Particularly for automatic coupling, active seal ring

Abstract

The invention relates to a seal ring for providing a fluid seal between a first flange and a second flange, the seal ring forming a tubular element and comprising a tapered wall member defining an internally funnelled through opening, the through opening extending axially and tapering from a proximal end to a distal end, the tapered wall member being made of an elastic material to provide axial deflection of the tapered wall member when subjected to an axial force.

Description

Technical Field

[0001] The present invention relates to a sealing ring for providing a fluid seal between a first flange and a second flange, the sealing ring forming a tubular element and including a tapering wall member defining an internal funnel-shaped through opening that extends axially and tapers from a proximal end to a distal end, the tapering wall member being made of an elastic material to provide axial deflection of the tapering wall member under axial force. Background Technology

[0002] In some practical implementations of pump supports, where the pump is located in a typically inaccessible location (such as a pump well), repairing or maintaining the pump support, and especially the pump itself (motor and pump housing with one or more impellers), is often very difficult due to limited space. One solution is to arrange the pump on a base in such a way that the pump is secured to the base by gravity acting on it. To allow for easy cleaning and maintenance of the pump without contact with sewage, a common solution is a system for easily lifting the pump out of the well and lowering it again, known as an auto coupling. Guide claws are attached to the pump to guide it during lifting / lowering on guide rods and to the base fixed to the bottom of the well. In the lower position, the pump is rigidly connected to the base via the guide claws at upper and lower contact points, using gravity to generate contact force. Lifting the pump unloads the contact force.

[0003] In this and other configurations, the flow path from the pump outlet to the base and through the base consists of various components that need to be sealed to each other to form a fluid-tight flow path, at least during pumping. While ordinary flat gaskets made of materials such as rubber, silicone, or other flexible materials can be arranged between the surfaces of the components, such gaskets have proven difficult to use in implementations utilizing guide claws. The less successful application of ordinary gaskets has several roots, one of the deeper ones being that such gaskets typically require manual handling of both the components to be sealed and the gasket itself to position all components in the sealing position.

[0004] Furthermore, standard flat gaskets require compression to achieve a tight seal. This presents several disadvantages, particularly in applications using guide claws and a base to allow the pump to connect to or disconnect from the outlet line during lowering or raising. One disadvantage is that the pump must be lowered and rotated at an angle to compress the gasket. If, in some cases, the angle is insufficient, there is a risk of the pump jamming before the guide claws and gasket are properly positioned, and the gasket will not be tight. Another disadvantage is that the sealing function is relatively sensitive to the positioning of the guide claws relative to the base.

[0005] Therefore, improved sealing rings would be advantageous, and in particular, the use of more effective and / or more reliable sealing rings would be advantageous.

[0006] Alternatively or in combination, it would be advantageous for the pump to be lowered at an angle and to be insensitive to the position of the guide claws relative to the base.

[0007] Purpose of the invention

[0008] One object of the present invention is to provide a sealing ring that solves one or more of the above-mentioned problems.

[0009] Another object of the present invention is to provide an alternative to the prior art. Summary of the Invention

[0010] Therefore, in a first aspect of the invention, the above-mentioned object and several other objects are intended to be achieved by providing a sealing ring for providing a fluid seal between a first flange and a second flange, the sealing ring forming a tubular element and comprising:

[0011] - A tapering wall member that defines an internal funnel-shaped through opening that extends axially and tapers gradually from the proximal end to the distal end. The tapering wall member is made of an elastic material that provides axial deflection of the tapering wall member when subjected to axial force.

[0012] - A first abutting surface is provided at the proximal end to provide a fluid seal when abutting one of the surfaces of the flange;

[0013] - A second abutment surface is provided at the distal end to provide a fluid seal when abutting another surface in the flange;

[0014] - A reinforcing member, made of a material with greater stiffness than the tapering wall member and shaped as a closed annular element, having an axial extension less than the axial distance between the proximal and distal ends, is arranged in or on the tapering wall member at an axial position between the proximal and distal ends, thereby limiting or preventing at least a portion of the tapering wall member from deflecting outward or inward when a pressure differential is applied to the tapering wall member.

[0015] The terminology used herein is in a manner commonly used by those skilled in the art. Some of these terms will be described in detail below:

[0016] The term "ring," as used in sealing rings, preferably means to refer to a closed-loop element or component, which can be, but is not limited to, circular. Therefore, a ring can also refer to a polygonal element or component.

[0017] "Gradually tapering wall member" is preferably used to refer to a member having two opposing wall sides, which are preferably tapering in the same direction.

[0018] As used herein, “elastic material” generally (though not in a limiting sense) refers to elastic materials such as elastomers that are typically nonlinear, hyperelastic materials, and / or materials having a Young’s modulus of up to 10% strain at about 2-5 MPa.

[0019] In some preferred embodiments of the sealing ring, the tapered wall members may have the shape of a truncated cone, and the reinforcing members may be circular members.

[0020] In some preferred embodiments of the sealing ring, the angle of the tapering wall member relative to the axial direction can be less than 75 degrees, such as less than 45 degrees, such as less than 40 degrees, preferably less than 35 degrees, such as less than 30 degrees, preferably less than 25 degrees, such as less than 20 degrees, preferably less than 15 degrees, and preferably greater than 10 degrees.

[0021] In some preferred embodiments of the sealing ring, the reinforcing member preferably has a uniform, preferably circular, cross-section over its entire extension.

[0022] In some preferred embodiments of the sealing ring, the reinforcing member can be embedded in the tapered wall member.

[0023] In some preferred embodiments of the sealing ring, the thickness of the tapering wall member can be locally increased in the region surrounding the embedded reinforcing member.

[0024] In some preferred embodiments of the sealing ring, the reinforcing member can be positioned axially at half the distance between the proximal and distal ends, or at the distal end.

[0025] In some preferred embodiments of the sealing ring, the sealing ring may include an annular protrusion that preferably extends outward at the proximal end, the outwardly extending annular protrusion having a first surface facing in a direction opposite to that toward the distal end and preferably defining at least a portion of a first abutment surface.

[0026] In some preferred embodiments of the sealing ring, the outwardly extending annular protrusion may be configured to be fastened to the first or second flange, for example by abutting against the first or second flange, preferably with the first abutting surface abutting against the surface of the first or second flange.

[0027] In some preferred embodiments of the sealing ring, the outwardly extending annular protrusion may include a recess preferably arranged opposite to a first abutting surface, the recess being preferably configured to cooperate with a clamping ring for clamping the annular protrusion against a first or second flange.

[0028] In some preferred embodiments of the sealing ring, the sealing ring may be configured to fit tightly into a recess provided in the first flange or the second flange.

[0029] In some preferred embodiments of the sealing ring, the distal end may have a second surface facing in the opposite direction to that toward the proximal end and preferably defining at least a portion of the second abutment surface.

[0030] In a second aspect, the present invention relates to a pump support, which preferably includes a first flange, a second flange, and a sealing ring according to the first aspect of the invention. The first and second flanges are preferably configured to be interconnected, with the sealing ring disposed between them. The two flanges include through openings that align with the sealing ring surrounding the opening when interconnected. Preferably, the first flange may be configured to support or form part of a pump housing, and the second flange may preferably form part of a fluid passage configured to receive fluid from the pump housing and deliver fluid at a delivery location. The sealing ring may be arranged to provide a seal between the first and second flanges.

[0031] In a third aspect, the present invention relates to a method for providing a seal between two flanges of a pump support according to a second aspect of the invention. The method preferably comprises:

[0032] - Position the sealing ring on one of the first and second flanges.

[0033] - Connect two flanges, wherein their through openings are aligned with a sealing ring surrounding the through openings. Attached Figure Description

[0034] The invention and its particularly preferred embodiments will now be described in more detail with reference to the accompanying drawings. The drawings illustrate embodiments of the invention and are not to be construed as limiting other possible embodiments falling within the scope of the appended claims.

[0035] Figure 1 A preferred embodiment of the pump support according to a preferred embodiment of the present invention is shown.

[0036] Figure 2 A cross-sectional view of a sealing ring according to a preferred embodiment of the present invention is shown, wherein the sealing ring is arranged in Figure 1 In the pump support shown,

[0037] Figure 3 as Figure 2 A close-up view shows the details of the sealing ring. Figure 3 has two illustrations. Figure 3A and Figure 3B ,in Figure 3B yes Figure 2 Another close-up view,

[0038] Figure 4 A three-dimensional view of a sealing ring according to a preferred embodiment of the present invention is shown.

[0039] [List of Labels in the Attached Image]

[0040] 1 pump

[0041] 2. Base section

[0042] 3 Guide claws

[0043] 4. Lower support section

[0044] 5. Upper support section

[0045] 6 Second horizontal support surface

[0046] 7 Second vertical support surface

[0047] 8. Top

[0048] 9. Lower end

[0049] 11 Second guiding component

[0050] 12 First guiding component

[0051] 13 Elastic elements

[0052] 14 Second vertical contact surface

[0053] 15 Second horizontal contact surface

[0054] 16 Supporting surfaces

[0055] 17 End face

[0056] 18. Vertically inclined contact surface

[0057] 19 First horizontal support surface

[0058] 20 Vertically extending lateral guiding planes

[0059] 21. Guiding opening

[0060] 22 guide rods

[0061] 23 Fluid Channels

[0062] 24 Through opening

[0063] 25. Depression

[0064] 26 Opening

[0065] 30 electric motors

[0066] 31 Sealing ring

[0067] 32 First flange

[0068] 33 Second flange

[0069] 35 Gradually tapering wall components

[0070] 36 Proximal

[0071] 37. Remote

[0072] 38 First contact surface

[0073] 39 Second contact surface

[0074] 40 Reinforcing Components

[0075] 41. Outwardly extending annular protrusions

[0076] 42 First Surface

[0077] 43. Depression

[0078] 44. Clamping ring

[0079] 45 Second Surface

[0080] 46 Pump support components

[0081] 47 gap

[0082] 48 holes

[0083] 49 thread Specific Implementation

[0084] Reference Figure 1 This illustrates a preferred embodiment of a pump support according to a preferred embodiment of the present invention.

[0085] Reference Figure 1 and 2 A particularly preferred application of the sealing ring according to the invention will be disclosed. Figure 1 and 2 A pump support is shown in particular, which has a pump 1 arranged on a base portion 2 by means of a guide claw 3.

[0086] According to a particularly preferred embodiment of the invention, the pump support has a first flange 32 on the guide claw 3, a second flange 33 on the base portion 2, and a sealing ring 31. The first and second flanges 32 and 33 are configured to be interconnected, and the sealing ring 31 is disposed between them. The configuration generally means that the size design of the flanges and the characteristics of their surfaces allow the sealing ring 31 to be accommodated between the flanges to provide a seal, at least during pump operation.

[0087] As from Figure 1 and2 As can be clearly seen, fluid from the pump flows through the guide claw 3 and enters a channel formed in the base portion 2. The fluid exits the base portion 2 through an opening at the rear end of the base portion 2. Therefore, the two flanges 32, 33 include through openings that align with a sealing ring 31 surrounding the openings when the two flanges are joined together. Thus, the first flange 32—or generally the guide claw 3—is configured to carry or form part of the pump housing, and the second flange 33 forms part of a fluid passage configured to receive fluid from the pump housing and deliver fluid at the delivery location, wherein the sealing ring 31 is arranged to provide a seal between the first flange 32 and the second flange 33.

[0088] When a sealing ring is applied to a pump construction, this typically involves arranging a sealing ring 31 on one of a first flange 32 and a second flange 33 and connecting the two flanges 32, 33, wherein their through openings are aligned with the sealing ring 31 surrounding the through openings.

[0089] Reference Figure 2 It shows a cross-sectional view of a sealing ring according to a preferred embodiment of the present invention, wherein the sealing ring is arranged in Figure 1 In the pump support shown.

[0090] Reference Figure 1 The figure illustrates a preferred embodiment of the pump support. The pump support may have a longitudinal direction, which in the illustrated embodiment is aligned with the flow direction of the pipe exiting the pump and entering the base.

[0091] The pump support member shown in the figure has a base portion 2, which has a lower end 9 and an upper end 8. The base portion 2 is configured to mount the pump support member at its lower end 9 to a pump support load-bearing member, such as a base plate. Figure 1 The base portion 25 is provided to receive a bolt screwed into the support member, thereby mounting the base portion 2 to the support member 10. In some embodiments, an elastic element may be arranged between the base portion 2 and the support member.

[0092] The base portion includes an end face 17. For example... Figure 2 As shown, end face 17 forms an opening into the tubular section of the base portion 2 (see Figure 17). Figure 2 The opening forms an inlet for receiving liquid from the pump. During use of the pump support, fluid flows through the opening in end face 17, through the tubular section, and exits the base portion 2 through the opening 26 in the base portion forming the outlet. A conduit (not shown) connects to the base portion 2 at the opening 26 to pump the pumped fluid to a location away from the base portion 2.

[0093] The pump support also includes a guide claw 3 adapted to carry the pump 1. The pump is connected to the guide claw via the outlet pipe of the pump 1. Figure 2 As can perhaps be most clearly seen, the guide claw 3 has a section between the pump flange and the base portion, allowing fluid to flow out of the pump 1, through the through opening 24, and into a channel provided in the base portion 2. As disclosed herein, a sealing ring 31 is provided between the guide claw 3 and the base portion 2. The pump 1 is shown bolted to the guide claw 3, but it may also be attached to the guide claw 3 in other ways, such as being integrally manufactured with the guide claw 3. Thus, in some preferred embodiments, the guide claw 3 forms part of a channel that guides fluid from the pump 1 to the opening 26.

[0094] As shown in the figure, the pump housing forms an internal cavity, and one or more impellers are arranged inside this internal cavity (not shown). The impeller is powered by an electric motor 30 (see Figure 30). Figure 1 The pump is driven, for example, by an impeller arranged on the rotating shaft of the motor. When the pump support is constructed with a motor and one or more impellers, the motor housing is arranged in a sealed manner at the upper opening of the pump housing 1. The pump 1 also includes a fluid inlet arranged below one or more impellers, such that when the motor is activated, the impellers (one or more) pump fluid through the inlet, through the impellers (one or more), and through the pump outlet pipe and through the opening in the guide claw 3 to the tubular section of the base portion 2.

[0095] The guide claw 3 is configured to connect the pump 1 to the base portion 2 at the end face 17. This connection is detachable, and to ensure, in particular, that the guide claw 3 is positioned on the base portion 2, the outlet of the pump 1 mates with the opening of the base portion 2. Figure 2 As shown in the diagram, the guide claw 3 is already equipped with a second guide member 11 and a first guide member 12. However, the second guide member 11 can be arranged at other locations on the guide claw 3.

[0096] The base portion 2 is provided with a support portion that cooperates with the guide member. A lower support portion 4 is provided and constructed at the lower end 9 to non-elastically support the pump in the longitudinal direction toward the base portion 2 and in the vertical direction toward the lower end 9. The lower support portion 4 serves as an end stop, which prevents the lower part of the guide claw 3 from moving downward and toward the base portion 2 when it is arranged on the base portion 2. The non-elasticity preferably means that no elastic material is arranged between the second guide member 11 and the lower support portion 4.

[0097] An upper support portion 5 is arranged at the upper end 8 of the base portion 2. The upper support portion 5 has a vertically inclined support surface 16 and is configured to support the first guide member 12. It should be emphasized that the support surface 16 may not be vertically inclined and may be vertical. During normal operation, there is no direct contact between the support surface 16 and the first guide member 12 because the elastic element 13 is placed between them.

[0098] As shown in the figure, the first guide member 12 is arranged in a retracted position relative to the front of the guide claw 3 and protrudes downward, thereby providing an opening into which the upper support portion 5 extends when the guide claw 3 is arranged on the base portion 2. The first guide member 12 extends downward at an angle, so that the opening in which the upper support portion 5 is arranged gradually tapers in the upward direction. If the support surface 16 is not inclined, the first guide member 12 preferably extends vertically without inclination. The elastic element 13 is fixed to the upper support portion 5 or the first guide member 12. Therefore, the elastic element 13 will not fall off when the guide claw is lifted.

[0099] The gradual taper between the upper support portion 5 and the first guide member 12 allows for easy manipulation of the guide claw 3 when positioned on the base portion 2, and generally ensures that the guide claw will not get stuck in an unexpected position on the base portion 2. Furthermore, the first guide member 12 engages with an elastic element 13 disposed between the upper support portion 5 and the first guide member 12, such that when gravity acts on the pump 1, it elastically forces the guide claw 3 toward the support surface 16. The reaction torque is absorbed by the contact point between the second guide member 11 and the first guide member 12.

[0100] Another effect of the tapering is that when the guide claw 3 is lowered onto the base portion 2, the upper support portion 5 will be guided to engage with the first guide member 12, with the elastic element 13 located between them.

[0101] In conjunction with the present invention, one or more elastic elements 13 serve an advantageous purpose in providing elasticity to the pump support, shifting the lowest natural frequency below the pump's lowest excitation frequency to avoid resonance. Such resonance is typically caused by the rotation of one or more impellers and / or motors, which can excite one or more natural frequencies of the pump support. If resonance cannot be avoided, even small forces from imbalances or passing blades will be amplified, resulting in vibration levels that can cause reliability problems in the pump and pump control. This is undesirable, and the combination of guide members 11, 12, elastic element 13, and supports 4, 5 is designed to avoid or at least mitigate the risk of such undesirable effects.

[0102] As disclosed above, the lower support 4 receives the second guide member 11 in a non-elastic manner and restricts the movement of the second guide member 11 toward the base 2 in the longitudinal direction. When the pump moves away from the base 2, the second guide member 11 can move horizontally in the direction away from the base 2, but during operation of the pump 1, this movement is prevented or at least minimized by the weight of the pump 1. It has been found that this rigid connection, together with the elastic element 13, is important for obtaining a resonant-free operating range for the pump 1.

[0103] At the upper part, the insertion of the elastic element 13 between the first guide member 12 and the upper support portion 5 provides an elastic connection between the guide claw 3 and the base portion 2. This arrangement provides a substantially rigid lower fixation of the guide claw 3 and a substantially elastic upper fixation of the guide claw 3 to the base portion 2, allowing for a certain degree of movement of the guide claw relative to the base portion 2. The result is typically that some of the natural frequencies of the guide claw 3, including the pump 1 and one or more, are altered, such as being reduced. In some specific embodiments, not all natural frequencies are reduced, but rather the three lowest natural frequencies are reduced while the upper natural frequency is kept high, resulting in a desired wide frequency range without natural frequencies. The lower natural frequency can be calculated for the pump mass (including water and the guide claw 3 supported by the pivot point at the second guide member 11), and the stiffness of the elastic element 13 defined by Young's modulus and dimensions. While the characteristics of the elastic element 13 (Young's modulus, dimensions) and the natural frequencies of the guide claw 3 including the pump can be calculated, these characteristics can also be determined experimentally. The lower natural frequency can be calculated for the pump mass (including water and the guide claw 3 supported by the pivot point at the second guide member 11), and the stiffness of the elastic element 13 defined by Young's modulus and dimensions. It can be determined by a full 3D model in a finite element model, as the relative position of the suspension point and the pump's center of gravity affects the calculation. Simultaneously, higher natural frequencies above the excitation (primarily dependent on the stiffness of the pump housing and guide claw) can be determined.

[0104] When designing the elastic element 13, a desirable objective is typically to change the lowest natural frequency to be lower than the pump's excitation. Generally, the excitation is generated by the impeller passing through the pump outlet, and this can be calculated based on the number of blades on the impeller and the impeller's rotational speed. In some cases, the excitation force with the lowest frequency is an unbalanced excitation where frequency = rotational speed (in rpm / 60). For example, a four-pole electric motor powered by a 50Hz power supply rotates at 50*2 / 4*60 = 1500 rpm. This causes an unbalanced excitation at 25Hz. However, if the variable frequency drive is set to half that speed, the unbalanced excitation becomes 12.5Hz. For example, if the impeller has one blade, rotates at a minimum of 750 RPM, and the pump has a single outlet, the characteristic vibration has a frequency of 12.5Hz. Therefore, when designing the elastic element 13, the objective is to ensure that the lowest natural frequency is below 12.5Hz.

[0105] like Figure 1 and 2 As shown, the guide claw 3 may have a guide opening 21 configured to cooperate with two vertically arranged guide rods 22, allowing the guide claw 3 to slide along the guide rods, thus the guide opening 21 serves as a guide member. The purpose of the guide rods 22 is to coarsely position the pump during descent so that the guide claw 3 can be connected to the base portion 2. The upwardly tapering angle on surfaces 21 and 16 is used to grip the guide claw during descent from the coarse position and move it to a more precise position where the pipe fittings are aligned. Preferably, the guide rods should not come into contact during normal operation.

[0106] like Figure 2 As shown, the sealing ring 31 is arranged to provide a fluid seal between the first flange 32 and the second flange 33 of the pump support. In this context, the flange is understood in a broad sense as, for example, two separate elements adapted to cooperate with each other to form a fluid connection via the sealing ring disposed therebetween. Figure 2 As shown, the sealing ring 31 is arranged coaxially with the openings in the flanges 32 and 33 to prevent fluid leakage between the flanges 32 and 33.

[0107] Figure 3 Figure 2 This allows you to see the details of the sealing ring more clearly. See also the image (see also...) Figure 4 The sealing ring 31 is a tubular element. The sealing ring 31 is described as having an axial direction and a radial direction, wherein the axial direction is aligned with the longitudinal direction of the tubular element, and the radial direction is perpendicular to the longitudinal direction. It should be noted that although the sealing ring is disclosed as circular, other shapes are also considered to be within the scope of the invention.

[0108] The sealing ring has a tapering wall member 35 that defines an internal funnel-shaped through opening that extends axially and tapers gradually from a proximal end 36 to a distal end 37. Thus, the proximal end 36 is defined as the end of the sealing ring with the largest opening, while the distal end 37 is defined as the opposite end. The sealing ring 31 is preferably arranged such that the narrowing direction of the tapering wall member is the same as the direction of fluid flow.

[0109] The tapering wall member 35 is made of an elastic material to provide axial deflection of the tapering wall member 35 when subjected to axial forces. This axial force is typically provided by fluid flowing through the sealing ring along the tapering direction. Since this fluid typically has a higher pressure than the pressure outside the sealing ring 31, the pressure difference provides the axial force inside the sealing ring. It should be noted that pressure is a force acting perpendicular to the surface, therefore the pressure difference provides both axial and radial forces (when pressure is considered in both geometric components). Radial forces will be discussed below with respect to the reinforcing member.

[0110] The sealing ring 31 has a first abutment surface 38 located at its proximal end 36 to provide a fluid seal when abutting the surface of one of the flanges 32, 33. This first abutment surface 38 is preferably shaped to geometrically conform to the shape of the flange surface to be abutted. Figure 2 In the embodiment shown, the surface of the flange 33 is flat and extends radially, and the first abutting surface is chamfered (shaped) relative to the course of the tapering wall member 35 to form a radially extending flat surface.

[0111] A second abutment surface 39 is disposed at the distal end 37 to provide a fluid seal when abutting the surface of another of the flanges 32, 33. With respect to the first abutment surface 38, the second abutment surface 39 is also preferably shaped to geometrically conform to the shape of the flange surface to be abutted. For the second abutment surface in the illustrated embodiment, this also means that the surface is chamfered (shaped) relative to the direction of the tapering wall member 35 to form a radially extending flat surface.

[0112] As described above, the pressure difference on the sealing ring 31 provides both axial and radial forces. While the axial force is used to provide or increase the sealing capability of the sealing ring, the radial force tends to deform the sealing ring 31 in an unfavorable manner. To increase the mechanical stability of the sealing ring 31 in the radial direction, a reinforcing member 40 is applied, made of a material (e.g., metal) with greater stiffness than the tapered wall member 35. In the illustrated embodiment, the reinforcing member 40 is shaped as a closed annular element with an axial extension less than the axial distance between the proximal end 36 and the distal end 37. Furthermore, the reinforcing member 40 may be arranged in or on the tapered wall member 35. In the illustrated embodiment, the reinforcing member 35 is positioned to be embedded within the tapered wall member 35 at an axial location between the proximal end 36 and the distal end 37. By providing a sealing ring 31 with such a relatively stiff reinforcing member 40, at least some of the radial force will be absorbed by this member, which limits or even prevents at least a portion of the tapered wall member 35 from deflecting outward when a pressure difference is applied to it. It should be noted that in the disclosed embodiments, the radial force is considered to act radially outward, but in the case of a radially inward force, the reinforcing member restricts or even prevents at least a portion of the tapering wall member 35 from deflecting inward.

[0113] As shown in Figure 3, the sealing ring 31 can be sized such that a gap 47 exists between the second abutting surface 39 of the sealing ring and the surface of the base portion 2. However, it is generally preferred that the sealing ring be sized such that this gap 47 is absent. This gap 47 forms a cavity because it provides an unsealed passage for the assembly of the pump support 46, or allows for tolerances or movement between the flanges, as will be disclosed below. As disclosed above, the guide claw 3 of the pump support is lowered onto the base portion 2. This lowering generally benefits from the high flexibility of the sealing ring 31, thereby reducing the risk of the guide claw getting stuck during the lowering of the guide claw 3 onto the base portion 2, at least to avoid damaging the sealing ring 1. Furthermore, since the pump support is typically used in environments where some leakage is acceptable during pumping operation (e.g., a fully submerged pump assembly), and the pump rapidly provides pressure in the fluid, thereby providing axial force on the sealing ring 31, the gap 47 will automatically close during startup due to the axial deflection of the sealing ring 31 caused by the pressure difference. This gap can even be found to be advantageous during startup, as it allows air trapped inside the pump housing to escape.

[0114] In the illustrated embodiment, the tapering wall member 35 has a truncated conical shape, and the reinforcing member 40 is a circular member. This is illustrated in Figure 3. Figure 4The most clearly shown is shown in Figure 3. It should be noted that the marked truncated conical shape refers to the overall shape of wall member 35 and [6], and as shown in Figure 3, this may include optional local thickening of wall member 35 in the area surrounding reinforcing member 40.

[0115] The tapering wall member 35 preferably has an angle of less than 75 degrees relative to the axial direction. Relative to the axial direction generally means that the axial direction forms one side when the angle is determined, and another side is formed through the centerline of the tapering wall member 35. In some preferred embodiments, this angle can be less than 45 degrees, such as less than 40 degrees, preferably less than 35 degrees, such as less than 30 degrees, preferably less than 25 degrees, such as less than 20 degrees, preferably less than 15 degrees, and preferably greater than 10 degrees. Without being theoretically constrained, an optimal angle of 45 degrees has been found, and advantageous solutions may be + / - 30 degrees or less than 75 degrees and greater than 15 degrees.

[0116] To achieve uniform reinforcement of the sealing ring 31, the reinforcing member 40 has a uniform, preferably circular, cross-section along its entire circumferential extension. However, different circumferential sections of the sealing ring 31 may have different cross-sections.

[0117] An advantageous way to introduce the reinforcing member 40 into the sealing ring 31 is to embed the reinforcing member 40 into the tapered wall member 35. Embedding generally means that no part of the reinforcing member 40 extends outside the wall member 35. This embedding can be provided by molding the wall member 35 in a mold, wherein the reinforcing member 40 is arranged in the mold before molding.

[0118] The axial position of the reinforcing member 40 may differ from that shown in Figure 3, in which the reinforcing member 40 is positioned at half the distance between the proximal end 36 and the distal end 37. For example, the reinforcing member 40 may be positioned at the distal end 37. However, in some cases, the sealing ring 31 is attached to one of the flanges 32 and 33, either at the distal end 37 or at the proximal end 36, and in this case, the reinforcing member 40 may advantageously be arranged at an axial distance from the attachment, since the attachment itself provides stiffness to the sealing ring 31 in both outward and inward directions.

[0119] As shown in Figure 3, the sealing ring 31 may have an outwardly extending annular protrusion 41 at the proximal end 36 of the tapering wall member 35. This outwardly extending annular protrusion 41 has a first surface 42 facing in a direction opposite to that towards the distal end 37 and defining at least a portion of a first abutment surface 38. In the embodiment shown in Figure 3, the first surface completely forms the first abutment surface 39. In many applications, the first surface 42 is sized to mate with the surface of the flange 32 to provide a fluid seal.

[0120] In the illustrated embodiment, the outwardly extending annular protrusion 41 is also configured to be fastened to the first or second flange (depending on the orientation of the sealing ring arrangement) for example by abutting against the first or second flange 32, 33, wherein the first abutting surface 8 abuts against the surface of the first or second flange 32, 33. This attachment can be provided in a manner different from clamping, such as vulcanization, gluing, or bolting. However, it is generally preferred to fasten the sealing ring 31 to the first flange 32, as this is part of the guide claw 2 after pumping out of the well, for easier maintenance.

[0121] In a preferred embodiment where the annular protrusion 41 is configured to clamp against a flange, the outwardly extending annular protrusion 41 advantageously has a recess 43 (see FIG. 3b) arranged opposite to the first abutment surface 38. In the embodiment shown in FIG. 3, this recess is formed as an annular notch extending 360 degrees through the sealing ring 31. The recess 43 is shaped to receive the protrusion of the clamping ring 44 and is thus configured to cooperate with the clamping ring 44 for clamping the annular protrusion 41 against the first or second flanges 32, 33. Clamping force is provided by bolting the clamping ring 44 to the flange, such as... Figure 3A The bid was successful. (For example...) Figure 3A As shown, a through hole 48 is provided in the guide claw 3, and a thread 49 is provided in the clamping ring 44. Therefore, when a bolt is inserted into the hole 48, the bolt can engage with the thread 49 in the clamping action to bias the clamping ring 44 onto the guide claw 3, thereby clamping the annular protrusion. The hole has an enlarged section on the side opposite the clamping ring 44, allowing the bolt head to be recessed into the guide claw 3 rather than protruding above the surface of the guide claw 3.

[0122] In an alternative embodiment (not shown), the sealing ring 31 is configured to fit snugly into a notch provided in the first flange 32 or the second flange 33. Typically, the sealing ring is press-fitted into the notch.

[0123] As shown in Figure 3, the distal end 37 of the sealing ring 31 has a second surface 45 facing in a direction opposite to that towards the proximal end 36 and defining at least a portion of the second abutment surface 39. In the illustrated embodiment, the second surface 45 completely forms the second abutment surface 39. Just as the dimensions of the first surface 42 are designed to mate with the surface of the flange 32 to provide a fluid seal, the dimensions of the second surface 45 may be designed to mate with the surface of the flange 33 to provide a fluid seal.

[0124] Although the invention has been described in conjunction with specific embodiments, it should not be construed in any way as limiting the described embodiments. The scope of the invention is defined by the appended set of claims. In the context of the claims, the terms "comprising" or "comprises" do not exclude other possible elements or steps. Similarly, references such as "a" or "an" should not be construed as excluding the plural. The use of reference numerals for elements indicated in the figures in the claims should also not be construed as limiting the scope of the invention. Furthermore, individual features mentioned in different claims may be advantageously combined, and mention of these features in different claims does not preclude the possibility and advantage of combining features.

Claims

1. A sealing ring (31) for providing a fluid seal between a first flange (32) and a second flange (33), the sealing ring (31) forming a tubular element and comprising: - A tapering wall member (35) defining an internal funnel-shaped through opening that extends axially and tapers from a proximal end (36) to a distal end (37), the tapering wall member (35) being made of an elastic material that provides axial deflection of the tapering wall member (35) when subjected to axial force; - A first abutting surface (38) is provided at the proximal end (36) to provide a fluid seal when abutting the surface of one of the flanges (32, 33); - A second abutment surface (39) is provided at the distal end (37) to provide a fluid seal when abutting the surface of another flange in the flanges (32, 33); - An annular protrusion (41) extending outward at the proximal end (36), the annular protrusion (41) having a first surface (42) facing in a direction opposite to that toward the distal end (37) and defining at least a portion of the first abutment surface (38); - A reinforcing member (40) made of a material with greater stiffness than the tapered wall member (35) and shaped as a closed annular element, the axial extension of which is less than the axial distance between the proximal end (36) and the distal end (37), the reinforcing member (40) being arranged in or on the tapered wall member (35) at an axial position between the proximal end (36) and the distal end (37), thereby limiting or preventing at least a portion of the tapered wall member (35) from deflecting outward or inward when a pressure differential is applied to the tapered wall member (35).

2. The sealing ring according to claim 1, wherein, The tapering wall member (35) has a truncated conical shape and the reinforcing member (40) is a circular member.

3. The sealing ring according to claim 1, wherein, The gradually tapering wall member (35) has an angle of less than 75 degrees relative to the axial direction.

4. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle of less than 45 degrees relative to the axial direction.

5. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle of less than 40 degrees relative to the axial direction.

6. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle of less than 35 degrees relative to the axial direction.

7. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle of less than 30 degrees relative to the axial direction.

8. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle of less than 25 degrees relative to the axial direction.

9. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle of less than 20 degrees relative to the axial direction.

10. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle of less than 15 degrees relative to the axial direction.

11. The sealing ring according to claim 3, wherein, The gradually tapering wall member (35) has an angle greater than 10 degrees relative to the axial direction.

12. The sealing ring according to claim 1, wherein, The reinforcing member (40) has a uniform cross-section over its entire extension.

13. The sealing ring according to claim 12, wherein, The reinforcing member (40) has a circular cross-section over its entire extension.

14. The sealing ring according to claim 1, wherein, The reinforcing member (40) is embedded in the tapering wall member (35).

15. The sealing ring according to claim 5, wherein, The thickness of the tapering wall member (35) is locally increased in the region surrounding the embedded reinforcing member (40).

16. The sealing ring according to any one of claims 1 to 15, wherein, The axial position of the reinforcing member (40) is located at half the distance between the proximal end (36) and the distal end (37), or at the distal end (37).

17. The sealing ring according to any one of claims 1 to 15, wherein, The outwardly extending annular protrusion (41) is configured to be clamped against the first flange (32) or the second flange (33) and secured to the first flange (32) or the second flange (33), wherein the first abutting surface (38) abuts against the surface of the first flange (32) or the second flange (33).

18. The sealing ring according to any one of claims 1 to 15, wherein, The outwardly extending annular protrusion (41) includes a recess (43) arranged opposite to the first abutting surface (38), the recess being configured to cooperate with a clamping ring (44) for clamping the annular protrusion (41) against the first flange (32) or the second flange (33).

19. The sealing ring according to any one of claims 1 to 15, wherein, The sealing ring (31) is configured to fit tightly into a notch provided in the first flange (32) or the second flange (33).

20. The sealing ring according to any one of claims 1 to 15, wherein, The distal end (37) has a second surface (39) facing in a direction opposite to that toward the proximal end (36) and defining at least a portion of the second abutment surface (39).

21. A pump support comprising a first flange (32), a second flange (33), and a sealing ring (31) according to any one of the preceding claims, the first flange (32) and the second flange (33) being configured to be interconnected, wherein the sealing ring is disposed between the first flange and the second flange, the two flanges (32, 33) including through openings aligned with the sealing ring (31) when interconnected, wherein the sealing ring surrounds the openings, wherein, The first flange (32) is configured to carry or form a portion of the pump housing, and the second flange (33) forms a portion of a fluid passage configured to receive fluid from the pump housing and deliver the fluid at a delivery location, wherein the sealing ring (31) is arranged to provide a seal between the first flange (32) and the second flange (33).

22. A method for providing a seal between the two flanges (32, 33) of a pump support according to claim 21, the method comprising: - The sealing ring (31) is arranged on one of the first flange (32) and the second flange (33). - Connect the two flanges (32, 33), wherein the through openings of the two flanges are aligned with the sealing ring (31) surrounding the through openings.

Images