Pump unit driven by an electric motor

Abstract

The invention relates to a pump unit that can be driven by an electric motor, in particular for providing vacuum for a pneumatic brake booster, including a pump housing that can be closed by a working-chamber cover and at least one elastic displacement element, wherein a working chamber is bounded between the displacement element and the working-chamber cover and wherein inlet valves and outlet valves and inlet channels and outlet channels associated with the valves are associated with the working chamber. According to the invention, in order to reduce noise emissions, devices for reducing a contact surface between the working-chamber cover and the pump housing are provided.

Claims

1. A pump unit that can be driven by electric motor, for the generation of negative pressure for a pneumatic brake force booster, comprising a pump housing that can be closed off by a working chamber cover and comprising at least one elastic displacement element, wherein a working chamber is delimited between the displacement element and the working chamber cover, and said working chamber is assigned in each case inlet and outlet valves and inlet and outlet ducts assigned to the valves, at least three protuberances extending from one of the working chamber cover and the pump housing for reducing an area of contact between the working chamber cover and the pump housing, and a decoupling element positioned between the at least three protuberances extending from the one of the working chamber cover and the pump housing and the other one of the working chamber cover and the pump housing.

2. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the at least three protuberances are distributed over the circumference of a housing flange, such that a spatially stable support is realized between the working chamber cover and the pump housing.

3. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the working chamber cover has a top cover and a bottom cover with a lower bottom cover flange, and the at least three protuberances are distributed over the circumference of the lower bottom cover flange, such that a spatially stable support is realized between the working chamber cover and the pump housing.

4. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the working chamber cover has a top cover with a top cover flange and has a bottom cover with an upper bottom cover flange, wherein the at least three protuberances are provided between the top cover and the bottom cover.

5. The pump unit that can be driven by electric motor as claimed in claim 4, wherein the at least three protuberances distributed over the circumference of the top cover flange or of the upper bottom cover flange, such that a spatially stable support is realized between the top cover and the bottom cover.

6. The pump unit that can be driven by electric motor as claimed in claim 2, wherein the working chamber cover is separated from the pump housing, and/or the top cover is separated from the bottom cover, by the decoupling element for the purpose of reducing a transmission of vibrations.

7. The pump unit that can be driven by electric motor as claimed in claim 6, wherein the elastic decoupling element is connected to at least one seal element to form a gasket.

8. The pump unit that can be driven by electric motor as claimed in claim 1, wherein at least one insert part that can be loaded in a valve opening direction by a valve plate is arranged, so as to be secured against rotation, in the inlet or the outlet duct.

9. The pump unit that can be driven by electric motor as claimed in claim 8, wherein the insert part has means for locking the insert part in corresponding locking openings, wherein the locking openings are provided in the bottom cover.

10. The pump unit that can be driven by electric motor as claimed in claim 8, wherein the insert part has at least one impact surface, which is rounded in a valve opening direction, for the abutment of the valve plate during the valve opening process.

11. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the bottom cover has a valve support surface for the support of the valve plate in a closed valve state, wherein at least one recess for reducing an area of contact between the valve plate and the valve support surface is arranged in the valve support surface.

12. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the pump unit can be fastened in elastically vibration-decoupled fashion in a base holder, wherein the elastic decoupling is realized by means of damping elements, wherein the base holder has supporting elements for receiving damping elements, and wherein at least one supporting element is manufactured by deformation of the base holder.

13. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the pump unit can be fastened in elastically vibration-decoupled fashion in a base holder, wherein the elastic decoupling is realized by damping elements, wherein at least one of the damping elements has an inner shell with a conical inner contour and an outer shell, wherein the inner shell is connected to the outer shell by an encircling collar and by radial webs arranged at least on one side of the collar.

14. The pump unit that can be driven by electric motor as claimed in claim 1, wherein an air outlet unit, which is pneumatically connected to the outlet duct, for the discharge of the air into the surroundings of the pump unit is provided, wherein the air outlet unit has an intermediate base with at least one passage opening, wherein the intermediate base comprises means closing the passage openings, in water-tight fashion in the direction of the outlet duct, in the manner of a check valve.

15. The pump unit that can be driven by electric motor as claimed in claim 14, wherein the means for closing passage openings are in the form of an elastically resilient tab that is integrally formed on the intermediate base.

16. The pump unit that can be driven by electric motor as claimed in claim 1, wherein an air outlet unit, which is pneumatically connected to the outlet duct, for the discharge of the air into the surroundings of the pump unit is provided, wherein the air outlet unit has a check valve with an elastic valve disk, and the check valve closes pneumatically in the direction of the outlet duct, wherein the valve disk is loaded counter to the valve opening direction by an elastic element.

17. The pump unit that can be driven by electric motor as claimed in claim 16, wherein a disk element is provided so as to be arranged between the elastic element and the valve disk.

18. The pump unit that can be driven by electric motor as claimed in claim 16, wherein the elastic element is in the form of a spiral spring.

19. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the pump unit is driven by an electric drive unit, wherein at least two elastic intermediate elements are interposed, so as to act in parallel, between the pump housing and the drive unit, wherein an inner intermediate element is provided for pneumatic and hydraulic sealing with respect to the surroundings of the pump unit, and an outer intermediate element is provided for a vibration decoupling of the drive unit from the pump housing, and wherein the intermediate elements are connected to one another by at least two elastic connecting webs.

20. The pump unit that can be driven by electric motor as claimed in claim 1, wherein the displacement element has an elastic diaphragm element and a connecting rod element, wherein the diaphragm element is non-detachably connected to the connecting rod element by an insert molding process, wherein the connecting rod element is of unipartite form and has a shank part and a connecting rod ring part.

Description

DESCRIPTION OF THE FIGURES

(1) Further details, features, advantages and possible uses of the invention will emerge from the subclaims together with the description and with reference to the drawings. Corresponding components and structural elements are denoted, where possible, by the same reference signs. In the drawings:

(2) FIG. 1 shows a known pump unit in a sectional illustration.

(3) FIG. 2 shows a known working chamber cover in a sectional illustration (a) and in an exploded illustration (b).

(4) FIGS. 3a and 3b show an embodiment according to the invention of a bottom cover.

(5) FIG. 4 shows a sectional detail illustration of a further embodiment according to the invention of a working chamber cover.

(6) FIG. 5 shows a further embodiment according to the invention of a working chamber cover in an exploded illustration.

(7) FIGS. 6a-6e show an embodiment according to the invention of a pump housing, and sectional detail illustrations of the assembled state.

(8) FIGS. 7a and 7b show a further embodiment according to the invention of a working chamber cover.

(9) FIG. 8 shows an embodiment according to the invention of an intermediate base for an air outlet unit.

(10) FIG. 9 shows an embodiment according to the invention of a check valve for an air outlet unit.

(11) FIG. 10 shows a pump unit mounted in a base holder.

(12) FIG. 11 shows an embodiment according to the invention of a base holder (b) in comparison with a known base holder (a).

(13) FIGS. 12a and 12b show an embodiment according to the invention of a damping element in a three-dimensional view and in a sectional view.

(14) FIG. 13 shows an exploded illustration depicting the arrangement of elastic intermediate elements according to the invention between the pump housing and the drive unit.

(15) FIGS. 14a and 14b show an embodiment according to the invention of a displacement element, and a detail illustration of a connecting rod element.

DETAILED DESCRIPTION OF THE INVENTION

(16) Because basic functional principles of generic pump units and of pneumatic brake force boosters that can be connected to such pump units are well known, a precise explanation of these will not be given below unless considered essential to the description of the invention.

(17) FIG. 1

(18) FIG. 1 shows a known pump unit 1. The pump unit is in the form of a double-diaphragm pump with two opposite displacement elements 4. The displacement elements 4 each have an elastic diaphragm element 46 which are each clamped in air-tight fashion between a pump housing 3 and a working chamber cover 2 and thereby delimit a working chamber 5. Each working chamber is assigned a respective inlet 6 and outlet valve 7 (not shown) and inlet 8 and outlet ducts 9 that are pneumatically connected to the valves. Here, the inlet duct 8 is pneumatically connected to a connection line 54 that is connected to a pneumatic brake force booster (not shown). Via said connection, air is drawn out of a negative-pressure chamber of the brake force booster into the working chamber 5.

(19) The outlet duct 9 is pneumatically connected to a housing interior 53 of the pump unit. From the housing interior 53, the air is discharged into the surroundings via an air outlet unit 34. The air outlet unit 34 is divided by an intermediate base 35 with passage openings 36, and comprises further structural elements such as a check valve 38, which is arranged between an air outlet unit base 66 and the intermediate base 36 and which prevents an ingress of air into the housing interior 53.

(20) The displacement elements 4 are moved in opposite directions by means of a crank drive 52 such that, as a result, a volume of the working chamber 5 is periodically varied and thus, in interaction with the inlet and outlet valves, a transfer of air is effected from a connected brake force booster into the surroundings of the pump unit via the working chamber 5.

(21) The crank drive 52 is set in motion by means of an electronically controllable drive unit 42.

(22) FIG. 2

(23) To illustrate the valve function, FIG. 2 shows a known working chamber cover 2 in a sectional illustration (a) and in an exploded illustration (b). The working chamber cover 2 comprises a relatively large top cover 12 and a relatively small bottom cover 13, wherein the top cover 12 has an inlet duct 8 and an outlet duct 9 integrated therein. The inlet duct 8 is assigned an inlet valve 6, and the outlet duct 9 is assigned an outlet valve 7. The two valves are each in the form of check valves with elastic valve disks 39′, 39″ which, in a closed valve position, bear sealingly against respectively associated valve support surfaces 22, 22′. A combination seal 55 ensures air-tight separation between the top cover 12 and the bottom cover 13 in the region of a top cover flange 14 and of an upper bottom cover flange 15, and also between the inlet duct 8 and the outlet duct 9.

(24) By means of a lower bottom cover flange 11, the working cover 2 presses the diaphragm element 46 shown in FIG. 1 against the pump housing 3 in a pneumatically sealed manner, and thus ensures a pneumatic delimitation of the working chamber 5. Air ducts 24, 24′ extending through the bottom cover 13 permit a connection of inlet 8 and outlet ducts 9 to the working chamber 5.

(25) FIG. 3

(26) For the support of a valve disk during the opening process of a generic valve as per FIG. 2, an impact surface is generally required. In the known embodiment as per FIG. 2, this is realized, in the case of the inlet valve, by means of an impact element 56 which is connected to the top cover 12 and which clamps the valve disk 39″. In an embodiment according to the invention of a bottom cover 13 as shown in FIG. 3, said function is realized by means of a separate insert part 20. The insert part 20 has two locking lugs 57 which are plugged into the locking openings 21 provided for the purpose in the bottom cover 13 and are thus locked so as to be secured against rotation. It is thus possible for both the bottom cover and also the top cover to be designed such that they can be produced considerably more easily, for valve disks to be replaced by simple valve plates 19 connected to the combination seal 55, and for the impact surface 58 to be configured such that sound generation during the impacting of the valve disk or valve plate can be reduced.

(27) FIG. 4

(28) FIG. 4 shows a further embodiment according to the invention, in which an insert part 20′ assigned to the outlet valve 7 is inserted into a recess 59, provided for the purpose, in the top cover 12 and provides, for the valve plate 19 connected to the combination seal 55, a rounded impact surface 58′ for abutment during the opening of the valve. The impact surface 58′ is abutted against by the valve plate 19 when the outlet valve opens and a flow takes place from the working chamber 5 into the outlet duct 9. It is preferable for the impact surface 58′ to be rounded with a radius R=10 mm, though it is also possible for other adequately large values to be selected in order that, firstly, particularly quiet impacting of the valve plate 19 is made possible and, secondly, the tendency for flow separation from a sharp body edge is reduced in an effective manner. It is furthermore possible, within the scope of the invention, for the insert part 20′ to be provided with further means for locking in the top cover 12, for example similar to those in FIG. 3.

(29) In the closed valve state, the valve plate 19 bears against the valve support surface 22. Said valve support surface 22 has an encircling recess 23. In this way, the area of contact between the valve support surface 22 and the valve plate 19 is reduced, and a tendency of the elastic material of the valve plate 19 to adhere or stick to the valve support surface 22 is thereby reduced in an effective manner. Furthermore, the air flowing out of the working chamber 5 through the air ducts 24 is split up in the recess 23 and acts on the valve plate 19 more uniformly and over a greater effective area. During the closing process, the impact noise of the valve plate 19 against the valve support surface 22 is likewise reduced owing to back-ventilation and a reduction in the area of contact. In this way, the valve operates altogether more smoothly and more quietly. It is self-evident that, within the scope of the invention, the recess 23 may also assume shapes other than the encircling trapezoidal profile that is shown.

(30) FIG. 5

(31) FIG. 5 shows another embodiment of a working chamber cover 2 according to the invention in an exploded illustration.

(32) By contrast to the embodiments described in the introduction, the top cover 12 is of elongate shape and, in terms of form, is substantially reduced to a tunnel-like encasement of the inlet duct 8 and of the outlet duct 9 and has an impact surface 58′, of integrated form, for the outlet valve 7 and a valve support surface 22′ for the inlet valve 6. By contrast to the embodiments described in the introduction, the length of the outer contour 25 of the top cover 12 is in this case considerably shorter than the length of the outer contour (26) of the bottom cover 13. It is thus possible for the working cover 2 to be made altogether considerably simpler and more lightweight and for the air ducts to be optimized in terms of flow. In the embodiment shown, the combination seal 55 is of very simple and space-saving form and has the valve plates 19 and 19′ integrated therein.

(33) The bottom cover 13 receives the combination seal and is equipped with positioning studs 60 which serve primarily for the positioning of the top cover 12 on the bottom cover 13 and which may additionally be provided for absorbing longitudinal and transverse forces between said two cover parts by virtue of said positioning studs engaging into the corresponding stud guides 61 integrally formed on the top cover 12. It is likewise possible for the positioning studs 60 to be used, by virtue of their being deformed after the mounting of the top cover 12, for permanently fixing the top cover 12 to the bottom cover 13. For sealing of the studs, the combination seal 55 has integrated O-rings 62 which engage around the positioning studs 60 in the assembled state. The O-rings 62 can sometimes stiffen the combination seal 55 overall and stabilize it against deformations and thus contribute, overall, to a reliable and simple assembly operation.

(34) FIG. 6

(35) FIG. 6 shows details of an embodiment of the pump unit according to the invention. The view 6a illustrates a three-dimensional oblique view of a housing flange 10 of the pump housing 3. The surface of the housing flange 10 has three molded protuberances 16 that are distributed over the circumference so as to be substantially uniformly spaced from one another. The molded protuberances 16 prevent the working chamber cover 2 (not shown) from bearing against the pump housing 3 over a large area. An area of contact between the pump housing 3 and the working chamber cover 2 (not shown) is reduced and, in the assembled state, is thus restricted to the three punctiform contact regions of the molded protuberances 16, which are small in relation to the area of the housing flange 10. Without the inserted diaphragm element 46 (see FIG. 1, FIG. 6e), a defined air gap would remain at all other points between the working chamber cover 2 and the pump housing 3. Three-point support thus exists between the working chamber cover 2 and the pump housing 3.

(36) During operation of the pump unit 1, noises or sound waves are generated both in the working chamber cover 2 and also in the pump housing 3, said noises or sound waves then being radiated through all of the existing surfaces. Noises at and in the working chamber cover 2 are generated primarily owing to air turbulence at the valves 6, 7 and in the air ducts 8, 9, and are normally of a higher frequency than noises at and in the pump housing 3, which originate primarily from the drive unit 42 and from the mechanical crank drive 52. At all of the areas of contact between the working chamber cover 2 and the pump housing 3, the sound waves are transmitted and repeatedly superposed on one another, which can give rise, for example, to undesired resonance.

(37) Owing to the high contact pressure in the areas of contact between the molded protuberances 16 and the working chamber cover 2 and the elimination of further sound-transmitting areas of contact, sound transmission effects between the working chamber cover 2 and the pump housing 3 are reduced, and resonance is prevented. Sound emissions both from the working chamber cover 2 and also from the pump housing 3 are likewise reduced considerably. To further intensify this expedient effect, a thin elastic decoupling element 17 is provided which is arranged between the working chamber cover 2 and the pump housing 3 and which both reduces a direct transmission of sound from one to the other counterpart at the 3 above-mentioned areas of contact and also permits extensive sound decoupling. In the exemplary embodiment shown, the decoupling element 17 is in the form of an elastomer foil and is connected to two seal elements 18 so as to form a single gasket. The two seal elements 18 serve for the sealing of the inlet duct and of the outlet duct at their parting point between the working chamber cover 2 and the pump housing 3.

(38) In a further embodiment according to the invention, it is however also possible to dispense with a decoupling element of said type.

(39) It is known that, in a three-dimensional space, three-point support constitutes a spatially stable and mathematically determinate mounting configuration of a body, because a center of mass of the body is situated within a virtual triangle, the ends of which are the support points. Because, in a three-dimensional space, it is furthermore the case that more than three vectors are always linearly dependent, it would, in the presence of more than three support points, be more cumbersome from a production aspect to ensure simultaneous and uniform contact at all of the support points. Within the scope of the invention, it is nevertheless also possible to provide more than three molded protuberances in order, for example, to limit material loads as a result of high contact pressure in the contact regions, and nevertheless reduce sound transmission and sound emission effects.

(40) The pump housing 3 shown in FIG. 6a is shown in FIG. 6b in a plan view, and in FIG. 6c in a section A-A through the pump housing 3. FIG. 6d shows the view X and FIG. 6e shows the section B-B from FIG. 6b, but in the case of an assembled pump unit 1.

(41) FIG. 6b illustrates that the molded protuberances 16 are arranged, so as to be substantially uniformly spaced from one another, on an outer edge of the housing flange 10 and provide an area of contact, which is very small in relation to the total area of the housing flange 10, for the support of the working chamber cover. From the view c, it can be seen that the molded protuberances 16 project only slightly beyond the surface of the housing flange 10.

(42) FIG. 6d shows a detail of a side view of an assembled pump unit 1. The decoupling element 17 is arranged between the working chamber cover 2 and the pump housing 3, said decoupling element being compressed in the region of the molded protuberance 16. From FIG. 6e in particular, it can be seen that the working chamber cover 2 is supported by way of the lower bottom cover flange 11 on the pump housing 3 and that the sealing of the working chamber 5 with respect to the surroundings of the pump unit is performed primarily by the elastic diaphragm element 46, which, at its edge which is thickened and stiffened in bead-like form, is sealingly compressed and clamped between the bottom cover 13 and the pump housing 3. The decoupling element 17 serves primarily for sound decoupling at an area of contact between the bottom cover 13 and the molded protuberance 16. The housing flange 10 runs below the above-mentioned area of contact, with a spacing to the bottom cover 13.

(43) FIG. 7

(44) FIG. 7 shows a further exemplary embodiment according to the invention of a top 12 and bottom cover 13 of a working chamber cover 2. In the case of a known embodiment, the top cover 12 and the bottom cover 13 are in contact over the entire circumference of the top cover flange 14 or of the upper bottom cover flange 15. In the embodiment illustrated, it is the case, by contrast, that the top cover has three molded protuberances 16 arranged in substantially uniformly distributed fashion on the top cover flange 14, which molded protuberances, in accordance with the principle already described above, permit three-point support between the top cover 12 and the bottom cover 13 and thus generate intensive acoustic decoupling. Within the scope of the invention, it is also possible for more than three molded protuberances 16 to be distributed on the top cover flange 14 or to be additionally or exclusively provided on the upper bottom cover flange 15 in order, for example, to optimize force profiles in the assembled state or the production of individual components. It is likewise conceivable for the molded protuberances to be provided exclusively on the lower bottom cover flange 11, or provided on the latter in addition to the molded protuberances 16 on the housing flange 14 (FIG. 6).

(45) FIG. 8

(46) FIG. 8 shows an embodiment according to the invention of an intermediate base 35 shown in FIG. 1. The intermediate base 35 is manufactured from a flexible material and has a likewise flexible tab 37 integrally formed on the intermediate base 35. The tab 37 is designed such that, in its relaxed normal state, it bears areally against the surface of the intermediate base 35 and covers, or closes off, the passage openings 36 in the direction of the housing interior 53 and thus in the direction of the outlet duct 9. In the event of an air shock caused by a movement of the displacement element 5, a pressure difference is built up on the two sides of the intermediate base 35, said pressure difference forcing the tab 37 to lift from the surface of the intermediate base 35 and thus open up the passage openings 36. At the same time, the tab 37 is elastically preloaded.

(47) After a certain amount of air has escaped through the passage openings 36, the pressure difference decreases, and the tab 36 springs back elastically, thus closing the passage openings 36 and preventing the ingress of air, dirt and moisture into the housing interior 53. The sound emissions from the housing interior 53 are also reduced as a result of the closure of the passage openings 36. In the event of an ingress of relatively large amounts of water into the air outlet unit 34, the water surge that has ingressed causes the tab 37 to be pressed with even greater intensity against the passage openings 36, with said tab thus preventing a further advancement of moisture in an effective manner.

(48) Further structural designs of the tab are also conceivable within the scope of the invention:

(49) In the embodiment shown, the tab 37 is in the form of a single, foldable integrally molded portion on the intermediate base, though it is likewise possible for more than one tab to be provided which is assigned to the individual passage openings 36 or groups of passage openings 36.

(50) It is likewise possible, for example, for the tabs 37 to be provided not so as to be integrally formed on the intermediate base 35 but so as to be rotatably mounted thereon and pressed against the surface of the intermediate base by means of an elastic element.

(51) FIG. 9

(52) FIG. 9 shows an embodiment according to the invention of a check valve 38 which is arranged between the intermediate base 35 and the air outlet unit base 66 and which ensures that the air discharged from the working chamber 5 can pass out of the housing interior 53 through the air outlet unit 34 into the surroundings of the pump unit 1, but not back in again. The intermediate base 35 has an integrally molded sleeve 63 which engages around a conical pin 64 that is arranged on the air outlet unit base 66 centrally within the valve seat 65, with said sleeve simultaneously pressing the elastic valve disk 39 against the valve seat 65. The valve disk 39 is additionally subjected to load by an elastic element 40 in the form of a spiral spring that is supported against the intermediate base 35. To ensure a uniform distribution of the pressure force over the entire circumference of the valve disk 39 and thus reliable closure of the check valve 38, a rigid disk element 41 is interposed between the elastic element 40 and the valve disk 39.

(53) An undesired opening of the check valve 37, for example owing to chattering of the valve disk 39 or unpredictable pressure difference fluctuations owing to interactions with the tab 37 described above, is thus counteracted.

(54) The described additional elastic support of the valve disk 39 between the valve seat 65 and the intermediate base 35 furthermore considerably improves the protection afforded by the check valve against an ingress of water into the housing interior 53 from the surroundings of the pump unit 1.

(55) FIG. 10

(56) FIG. 10 shows the pump unit 1 mounted or suspended in a base holder 28. The base holder 28 serves for the fastening of the pump unit 1 fixedly to a vehicle body. For vibration decoupling, elastic damping elements 27 are interposed between the pump unit 1 and the base holder 28. The pump unit 1 thus exhibits restricted freedom of movement in and around all spatial directions.

(57) FIG. 11

(58) FIG. 11 shows a known embodiment (view a) and an embodiment according to the invention (view b) of the base holder 28 in a three-dimensional illustration.

(59) To receive damping elements 27, the base holder 28 has supporting elements 29, 29′. The supporting elements 29′ of the known embodiment are formed as separate components which, in a separate joining process, are inserted into the openings provided for them in the base holder. By contrast, the embodiment according to the invention as per FIG. 1lb has support elements 29 which are integrated in the base holder 28 and which are generated by deformation of the base holder blank, for example by deep drawing or pressing processes.

(60) If required, support elements 29 formed in this way may for example be provided with a rolled or cut internal thread, for example in order to serve as a fixing point for plug connectors, cable holders or other peripheral elements or units.

(61) Further exemplary embodiments of integrated support elements generated by deformation processes—for example by means of punching and bending, or upsetting—are likewise conceivable within the scope of the invention.

(62) FIG. 12

(63) FIG. 12 illustrates a damping element 27 composed of elastic material, preferably EPDM or a silicone material, in a three-dimensional view (view a, obliquely from above and obliquely from below) and a sectional illustration (view b). Said damping element has an outer shell 31 and an inner shell 30, wherein the inner shell has a rotationally symmetrical inner contour which is of tubular conical form and which corresponds with above-described supporting elements 29, 29′ of the base holder or with a further fastening element. On the outer shell 31 there is formed an encircling groove 67 which is suitable for the fixing of the damping element 27 in a bore in a suitable holding element.

(64) The inner shell 30 is connected to the outer shell 31 via an encircling collar 32 that is arranged obliquely with respect to the axis of rotation R. Furthermore, the inner shell 30 is connected to the outer shell 31 via multiple webs 33 which are arranged on one side of the collar and which run radially from the inner shell 30 to the outer shell 31. Assisted by the conically running inner contour of the inner shell 30 together with the collar 32 and the webs 33, the damping element 27, under load, deforms both transversely and along or obliquely with respect to the axis of rotation R and generates a resistance force counter to the load, which resistance force is dependent on the degree of deformation and is initially weak (soft), increases progressively (hard) with increasing deformation, and is particularly high after a collapse of the free intermediate spaces between the inner shell 30 and the outer shell 31. In this way, small vibrations of the pump unit are intercepted in an effective manner by the “soft” part of the spring characteristic curve and are not transmitted to the body, and a relatively large movement of the pump unit is damped by the hard part of the spring characteristic curve, with effective decoupling thus being realized over a broad range.

(65) FIG. 13

(66) The connecting point between the drive unit 42 and the pump housing 3 must be of both sealed and also vibration-decoupled design. In the embodiment according to the invention shown in FIG. 13, two elastic intermediate elements 43, 44 which are of substantially annular form and are arranged concentrically with respect to one another are provided between the pump housing 3 and the drive unit 42. The inner intermediate element 43 has a circular cross section and serves primarily for the sealing of the interface. The inner intermediate element 43 is connected to the outer intermediate element 44 via four connecting webs 45. Within the scope of the invention, some other number of connecting webs 45 is also possible. A further embodiment without connecting webs 45 is likewise conceivable.

(67) The cross section of the outer intermediate element 44 and of the connecting webs 45 is preferably cuboidal, and in this case configured such that the outer intermediate element 44 and optionally also the connecting webs 45 are compressed between the pump housing 3 and the drive unit 42 when the pump unit 1 is in an assembled state. Here, a defined air gap remains between the pump housing 3 and the drive unit 42 at least in the region around the outer intermediate element 44. In this way, a transmission of vibrations between the drive unit 42 and the pump housing 3 is reduced by way of a conversion of the kinetic energy into heat, without the seal function being impaired.

(68) FIG. 14

(69) FIG. 14 shows an embodiment according to the invention of a displacement element 4. The displacement element 4 comprises an elastic diaphragm element 46 and a connecting rod element 47. The diaphragm element 46 is molded onto the connecting rod element 47 by insert molding, and is thus irreversibly connected thereto. To make it possible to realize a durable connection, the diaphragm element 46 has a material reinforcement in the region of the insert-molded portion, and the connecting rod element 47 has, in the insert-molded region, a shank head 50 with an aperture 51 in order to form an effective anchor and counteract a detachment of the diaphragm element 46 from the connecting rod element 47 during pump operation. Owing to the aperture 51, which after the insert molding process is filled with the material of the diaphragm element 46, it is not possible for the two parts to be separated from one another without being destroyed. Further designs of the aperture 51, and the provision of multiple apertures in the shank head 50, are also conceivable within the scope of the invention.

(70) The connecting rod element 47 is of unipartite form and is composed substantially of a shank part 48 and of a connecting rod ring part 49 integrally formed on the shank part 48. The connecting rod element may preferably be produced from a plastics material in an injection molding process, although other production methods, for example punching or sintering, and metal materials are likewise possible.

REFERENCE SIGNS

(71) 1 Pump unit 2 Working chamber cover 3 Pump housing 4 Displacement element 5 Working chamber 6 Inlet valve 7 Outlet valve 8 Inlet duct 9 Outlet duct 10 Housing flange 11 Lower bottom cover flange 12 Top cover 13 Bottom cover 14 Top cover flange 15 Upper bottom cover flange 16 Molded protuberance 17 Decoupling element 18 Seal element 19, 19′ Valve plate 20 Insert part 21 Locking opening 22, 22′ Valve support surface 23 Recess 24 Air duct 25 Outer contour 26 Outer contour 27 Damping element 28 Base holder 29, 29′ Supporting element 30 Inner shell 31 Outer shell 32 Collar 33 Web 34 Air outlet unit 35 Intermediate base 36 Passage opening 37 Tab 38 Check valve 39 Valve plate 40 Elastic element 41 Disk element 42 Drive unit 43 Inner intermediate element 44 Outer intermediate element 45 Connecting web 46 Diaphragm element 47 Connecting rod element 48 Shank part 49 Connecting rod ring part 50 Shank head 51 Aperture 52 Crank drive 53 Housing interior 54 Connection line 55 Combination seal 56 Impact element 57 Locking lug 58 Impact surface 60 Positioning stud 61 Stud guide 62 O-ring 63 Sleeve 64 Pin 65 Check valve seat 66 Air outlet unit base 67 Groove R Axis of rotation