured to block the circulation of the refrigerant fluid between one of the orifices of the first circulation pipe with another of said orifices.

[0006] According to one aspect of the invention, the first opening of the first housing is distinct from the orifices of the first circulation pipe and the first opening is blocked by a closing means.

[0007] According to another aspect of the invention, the first opening of the first housing is also the third orifice of the first annex pipe.

[0008] According to another aspect of the invention, the hydraulic block comprises a second refrigerant fluid circulation pipe between a first orifice opening onto one face of the block hydraulic block and a second orifice opening onto one face of the hydraulic block, the hydraulic block comprising a second annex pipe connecting said second circulation pipe to a third orifice, the hydraulic block further comprising a second machined housing and sinking into the second auxiliary pipe from a second opening made on one face of the hydraulic block, said hydraulic block comprising a second non-return valve inserted completely within said second housing and configured to block the circulation of the refrigerant fluid between one of the orifices of the second pipe circulation with another of said orifices.

[0009] According to another aspect of the invention, the second opening of the second housing is distinct from the orifices of the second circulation pipe and the second opening is blocked by a closing means.

[0010] According to another aspect of the invention, the second opening of the second housing is also the third orifice of the second annex pipe.

[0011] According to another aspect of the invention, the third orifice of the first annex pipe opens onto one face of the hydraulic block and the third orifice of the second annex pipe opens into the first annex pipe between the third orifice of the first pipe annex and the first non-return valve.

[0012] According to another aspect of the invention:

- the first orifice of the first circulation pipe opens onto a first face of the hydraulic block, said first orifice being intended to be a refrigerant fluid inlet,

- the second orifice of the first circulation pipe opens onto a second face of the hydraulic block, distinct from the first face, so as to allow direct circulation of the refrigerant fluid between the first orifice and the second orifice of the first circulation pipe,

- the first non-return valve is configured to allow the circulation of the refrigerant fluid from the first circulation pipe to the third orifice of the first annex pipe and to allow the circulation of the refrigerant fluid from the third orifice of the first annex pipe to be blocked towards the first circulation pipe,

- the first orifice of the second circulation pipe also opens onto the first face of the hydraulic block, said first orifice being intended to be a refrigerant fluid outlet,

- the second orifice of the second circulation pipe opens onto a second face of the hydraulic block, distinct from the first face, so as to allow direct circulation of the refrigerant fluid between the first orifice and the second orifice of the second circulation pipe,

- the second non-return valve is configured to allow the circulation of the refrigerant fluid from the third orifice of the second annex pipe, therefore from the first annex pipe, towards the second circulation pipe and to allow the circulation of the refrigerant fluid from the second circulation pipe towards the third orifice of the second annex pipe, therefore towards the first annex pipe. [0013] According to another aspect of the invention, the hydraulic block comprises an additional block attached to and covering the first and second openings, said additional block comprising a pipe connecting said first and second openings together as well as with an opening opening outside said additional block.

[0014] According to another aspect of the invention:

- the first orifice of the first circulation pipe opens onto a first face of the hydraulic block, said first orifice being intended to be a refrigerant fluid inlet,

- the second orifice of the first circulation pipe opens onto a second face of the hydraulic block, distinct from the first face, so as to allow direct circulation of the refrigerant fluid between the first orifice and the second orifice of the first circulation pipe,

- the first non-return valve is configured to allow the circulation of the refrigerant fluid from the first circulation pipe towards the third orifice of the first auxiliary pipe, therefore towards the pipe of the additional block, and to allow the circulation of the refrigerant fluid to be blocked from the third orifice of the first auxiliary pipe, therefore from the pipe of the additional block, towards the first circulation pipe,

- the first orifice of the second circulation pipe also opens onto the first face of the hydraulic block, said first orifice being intended to be a refrigerant fluid outlet,

- the second orifice of the second circulation pipe opens onto a second face of the hydraulic block, distinct from the first face, so as to allow direct circulation of the refrigerant fluid between the first orifice and the second orifice of the second circulation pipe,

- the second non-return valve is configured to allow the circulation of the refrigerant fluid from the third orifice of the second auxiliary pipe, therefore from the pipe of the additional block, towards the second circulation pipe, and to allow the circulation of the fluid to be blocked refrigerant from the second circulation pipe towards the third orifice of the second annex pipe, therefore towards the pipe of the additional block.

Other characteristics and advantages of the present invention will appear more clearly on reading the following description, provided by way of illustration and not limitation, and the appended drawings in which:

[0016] [Fig 1] Figure 1 shows a schematic perspective representation of a hydraulic block according to a first embodiment,

[0017] [Fig 2] Figure 2 shows a schematic representation in top view and in section of the hydraulic block of Figure 1,

[0018] [Fig 3] Figure 3 shows a schematic representation in perspective and in side section according to a first section plane of the hydraulic block of Figure 1,

[0019] [Fig 4] Figure 4 shows a schematic representation in perspective and in side section according to a second section plane of the hydraulic block of Figure 1,

[0020] [Fig 5] Figure 5 shows a schematic representation in exploded perspective of an assembly for a desiccant tank according to a first embodiment, [0021] [Fig 6] Figure 6 shows a schematic representation in exploded perspective of an assembly for a desiccant tank according to a second embodiment,

[0022] [Fig 7] Figure 7 shows a schematic representation in top view and in section of a hydraulic block with an additional block according to a second embodiment, [0023] [Fig 8] Figure 8 shows a representation schematic in perspective and section of the hydraulic block and the additional block of Figure 7,

[0024] [Fig 9] Figure 9 shows a schematic perspective representation of the hydraulic block and the additional block of Figure 7,

[0025] [Fig 10] Figure 10 shows a schematic perspective representation of the hydraulic block of Figure 9.

[0026] In the different figures, identical elements bear the same reference numbers.

The following achievements are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment, or that the features only apply to a single embodiment. Simple features of different embodiments may also be combined and/or interchanged to provide other embodiments.

[0028] In the present description, certain elements or parameters can be indexed, such as for example first element or second element as well as first parameter and second parameter or even first criterion and second criterion, etc. In this case, it is a simple indexing to differentiate and name elements or parameters or criteria that are close, but not identical. This indexing does not imply a priority of one element, parameter or criterion in relation to another and such denominations can easily be interchanged without departing from the scope of this description. This indexing does not imply an order in time either, for example to assess this or that criterion.

[0029] In the present description, the term “placed upstream” means that one element is placed before another with respect to the direction of circulation of a fluid. Conversely, by “placed downstream” we mean that one element is placed after another in relation to the direction of circulation of the fluid.

[0030] Figure 1 shows a hydraulic block 3 for refrigerant fluid of a thermal management circuit of a motor vehicle. This hydraulic block 3 is intended in particular to be integrated into a compact thermal management circuit in order to direct the flow of refrigerant fluid. This hydraulic block 3 can in particular be made of metal, for example aluminum or aluminum alloy.

The hydraulic block 3 thus comprises within it at least a first circulation pipe A of refrigerant fluid (visible in Figure 2 showing a top view and in section of the block 3 of Figure 1). This first circulation pipe A comprises in particular a first orifice Al opening onto a face 3a, 3b, 3c of the hydraulic block 3 and a second orifice A2 opening onto a face 3a, 3b, 3c of the hydraulic block 3. The refrigerant fluid circulating within of this first circulation pipe A thus circulates between these two orifices Al, A2. The first circulation pipe A also comprises a first annex pipe A' connecting said first circulation pipe A to a third port A3 (also visible in Figure 2).

[0032] The hydraulic block 3 further comprises a first housing RI sinking into the first annex pipe A' from a first opening 01 made on a face 3a, 3b, 3c of the hydraulic block 3. The first housing RI can thus extend within the hydraulic block 3 along a parallel axis and preferably coincident with an axis of elongation of the first annex pipe A'. Thus, the first housing RI can extend the first annex pipe A' to a face 3a, 3b, 3c of the hydraulic block 3.

The hydraulic block 3 also includes a first non-return valve V 1 (visible in Figure 2) completely inserted within said first housing RI and configured to block the circulation of the refrigerant fluid between one of the orifices Al, A2, A3 of the first circulation pipe A with another of said orifices Al, A2, A3. By completely inserted, we mean here that the first non-return valve V 1 is inserted in its entire thickness within the first housing RI so that it does not protrude from said first housing RL. The first housing RI can be formed entirely within the block hydraulic 3 according to a first embodiment described below and illustrated in Figures 1 to 6. The first housing RI can also be formed by the association of the hydraulic block 3 and an additional block 4 according to a second embodiment described more far and illustrated in Figures 7 to 10. The orientation of the first non-return valve V 1 can vary according to the needs and the place of the hydraulic block 3 within the thermal management circuit.

[0034] The first non-return valve V 1 can in particular be surrounded by one or more sealing means such as a seal. The first non-return valve V 1 can also be held in place within the first housing RI by one or more holding elements (not shown) such as an elastic ring.

[0035] The fact of completely integrating the first non-return valve VI within a first dedicated housing RI makes it possible to group several redirection and connection functions within the same compact element. This is particularly useful in order to reduce the bulk of the thermal management circuit as a whole within the motor vehicle.

The hydraulic block 3 can also include within it a second refrigerant fluid circulation pipe B allowing the circulation of the refrigerant fluid between a first orifice B1 opening onto a face 3a, 3b, 3c of the hydraulic block 3 and a second orifice B2 opening onto a face 3a, 3b, 3c of the hydraulic block 3. The hydraulic block 3 may also include a second annex pipe B', connecting said second circulation pipe B to a third orifice B3.

[0037] The hydraulic block 3 can also include a second housing R2 sinking into the second annex pipe B' from a second opening 02 made on a face 3a, 3b, 3c of the hydraulic block 3. The second housing R2 can thus extend within the hydraulic block 3 along a parallel axis and preferably coincident with an axis of elongation of the second annex pipe B'. Thus, the second housing R2 can extend the second annex pipe B' to a face 3a, 3b, 3c of the hydraulic block 3.

[0038] The hydraulic block 3 also includes a second non-return valve V2 inserted completely within said second housing R2 and configured to block the circulation of the refrigerant fluid between one of the orifices Bl, B2, B3 of the second circulation pipe B with another of said orifices Bl, B2, B3. By completely inserted, we mean here that the second non-return valve V2 is inserted in its entire thickness within the second housing R2 so that it does not protrude from said second housing R2. The second housing R2 can be formed entirely within the hydraulic block 3 according to a first embodiment described below and illustrated in Figures 1 to 6. The second housing R2 can also be formed by the association of the hydraulic block 3 and an additional block 4 according to a second embodiment described below and illustrated in Figures 7 to 10. As with the first non-return valve VI, the orientation of the first non-return valve V2 can vary according to needs and the place of the hydraulic block 3 within the thermal management circuit.

The second non-return valve V2 can in particular be surrounded by one or more sealing means such as a seal. The second non-return valve V2 can also be held in place within the second housing R2 by one or more holding elements (not shown) such as an elastic ring.

[0040] The fact of having two circulation pipes with non-return valves VI, V2 completely integrated within dedicated housings RI, R2 makes it possible to group several redirection and connection functions within the same compact element. This is particularly useful in order to reduce the bulk of the thermal management circuit as a whole within the motor vehicle.

[0041] According to a first embodiment illustrated in Figures 1 to 4, the first opening 01 of the first housing RI can be distinct from the orifices Al, A2, A3 of the first circulation pipe A and the first opening 01 is obstructed by a closing means 31. This closing means 31 may in particular be a plug screwed into the first opening 01. The closing means 31 may in particular have one or more sealing means such as a seal.

Likewise, the second opening 02 of the second housing R2 can also be distinct from the orifices Bl, B2, B3 of the second circulation pipe B and said second opening 02 can be obstructed by a closing means 32. This means shutter 32 may in particular be a screwed cap within the second opening 02. The shutter means 32 may in particular have one or more sealing means such as a seal.

[0043] In the example illustrated in Figures 1 to 4, the third orifice A3 of the first annex pipe A' opens onto a face 3a, 3b, 3c of the hydraulic block 3. The third orifice B3 of the second annex pipe B' opens into the first annex pipe A' between the third orifice A3 of the first annex pipe A' and the first non-return valve V 1.

[0044] Still according to the example illustrated in Figures 1 to 4, the first orifice Al of the first circulation pipe A opens onto a first face 3a of the hydraulic block 3. This first orifice Al is intended in particular to be a fluid inlet refrigerant. The second orifice A2 of the first circulation pipe A opens onto a second face 3b, 3c of the hydraulic block 3, distinct from the first face 3a, so as to allow direct circulation of the refrigerant fluid between the first orifice Al and the second orifice A2 of the first circulation pipe A. By direct circulation, we mean here that the refrigerant fluid can circulate directly between these two orifices Al, A2 without passing through a pipe other than the first circulation pipe A and without crossing a stopping or regulating element such as a stop or non-return valve for example.

The first non-return valve V 1 can then be configured to allow the circulation of the refrigerant fluid from the first circulation pipe A towards the third orifice A3 of the first annex pipe A' and to allow the circulation of the fluid to be blocked refrigerant from the third port A3 of the first annex pipe A' to the first circulation pipe A.

The first orifice B 1 of the second circulation pipe B can also open onto the first face 3a of the hydraulic block 3. This first orifice B1 can then be intended to be a refrigerant fluid outlet.

The second orifice B2 of the second circulation pipe B can open onto a second face 3b, 3c of the hydraulic block 3, distinct from the first face 3a, so as to allow direct circulation of the refrigerant fluid between the first orifice B 1 and the second orifice B2 of the second circulation pipe B. By direct circulation, we mean here that the refrigerant fluid can circulate directly between these two orifices Bl, B2 without passing through any pipe other than the second circulation pipe B and without pass through a stopping or regulating element such as a shut-off or non-return valve for example.

The second non-return valve V2 can then be configured to allow the circulation of the refrigerant fluid from the third orifice B 3 of the second annex pipe B', therefore from the first annex pipe A', towards the second circulation pipe B and to allow the circulation of the refrigerant fluid to be blocked from the second circulation pipe B towards the third orifice B 3 of the second annex pipe B', therefore towards the first annex pipe A'.

The hydraulic block 3 can in particular be intended to be fluidly connected to a desiccant tank 2, as illustrated in Figure 5.

The desiccant tank 2 extends more particularly along a longitudinal axis L and is intended to receive refrigerant fluid. This desiccant tank 2 has a first closed end 2a and a second end 2b, opposite the first end 2a, comprising an inlet 21 of refrigerant fluid and an outlet 22 of refrigerant fluid. The desiccant tank 2 can in particular be fixed on a first face 3a of the hydraulic block 3. The first face 3a then comprises the first orifice Al of the first circulation pipe A and the first orifice B 1 of the second circulation pipe B.

The second end 2b of the desiccant tank 2 further comprises at least one offset 24 extending perpendicular to the longitudinal axis L. This at least one offset 24 may include at least one means of attachment with the hydraulic block 3. This way of fixation can be for example through orifices complementary to other orifices 35 provided on the first face 3a of the hydraulic block 3. The orifices 35 of the hydraulic block 3 can more particularly be tapped in order to receive screws or bolts for fixing the desiccant tank 2 .

[0053] In order to enable keying when fixing the desiccant tank 2 to the hydraulic block 3, the fixing means 25 may in particular be of an odd number, for example three, or arranged irregularly around the desiccant tank 2 This thus makes it possible to connect the orifice playing the role of refrigerant outlet of the hydraulic block 3 to the refrigerant fluid inlet 21 of the desiccant tank 2 and makes it possible to connect the orifice playing the role of refrigerant fluid inlet of the hydraulic block 3 at the refrigerant fluid outlet 22 of the desiccant tank 2.

[0054] Another means of foolproofing can also be to use different fluidic connection diameters between the desiccant tank 2 and the hydraulic block 3, or even not to align these fluidic connections with the center of the desiccant tank 2.

The desiccant tank 2 may in particular include within it a dip tube 23 extending from its second end 2b towards its first end 2a, over a length of at least 70% of said desiccant tank 2.

[0056] According to a first alternative illustrated in Figure 5, this dip tube 23 is connected to the refrigerant fluid inlet 21 of said desiccant tank 2. This thus makes it possible to connect the first end 2a of the desiccant tank 2 to the inlet 21 of refrigerant fluid and thus position the desiccant tank 2 with its first end 2a oriented upwards and its second end 2b, with the fluidic connections, downwards. Here, up and down mean positioning relative to Earth's gravity. The outlet 22 is connected directly to the second end 2b and is thus positioned at the bottom, the latter, due to gravity, will only allow the evacuation of the refrigerant fluid in its liquid state.

[0057] This particular positioning with the second end 2b of the desiccant tank 2 can in particular allow improved assembly and maintenance of the desiccant tank 2, the latter being able to simply be placed on the block 3 before being fixed, without the need for means for keep it in place for example.

[0058] According to a second alternative illustrated in Figure 6, the dip tube 23 is connected to the refrigerant fluid outlet 22 of said desiccant tank 2. This thus makes it possible to connect the first end 2a of the desiccant tank 2 to the fluid outlet 22 refrigerant and thus position the desiccant tank 2 with its first end 2a oriented downwards and its second end 2b, with the fluidic connections, upwards. Due to gravity, outlet 22 will only allow the refrigerant to be evacuated in its liquid state. Input 21 is directly connected to the second end 2b and is positioned at the top.

[0059] According to one or the other of these alternatives, the first orifice B 1 of the second circulation pipe B can thus play the role of refrigerant fluid outlet from the second circulation pipe B and be fluidly connected to the refrigerant fluid inlet 21 of the desiccant tank 2. The second B2 and third B3 orifices then play the role of inlet of refrigerant.

The first orifice Al of the first circulation pipe A can for its part play the role of refrigerant fluid inlet of the first circulation pipe A and be fluidly connected to the refrigerant fluid outlet 22 of the desiccant tank 2. The second orifice A2 then plays a refrigerant outlet role and the third orifice A3 can play a refrigerant inlet or outlet role as required.

[0061] The second orifices A2 and B2 of the first A and second B circulation pipes can for their part be arranged on a so-called lateral face 3b of the hydraulic block 3. By lateral face 3b, we mean more particularly a face of the hydraulic block 3 contiguous to the first face 3a and which marks an angle with the latter, for example an angle substantially perpendicular to the first face 3a and parallel to the longitudinal axis L of the desiccant tank 2.

[0062] Such an assembly 1 allows in particular easy fixing of the desiccant tank 2 on the hydraulic block 3 in particular for the manufacture of a compact thermal management circuit as well as for good access to the desiccant tank in the event of a need for maintenance of this last. In addition, the use of such a hydraulic block 3 allows simpler assembly and integration within a thermal management circuit including other elements, such as pipes, valves, regulators or even elements such as the pump, are also integrated into hydraulic blocks for the sake of compactness of the thermal management circuit.

[0063] In the example illustrated in Figures 1 to 6, the same side face 3b carries the second orifice B2 of the second circulation pipe B and the third orifice A3 of the first annex pipe A'. It is however entirely possible to imagine an embodiment in which these orifices B2, B3 are arranged on different side faces 3b. The third orifice B3 of the second annex pipe B’ can be arranged on a separate side face 3b. The side face(s) 3b carrying these orifices B2, A3, B3 may also include fixing means 36 for fixing to another hydraulic block another element connecting to the second orifice B2 of the second circulation pipe B and /or at the third port A3 of the first annex pipe A' and/or the third port B3 of the second annex pipe B'. The openings 01 and 02 of the first RI and second R2 housings are also arranged on side faces 3b of the hydraulic block 3.

[0064] In the example illustrated in Figures 1 to 6, the hydraulic block 3 has a generally parallelepiped shape comprising a first face 3a, a second face 3c, opposite the first face 3a, and lateral faces 3b connecting the first face 3a to the second face 3c, here four side faces. Other shapes of the connection and distribution block 3 can in particular be considered with more or fewer side faces for example.

[0065] Within the thermal management circuit, the second orifice A2 of the first circulation pipe A can for example be fluidly connected to one or more heat exchangers having the role of evaporator or cooler, that is to say i.e. configured to increase the heat energy of the refrigerant fluid. Such a heat exchanger can example be an evaporator of an air conditioning circuit to cool an air flow intended for the passenger compartment and/or a cooler for cooling the batteries of an electric or hybrid vehicle. More precisely, the second port A2 can be fluidly connected to one or more expansion valves arranged upstream of these heat exchangers.

The second orifice B2 of the second circulation pipe B can for its part be fluidly connected to an internal condenser configured to heat an internal air flow intended for the passenger compartment.

[0067] Finally, in this first embodiment, the third orifice A3 of the first annex pipe A3 is fluidly connected to an evapo/condenser, for example placed on the front of the motor vehicle. More particularly, this third orifice A3 can be fluidly connected to an expansion valve which can be passed through in both directions by the refrigerant fluid.

[0068] Figures 5 and 6 show the circulation of the refrigerant fluid with arrows according to a cooling operating mode, the refrigerant fluid, coming from F evapo/condenser having a condenser function, enters the hydraulic block 3 via the third port A3 of the first annex pipe A'. The refrigerant fluid is blocked by the first non-return valve VI, enters the second annex pipe B' via its third port B3 and passes through the second non-return valve V2. The refrigerant joins the second circulation line B and enters the desiccant tank 2 via the first orifice B1 of the second circulation line B. The refrigerant fluid does not exit through the second orifice B2 of the second circulation line B because for example a non-return valve or controllable stop valve fluidly connected to said second port B2. After passing through the desiccant tank 2, the refrigerant fluid returns to the hydraulic block 3 via the first orifice Al of the first circulation pipe A and joins the second orifice A2 of said first circulation pipe A. The first non-return valve V 1 is closed and does not allow the refrigerant fluid to return to the first auxiliary pipe.

[0069] In a heat pump operating mode, the refrigerant fluid, coming from the internal condenser, enters the hydraulic block 3 through the second orifice B2 of the second circulation pipe B. The refrigerant fluid passes through the second circulation pipe circulation B and enters the desiccant tank 2 via the first orifice B1 of the second circulation pipe B. The refrigerant fluid does not circulate in the second annex pipe B' because it is blocked by the second non-return valve V2. After passing through the desiccant tank 2, the refrigerant fluid returns to the hydraulic block 3 via the first orifice Al of the first circulation pipe A, passes through the first annex pipe A' due to the fact that the first non-return valve V 1 lets it pass the refrigerant fluid. The refrigerant fluid leaves the hydraulic block 3 via the third port A3 of the first annex pipe A'. At the outlet of the third orifice A3 of the first annex pipe A', the refrigerant fluid passes through an expansion valve in order to undergo a loss of pressure before joining F evapo/condenser which here plays the role of evaporator. Refrigerant does not come out or circulate in the first circulation line A and does not emerge via the second orifice A2 for example due to the presence of a closed stop valve placed downstream of said second orifice A2 or due to the closing of the expansion valve(s) placed downstream in the thermal management circuit. The second non-return valve V2 being closed, the latter prevents the refrigerant fluid circulating in the first annex pipe A' from returning to the second circulation pipe B via the third orifice B 3 of the second annex pipe B'.

[0070] Other operating modes are also possible, in particular an operating mode in which the refrigerant fluid can exit simultaneously through the orifices A2 and A3 or from one or other of the orifices A2 or A3 in order to ensure other functions of the thermal management circuit of a motor vehicle, such as for example a heat recovery mode at the level of elements such as the batteries to help heat the passenger compartment or even dehumidification modes in series or in parallel.

[0071] According to a second embodiment illustrated in Figures 7 to 10, the first opening 01 of the first housing RI can also be the third orifice A3 of the first annex pipe A'. Likewise, the second opening 02 of the second housing R2 can also be the third orifice B 3 of the second annex pipe B.

[0072] According to this second embodiment, the hydraulic block 3 may in particular include an additional block 4 attached to it. This additional block A covers more particularly the first 01 and second 02 openings. The additional block 4 comprises a pipe C connecting the first 01 and second 02 openings to each other as well as to an orifice C3 opening outside of said additional block 4.

[0073] In this second embodiment, the first RI and second R2 housing can be arranged entirely within the hydraulic block 3 or straddle between the hydraulic block 3 and the additional block 4. The first VI and/or the second V2 non-return valve are thus completely inserted respectively within the first RI and the second R2 housing, but can also be straddled between the hydraulic block 3 and the additional block 4.

[0074] Still according to this second embodiment, the first orifice Al of the first circulation pipe A can open onto a first face 3a of the hydraulic block 3. This first orifice Al is intended to be a refrigerant fluid inlet.

[0075] The second orifice A2 of the first circulation pipe A can open onto a second face 3b, 3c of the hydraulic block 3, distinct from the first face 3a, so as to allow direct circulation of the refrigerant fluid between the first orifice Al and the second orifice A2 of the first circulation pipe A. By direct circulation, we mean here that the refrigerant fluid can circulate directly between these two orifices Al, A2 without passing through any pipe other than the first circulation pipe A and without crossing a stopping or regulating element such as a shut-off or non-return valve for example.

[0076] The first non-return valve V 1 can be configured here to allow the circulation of the refrigerant fluid from the first circulation pipe A towards the third orifice A3 of the first annex pipe A', therefore towards pipe C of the additional block 4. The first first non-return valve V 1 is also configured here to allow the circulation of the refrigerant fluid to be blocked from the third orifice A3 of the first annex pipe A', therefore from pipe C of the additional block 4, towards the first circulation pipe A .

The first orifice B 1 of the second circulation pipe B can also open onto the first face 3a of the hydraulic block 3. This first orifice Bl is in particular intended to be a refrigerant fluid outlet.

[0078] The second orifice B2 of the second circulation pipe B can open onto a second face 3b, 3c of the hydraulic block 3, distinct from the first face 3a, so as to allow direct circulation of the refrigerant fluid between the first orifice B 1 and the second orifice B2 of the second circulation pipe B. By direct circulation, we mean here that the refrigerant fluid can circulate directly between these two orifices Bl, B2 without passing through any pipe other than the second circulation pipe B and without crossing a stopping or regulating element such as a shut-off or non-return valve for example.

The second non-return valve V2 is here configured to allow the circulation of the refrigerant fluid from the third orifice B3 of the second annex pipe B', therefore from the pipe C of the additional block 4, towards the second circulation pipe B The second non-return valve V2 is also configured here to block the circulation of the refrigerant fluid from the second circulation pipe B towards the third orifice B3 of the second annex pipe B', therefore towards pipe C of the additional block.

[0080] Like the first embodiment, the hydraulic block 3 of the second embodiment can be intended to be fluidly connected to a desiccant tank 2 like that described above.

[0081] Likewise for the first embodiment, according to one or other of the positioning alternatives of the desiccant tank 2, the first orifice Bl of the second circulation pipe B can thus play a role of fluid outlet refrigerant from the second circulation line B and be fluidly connected to the refrigerant fluid inlet 21 of the desiccant tank 2. The second B2 and third B3 orifices then play the role of refrigerant fluid inlet.

The first orifice Al of the first circulation pipe A can for its part play the role of refrigerant fluid inlet of the first circulation pipe A and be fluidly connected to the refrigerant fluid outlet 22 of the desiccant tank 2. The second orifice A2 then plays a refrigerant outlet role and the third orifice A3 can play a refrigerant outlet role as required.

[0083] The second orifices A2 and B2 of the first A and second B circulation pipes can for their part be arranged on a so-called lateral face 3b of the hydraulic block 3. By lateral face 3b, we mean more particularly a face of the hydraulic block 3 contiguous to the first face 3a and which marks an angle with the latter, for example an angle substantially perpendicular to the first face 3a and parallel to the longitudinal axis L of the desiccant tank 2. [0084] Such an assembly 1 allows in particular easy fixing of the desiccant tank 2 on the hydraulic block 3 in particular for the manufacture of a compact thermal management circuit as well as for good access to the desiccant tank in the event of a need for maintenance of this last. In addition, the use of such a hydraulic block 3 allows simpler assembly and integration within a thermal management circuit including other elements, such as pipes, valves, regulators or even elements such as the pump, are also integrated into hydraulic blocks for the sake of compactness of the thermal management circuit.

[0085] In the example illustrated in Figures 7 to 10, the same side face 3b carries the openings 01 and 02, that is to say, in this second embodiment, the third orifice A3 of the first annex pipe A' and the third orifice B3 of the second annex pipe B'. The additional block 4 is attached and fixed to this side face 3b in order to be in fluid connection with these third orifices A3, B3. It is however entirely possible to imagine an embodiment in which these orifices A3, B3 are arranged on different side faces 3b and in which the additional block 4 has a shape adapted to be in fluidic connection with the latter. The second orifices A2 and B2 of the first A and the second B circulation pipe can be arranged on side faces 3b distinct from each other and distinct from that carrying the openings 01 and 02. The or the side faces 3b carrying these orifices A2, B2, A3, B3 can also include fixing means 36 for fixing to another hydraulic block of another element connecting to the hydraulic block 3.

[0086] In the example illustrated in Figures 7 to 10, the hydraulic block 3 has a generally parallelepiped shape comprising a first face 3a, a second face 3c, opposite the first face 3a, and lateral faces 3b connecting the first face 3a to the second face 3c, here four side faces. Other shapes of the connection and distribution block 3 can in particular be considered with more or fewer side faces for example.

[0087] The additional block 4 can also have a parallelepiped shape like the hydraulic block 3. The orifice C3 can in particular be arranged on a side face of the additional block 4. As illustrated in Figures 7 to 10, the face side of the additional block 4 carrying its orifice C3 can be parallel and contiguous to the lateral face 3b of the hydraulic block 3 carrying the second orifice B2 of the second circulation pipe B. This arrangement allows in particular an easier connection with another hydraulic block by example.

[0088] Within the thermal management circuit, the second orifice A2 of the first circulation pipe A can for example be fluidly connected to one or more heat exchangers having the role of evaporator or cooler, that is to say i.e. configured to increase the heat energy of the refrigerant fluid. Such a heat exchanger can for example be an evaporator of an air conditioning circuit for cooling an air flow intended for the passenger compartment and/or a cooler for cooling the batteries of an electric or hybrid vehicle. More precisely, the second port A2 can be fluidly connected to one or more expansion valves arranged upstream of these heat exchangers. [0089] The second orifice B2 of the second circulation pipe B can for its part be fluidly connected to an internal condenser configured to heat an internal air flow intended for the passenger compartment.

[0090] Finally, in this second embodiment, the orifice C3 of the pipe C of the additional block 4 is fluidly connected to an evapo/condenser, for example placed on the front of the motor vehicle. More particularly, this orifice C3 can be fluidly connected to an expansion valve which can be passed through in both directions by the refrigerant fluid.

[0091] In a cooling operating mode, the refrigerant fluid, coming from F evapo/condenser having a condenser function, enters the additional block 4 through the orifice C3 of its pipe C. The refrigerant fluid is blocked by the first non-return valve VI and cannot reach the first circulation pipe. The refrigerant fluid passes through the second non-return valve V2 and joins the second circulation line B before entering the desiccant tank 2 via the first orifice B 1 of the second circulation line B. The refrigerant does not exit through the second orifice B2 of the second circulation pipe B due for example to a non-return valve or controllable stop valve fluidly connected to said second orifice B2. After passing through the desiccant tank 2, the refrigerant fluid returns to the hydraulic block 3 via the first orifice Al of the first circulation pipe A and joins the second orifice A2 of said first circulation pipe A. The first non-return valve V 1 is closed and does not allow the refrigerant fluid to return to the first annex pipe A' and to pipe C of the additional block 4.

[0092] In a heat pump operating mode, the refrigerant fluid, coming from the internal condenser, enters the hydraulic block 3 through the second orifice B2 of the second circulation pipe B. The refrigerant fluid passes through the second circulation pipe circulation B and enters the desiccant tank 2 via the first orifice B1 of the second circulation pipe B. The refrigerant fluid does not circulate in the second annex pipe B' because it is blocked by the second non-return valve V2. After passing through the desiccant tank 2, the refrigerant fluid returns to the hydraulic block 3 via the first orifice Al of the first circulation pipe A, passes through the first annex pipe A' due to the fact that the first non-return valve V 1 lets it pass the refrigerant fluid. The refrigerant fluid emerges from the hydraulic block 3 via the third port A3 of the first annex pipe A' and joins the pipe C of the additional block 4 to exit via its port C3. At the outlet of port C3 of pipe C of additional block 4, the refrigerant fluid passes through an expansion valve in order to undergo a loss of pressure before joining F evapo/condenser which here plays the role of evaporator. The refrigerant fluid does not emerge or circulate in the first circulation pipe A and does not emerge via the second orifice A2 for example due to the presence of a closed stop valve disposed downstream of said second orifice A2 or else due to the closing of the expansion valve(s) located downstream in the thermal management circuit. The second non-return valve V2 being closed, the latter prevents the refrigerant fluid circulating in line C of the additional block 4 from returning to the second circulation line B via the third orifice B 3 of the second annex pipe B'.

[0093] Likewise, other modes of operation are also possible, in particular a mode of operation in which the refrigerant fluid can exit simultaneously through the orifices A2 and A3 or from one or other of the orifices A2 or A3 in order to ensure other functions of the thermal management circuit of a motor vehicle, such as for example a heat recovery mode at the level of elements such as the batteries to help heat the passenger compartment or even series dehumidification modes or in parallel.

[0094] Thus, we can clearly see that the hydraulic block 3, in particular by completely integrating at least one non-return valve VI, V2 within a dedicated housing RI, R2, makes it possible to group several redirection functions and connection within the same compact element.

Claims

Claims [Claim 1] Hydraulic block (3) for refrigerant fluid of a thermal management circuit of a motor vehicle, said hydraulic block (3) comprising within it at least a first circulation pipe (A) of refrigerant fluid between a first orifice (Al) opening onto one face (3a, 3b, 3c) of the hydraulic block (3) and a second orifice (A2) opening onto one face (3a, 3b, 3c) of the hydraulic block (3), the first circulation pipe (A) comprising a first auxiliary pipe (A') connecting said first circulation pipe (A) to a third orifice (A3), the hydraulic block (3) further comprising a first housing (RI) machined and sinking into the within the first annex pipe (A') from a first opening (01) made on one face (3a, 3b, 3c) of the hydraulic block (3), said hydraulic block (3) comprising a first non-return valve (VI ) inserted completely within said first housing (RI) and configured to block the circulation of the refrigerant fluid between one of the orifices (Al, A2, A3) of the first circulation pipe (A) with another of said orifices (Al, A2, A3). [Claim 2] Hydraulic block (3) according to claim 1, characterized in that the first opening (01) of the first housing (RI) is distinct from the orifices (Al, A2, A3) of the first circulation pipe (A) and in that said first opening (01) is obstructed by a closing means (31). [Claim 3] Hydraulic block (3) according to claim 1, characterized in that the first opening (01) of the first housing (RI) is also the third orifice (A3) of the first auxiliary pipe (A’). [Claim 4] Hydraulic block (3) according to any one of the preceding claims, characterized in that it comprises a second circulation pipe (B) of refrigerant fluid between a first orifice (Bl) opening onto a face (3a, 3b, 3c) of the hydraulic block (3) and a second orifice (B2) opening onto one face (3a, 3b, 3c) of the hydraulic block (3), the hydraulic block (3) comprising a second annex pipe (B') connecting said second circulation pipe (B) to a third orifice (B3), the hydraulic block (3) further comprising a second housing (R2) machined and sinking into the second annex pipe (B') from a second opening (02) made on one face (3a, 3b, 3c) of the hydraulic block (3), said hydraulic block (3) comprising a second non-return valve (V2) inserted completely within said second housing (R2) and configured to block the circulation of the refrigerant fluid between one of the orifices (Bl, B2, B3) of the second circulation pipe (B) with another of said orifices (Bl, B2, B3). [Claim 5] Hydraulic block (3) according to claim 4, characterized in that the second opening (02) of the second housing (R2) is distinct from the orifices (Bl, B2, B3) of the second circulation pipe (B) and in that said second opening (02) is obstructed by a closing means (32). [Claim 6] Hydraulic block (3) according to claim 4, characterized in that the second opening (02) of the second housing (R2) is also the third orifice (B 3) of the second annex pipe (B). [Claim 7] Hydraulic block (3) according to claims 2 and 5 in combination, characterized in that the third orifice (A3) of the first annex pipe (A') opens onto one face (3a, 3b, 3c) of the block hydraulic (3) and in that the third orifice (B 3) of the second annex pipe (B') opens into the first annex pipe (A') between the third orifice (A3) of the first annex pipe (A') and the first non-return valve (VI). [Claim 8] Hydraulic block (3) according to claim 7, characterized in that: - the first orifice (Al) of the first circulation pipe (A) opens onto a first face (3a) of the hydraulic block (3), said first orifice (Al) being intended to be a refrigerant fluid inlet, - the second orifice (A2) of the first circulation pipe (A) opens onto a second face (3b, 3c) of the hydraulic block (3), distinct from the first face (3a), so as to allow direct circulation of the refrigerant fluid between the first orifice (Al) and the second orifice (A2) of the first circulation pipe (A), - the first non-return valve (VI) is configured to allow the circulation of the refrigerant fluid from the first circulation pipe (A) towards the third orifice (A3) of the first annex pipe (A') and to allow the blocking of the circulation of the refrigerant fluid from the third orifice (A3) of the first annex pipe (A') towards the first circulation pipe (A), - the first orifice (Bl) of the second circulation pipe (B) also opens onto the first face (3a) of the hydraulic block (3), said first orifice (Bl) being intended to be a refrigerant fluid outlet, - the second orifice (B2) of the second circulation pipe (B) opens onto a second face (3b, 3c) of the hydraulic block (3), distinct from the first face (3a), so as to allow direct circulation of the refrigerant fluid between the first orifice (Bl) and the second orifice (B2) of the second circulation pipe (B), - the second non-return valve (V2) is configured to allow the circulation of the refrigerant fluid from the third orifice (B 3) of the second annex pipe (B'), therefore from the first annex pipe (A'), towards the second circulation pipe (B) and to allow the circulation of the refrigerant fluid to be blocked from the second circulation pipe (B) towards the third orifice (B3) of the second annex pipe (B'), therefore towards the first annex pipe ( HAS'). [Claim 9] Hydraulic block (3) according to claims 3 and 6 in combination, characterized in that it comprises an additional block (4) attached to and covering the first (01) and second (02) openings, said additional block ( 4) comprising a pipe (C) connecting said first (01) and second (02) openings to each other as well as to an orifice (C3) opening out to the outside of said additional block (4). [Claim 10] Hydraulic block (3) according to claim 9, characterized in that: - the first orifice (Al) of the first circulation pipe (A) opens onto a first face (3a) of the hydraulic block (3), said first orifice (Al) being intended to be a refrigerant fluid inlet, - the second orifice (A2) of the first circulation pipe (A) opens onto a second face (3b, 3c) of the hydraulic block (3), distinct from the first face (3a), so as to allow direct circulation of the refrigerant fluid between the first orifice (Al) and the second orifice (A2) of the first circulation pipe (A), - the first non-return valve (VI) is configured to allow the circulation of the refrigerant fluid from the first circulation pipe (A) towards the third orifice (A3) of the first annex pipe (A'), therefore towards the pipe ( C) of the additional block (4), and to allow the circulation of the refrigerant fluid to be blocked from the third orifice (A3) of the first annex pipe (A'), therefore from the pipe (C) of the additional block (4), towards the first circulation pipe (A), - the first orifice (Bl) of the second circulation pipe (B) also opens onto the first face (3a) of the hydraulic block (3), said first orifice (Bl) being intended to be a refrigerant fluid outlet, - the second orifice (B2) of the second circulation pipe (B) opens onto a second face (3b, 3c) of the hydraulic block (3), distinct from the first face (3a), so as to allow direct circulation of the refrigerant fluid between the first orifice (Bl) and the second orifice (B2) of the second circulation pipe (B), - the second non-return valve (V2) is configured to allow the circulation of the refrigerant fluid from the third orifice (B 3) of the second annex pipe (B'), therefore from the pipe (C) of the additional block (4) , towards the second circulation pipe (B), and to allow the circulation of the refrigerant fluid to be blocked from the second circulation pipe (B) towards the third orifice (B3) of the second annex pipe (B'), therefore towards the pipe (C) of the additional block.