DE29708581U1 - Pump element for a lubricant pump - Google Patents

Description

Pump element for a lubricant pump

The invention relates to a pump element of the type specified in the preamble of claim 1.

A pump element is known from a publication entitled "Oil Lubrication Pump Type T" by Joseph Vögeie AG, DSK 1-900-00(09.92), p. 3, which is installed together with several similar pump elements in an oil lubrication pump for lubricating the cylinders of medium and large diesel engines and compressors. The pump has a box-like housing filled with lubricating oil with a stationary gear shaft in which the pump elements are attached to a base plate with cylinder axes parallel to the gear shaft and distributed in the circumferential direction. A working lifting disk is provided on the gear shaft, which moves the lifting piston of each pump element back and forth as it rotates. An inlet channel opens into an axial area of the cylinder. Pressure outlets leading off to the sides are provided, offset axially to the inlet channel. The flow rate adjustment device has an adjustment screw with which a jaw-shaped driver on the lifting piston is coupled to the working lifting disc. By adjusting the adjustment screw, the working stroke or the reversal point of the lifting piston in the transition from the stroke to the suction stroke is adjusted. The structure of the pump element and the flow rate adjustment device is complex. The design of the pump element and the drive mechanism limit the permissible number of cycles and thus the performance of the lubricating oil pump inappropriately.

The invention is based on the object of creating a pump element of this type which is structurally simple and significantly more efficient than the known pump element.

The stated object is achieved according to the invention with the features of claim 1.

In the pump element, when the delivery rate is adjusted, the working stroke of the piston is left unchanged and, in contrast to the known adjustment method, an inlet channel is selected that determines the delivery rate based on the axial position of its mouth in the cylinder. Only the selected inlet channel is connected to the supply. Any other inlet channel remains inoperative. The piston passes over the mouth of the inlet channel during the pressure stroke sooner or later, depending on the axial position of the mouth of the selected inlet channel connected to the supply. The piston always works with the same working stroke, can be fitted tightly and driven at a relatively high cycle rate! because the delivery rate adjustment device is structurally separate from the drive mechanism of the piston and a low-wear, high-performance drive mechanism (e.g. eccentric shaft) can be used. This results in a significantly higher performance of the pump equipped with the pump element.

It is obvious that the sleeve body cannot have just one inlet channel in each of the different axial areas, but possibly more than one inlet channel, whereby these inlet channels selected for a specific delivery rate, whose mouths are located in the same axial area of the cylinder, are then connected together to the supply.

According to claim 2, the adjustment of the delivery rate is very simple and possible by means of a relative rotation between the sleeve body and the housing.

According to claim 3, the pump element is fixed in its operating position by means of the housing and the sleeve body is rotated in the housing to adjust the delivery rate.

According to claim 4, convenient handling of the flow rate adjustment with high operational reliability is achieved by the rotary positioning device.

Each delivery quantity is assigned a specific relative rotational position between the sleeve body and the housing, expediently the sleeve body in the housing, which is held by means of the rotary positioning device and can be set in a precisely reproducible manner.

According to claim 5, radial bores in the wall of the sleeve body are structurally simple for the inlet channels.

Alternatively, according to claim 6, at least some inlet channels are bores that are inclined to the cylinder axis, the openings of which on the outside of the sleeve body can be aligned with one another in the circumferential direction, while their inner openings in the cylinder are offset from one another in the axial direction.

According to claim 7, the passage of the housing aligned with an inlet channel establishes the connection to the supply, while the outer and inner sides of the sleeve body and the housing, which lie against one another with a relatively tight sliding fit, separate the other inlet channels that are not currently selected from the supply.

According to claim 8, the open pockets in the outside of the sleeve body bridge the axial offsets of the inlet channels in relation to the passage leading to the supply in the housing.

According to claim 9, the passage itself or a pocket formed at the passage in the inside of the housing bridges the axial offsets between the inlet channels, so that only the selected inlet channel is reliably connected to the supply, while the other, non-selected inlet channels are separated from the supply.

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According to claim 10, a sensitive adjustment of the delivery quantity is achieved, since the openings in the cylinder overlap in the circumferential direction and are therefore only slightly axially offset relative to one another.

According to claim 11, the pump element is simple and compact in terms of manufacturing and assembly, since the check valve is integrated into the pump element.

According to claim 12, the adjustment of the delivery quantity can be carried out conveniently, since the rotary handle is easily accessible at the protruding end section.

According to claim 13, the clamping nut can also be used to position the sleeve body in the selected rotational position.

According to claim 14, the rotary positioning means are provided in a structurally simple manner between the housing and the end section of the sleeve body, whereby only a few individual parts are required.

According to claim 15, a structurally simple and functionally reliable rotary positioning device is created with which the rotary positions assigned to the conveying quantities can be precisely set and maintained.

According to claim 16, the piston always remains coupled to the drive mechanism via the return spring even at higher cycle rates (reduced wear and low running noise) and the reaction force from the compression stroke of the piston on the sleeve body is safely transferred to the housing. A low-wear drive for the piston can be used even at high cycle rates (good performance characteristics), e.g. a direct-drive energy source.

According to claim 17, the pump element is expediently integrated together with several similar pump elements into a cylinder oil lubrication pump for

Medium or large diesel engines or compressors. Inserting the pump element into the outwardly open receptacle is easy to assemble and enables the flow rate to be easily adjusted with only negligible assembly effort. Complex piping in the pump module housing is not required, as the channels in the pump module housing are conveniently designed as bores on the inside. The increased performance and convenient handling when adjusting the flow rate result in an oil lubrication pump that easily meets the high lubrication requirements of modern medium or large diesel engines or compressors. Despite its high performance, the oil lubrication pump is compact, wear-resistant, easy to assemble and cost-effective. Several such pump module housings can be placed in series in the pump and functionally coupled to one another in order to supply a large number of lubrication levels or lubrication points or cylinders.

An embodiment of the subject matter of the invention is explained using the drawing. They show:

Fig. 1 shows a longitudinal section of a pump element for a lubricant pump,

Fig. 2 a view of the pump element in Fig. 1 from the right,

Fig. 3 A - F show longitudinal sections of a part of the pump element supplementing the sectional view of Fig. 1 in cutting planes offset around the longitudinal axis of the pump element, which are indicated in Fig. 2 with a 60° offset in each case, and

Fig. 4 shows a partial longitudinal section of a cylinder lubricating oil pump with integrated pump elements according to Figs. 1 to 3.

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A pump element E, preferably for lubricating oil, according to Fig. 1 and 2 consists essentially of an outer housing G, a sleeve body H arranged in the housing G and a piston K that can be moved in a cylinder Z in the sleeve body H. The pump element has a delivery rate adjustment device V and is intended for installation, for example, in a cylinder lubricating oil pump P according to Fig. 4.

The lifting piston K, which is guided in the cylinder Z of the sleeve body H, is acted upon in the suction direction by a return spring 1, which is arranged between the sleeve body H and a sliding tappet 2 of the lifting piston K. With the sliding tappet 2, the lifting piston K rests against a drive element, for example an eccentric shaft 33, 34 according to Fig. 4, which sets it in a back and forth movement.

In the sleeve body H, the cylinder Z continues with an enlarged end bore 3, in which a check valve R is arranged, which opens in the flow direction to a pressure outlet D of the sleeve body H. The check valve R is fixed in the sleeve body H by means of a screw insert 4, which is screwed into an internal thread section 5 in front of a screw plug 6. Sealing rings 7, 8, 9, 10 are provided on the housing G and on the sleeve body H or on the check valve R. The pressure outlet D (several radial bores distributed in the circumferential direction) opens into a circumferential groove 11, which is connected to at least one outlet 12 in the housing G. A line (not shown) leads from the outlet 12 to a lubrication connection. At least one passage F is provided in the housing G, which is limited in the circumferential direction, but can extend over a larger distance in the axial direction like an elongated hole.

The piston K has a front pressure surface 13 and slides with its circumferential surface 14 in the cylinder Z. The housing G supports the sleeve body H, e.g. with a relatively tight sliding fit, rotatable about the axis X of the cylinder Z, with the outside 22 of the sleeve body H on the inside of a sleeve

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part 15 of the housing G. Furthermore, a fastening flange 16 is formed on the base body G, in which fastening holes 17 are provided and which defines a frontal contact surface 18. In the fastening flange 16 there is at least one threaded hole 19 for a fixing element 20, for example designed as a head screw. The sleeve body H can be supported by a peripheral shoulder 21 on the housing G in the compression stroke direction of the reciprocating piston K. At an axial distance in front of the check valve R, several inlet channels B open into the cylinder Z ₁ , for example and, according to Fig. 3, six radial holes offset from one another by 60° each, which form inlet channels B1 to B6, one of which is indicated by B in Fig. 1. One inlet channel B1 to B6 can be optionally aligned with the passage F in the housing G connected to the lubricant supply. The openings of the inlet channels B, B1 to B6, located in cylinder Z (Fig. 1, 3) are offset from one another in the direction of the cylinder axis X.

The sleeve body H projects beyond the housing G with an end section 24. The end section 24 has an external thread 26 and a longitudinal groove 25. A clamping nut 27 is screwed onto the external thread 26. A disk body 28 with a nose engages in the longitudinal groove 25, which has peripheral positioning notches 29 (Fig. 1 and 2) which are arranged and shaped in such a way that the fixing element 20 (either with the shaft or the head) can engage in one of the positioning notches 29. The disk body 28 is clamped against the stop surface 18 by means of the clamping nut 27, while the clamping nut 27 simultaneously pulls the sleeve body H with the shoulder 21 against the housing G.

In the view of Fig. 2 it can be seen that the disk body 28 has the positioning notches 29 with 60° divisions, for example approximately semicircular cutouts, with each positioning notch 29 being assigned a Roman numeral (I to VI) as a marking. The positioning notches 29 of the disk body 28, which is connected to the end section 24 in a rotationally fixed manner via the longitudinal groove 25, are assigned to the various inlet channels B1 to B6 in such a way that only

one of the inlet channels B1 to B6 is connected to the passage F of the housing G when the fixing element 20 engages in a positioning notch 29. Finally, Fig. 2 indicates that an exposed rotary handle 25 ¹ (two diametrically opposed flats which define a certain wrench size) is formed on the end section 24 in order to rotate the sleeve body H relative to the housing G after loosening the clamping nut 27 and the fixing element 20.

In Fig. 3A to 3F, each inlet channel B (B1 to B6) is a radial bore in the wall of the sleeve body H. The axial distances Y1, Y2, etc. between the left front end Y of the sleeve body H and the mouths of the inlet channels B1 to B6 differ from one another, but expediently only slightly, so that the contours of the mouths of the inlet channels B1 to B6 can overlap one another in the circumferential direction. In the outside of the sleeve body, for each inlet channel B1 to B6, an axially extending pocket T1 is provided which is circumferentially limited approximately to the width of the inlet channel B1 to B6 and which is open to the outside, the end of which facing away from the respective inlet channel B1 to B6 is at a distance Y ¹ from the left front end Y of the sleeve body H, which is the same for all pockets T1 to T6.

In Fig. 4, two pump elements E are inserted into a pump module housing C in outwardly open receptacles 30, such that the flanges 16 of the housings G are located on an outside of the pump module housing C and the flow rate adjustment devices V are freely accessible. The receptacles 30 lead to a chamber in which an eccentric shaft 33, 34 is rotatably mounted in bearings 35. The pump elements E are approximately radial to the eccentric shaft 33, 34, which leads to a gear MG of a drive motor M flanged to the pump module housing C. Other similar pump module housings C can be connected in series to the pump module housing C shown in Fig. 4, the eccentric shafts (not shown) of which are connected by couplings 36 with retaining rings.

37 are connected to the common drive M, MG in a torque-transmitting manner.

In the pump module housing C, two pump elements E are inserted in Fig. 4. It is conceivable to use only one pump element E, or to insert further pump elements into corresponding receptacles 30 from the other outer sides of the pump module housing C (not shown in Fig. 4), so that, for example, with a pump module housing C with four pump elements E, two cylinders can be supplied with lubricating oil, each in an upper and lower lubrication level and in the outlet valve area. The lubricating oil delivered by each pump element E is expediently distributed to several lubrication points in the respective lubrication area via a progressive distributor. Internal channels are provided in the form of bores 31, 32 in the pump module housing C, so that the pump module housing C takes on the function of a distributor block. One channel can be connected to the supply (not shown), while another channel can be an oil drain channel or a supply channel for running-in oil that is separate from the normal oil supply or can be optionally separated.

Function:

On the eccentric shaft 33, 34 as a drive element for the pump element, the sliding tappet 2 rests on an eccentric shaft section 34 under the force of the return spring 1. In Fig. 1, for example, the piston K is at the turning point from the suction stroke to the pressure stroke. Its unchangeable working stroke is indicated by h. During the pressure stroke, the piston K in Fig. 1 is moved to the right, whereby it first pushes out the lubricant located in front of its front face 13 in the cylinder Z through the selected inlet channel B (131 - B6) and the passage F, until finally the front face 13 passes over the mouth of the inlet channel B (B1 - B6) in the cylinder Z, blocks the mouth and forces the remaining lubricant! through the pressure outlet D and the circumferential groove 11 to the pressure outlet 12 in the housing G by opening the check valve R.

changed. Before the check valve R, the piston K reaches its reversal point between the pressure stroke and the suction stroke. Under the force of the return spring 1, the piston is moved to the left in Fig. 1, whereby the check valve R closes and the piston K builds up negative pressure until its front surface 13 passes over the inlet channel B aligned with the passage F and again sucks lubricant into the cylinder Z until the piston reaches its left reversal point. The new pressure stroke then runs in the manner mentioned above. The other inlet channels not selected are not functional.

Adjusting the flow rate:

The clamping nut 27 is loosened. The fixing element 20 is released. For example, the handle 25 is gripped using a wrench and the sleeve body H is rotated relative to the housing G into one of the five additional rotational positions, each of which corresponds to a specific delivery rate. In the newly selected rotational position, the fixing element 20 is inserted into the positioning notch 29 before the clamping nut 27 is subsequently tightened again. The pump element E is then ready for operation again.

In Fig. 3A to 3F, the inlet channels B1 to B6 are radial bores in the wall of the sleeve body H. It would be possible, for example, to design only the inlet channel B4 as a radial bore, while the other inlet channels B1, B2, B3 and B5 and B6 are designed as oblique bores with respect to the axis X of the cylinder Z, the openings of which on the outside of the sleeve body H are aligned with one another in the circumferential direction, while their openings on the inside and in the cylinder Z are axially offset from one another, analogous to the offset of the openings in Fig. 3A to 3F. With this design, the pockets T1 to T6 could be omitted and the passage F could be a simple bore. In a further alternative, the radial bores shown in Fig. 3A to 3F, which form the inlet channels B1 to B6, could each pass through to the outside of the sleeve body H. At the passage F in the

Housing G could be formed as a single axially extending pocket (indicated by dashed lines) which is open to the inside and bridges the axial offsets between the individual inlet channels B1 to B6. In the embodiments shown, a single inlet channel 131 to B6 is assigned to a specific delivery rate. However, it is conceivable to form the inlet channels B1 to B6 from associated pairs or inlet channel groups in order to suck the lubricant into the cylinder Z from several sides at the same time. Of course, in this case two or more passages F or a passage F with a correspondingly wide circumference would have to be provided in the base body G, in such a way that only the selected group of inlet channels is connected to the supply, while the non-selected groups of the other inlet channels remain separated from the supply.

The disk body 28 with its positioning notches 29 allows a step-by-step adjustment of the delivery rate. However, it could be considered sufficient not to fix the adjustment by means of a positive connection between the fixing element 20 and the positioning notches 29, but to allow a stepless adjustment, in which the selected rotational position of the sleeve body is only fixed by the clamping nut 27 and controlled by markings on the housing G and the sleeve body H that can be aligned with one another. Alternatively, a ball rotary lock could also be provided, which indicates that the selected position has been reached by audibly and tactilely locking, whereby the clamping nut 27 could be used to fix the selected position if necessary. In a further alternative, the sleeve body H could be mounted in the holder in a rotationally fixed manner, while the housing G can be rotated relative to the sleeve body H in order to adjust the delivery rate.

Claims (17)

Patent claims 1. Pump element (E) for a lubricant pump (P), in particular a cylinder oil lubrication pump for medium and large diesel engines, with a sleeve body (H) delimiting a cylinder (Z) for a reciprocating piston (K) that can be driven by a drive element (34), with an inlet channel (B1 to B6) opening laterally into the cylinder (Z) and over which the reciprocating piston (K) can travel, which is connected to a lubricant supply in a housing (G) arranged on the sleeve body (H), with a pressure outlet (D) assigned to a pressure side of the piston (K) and with a delivery quantity adjustment device (V) ₁ , characterized in that the delivery quantity adjustment device (V) in the sleeve body (H) within the unchangeable working stroke (h) of the reciprocating piston (K) has several inlet channels that open into different axial positions in the cylinder (Z) and can each be optionally connected to the lubricant supply. (B, B1 to B6). 2. Pump element according to claim 1, characterized in that the sleeve body (H) and the housing (G) are rotatable relative to one another about the cylinder axis (X), preferably continuously or in steps with predetermined holding positions (I to VI). 3. Pump element according to claims 1 and 2, characterized in that the sleeve body (H) is mounted in the housing (G) so as to be rotatable and immovable in the axial direction, and that the pump element (E) can be fixed in its operating position by means of the housing (G). 4. Pump element according to claim 1, characterized in that the delivery quantity adjustment device (V) has a positive and/or non-positive rotary positioning device (20, 28, 29) between the sleeve body (H) and the housing (G). 5. Pump element according to claim 1, characterized in that each inlet channel (B, B1 to B6) is an approximately radial bore in the wall of the sleeve body (H). 6. Pump element according to claim 1, characterized in that at least some inlet channels are bores in the wall of the sleeve body (H) which are inclined to the cylinder axis (X) in such a way that the mouths of the inlet channels located on the outside of the sleeve body (H) are aligned approximately in the circumferential direction and arranged in the same axial region of the sleeve body, while the mouths located in the cylinder (Z) are axially offset from one another. 7. Pump element according to claims 5 or 6, characterized in that at least one passage (F) limited in the circumferential direction, connected to the supply, is provided in the housing (G), which can be aligned with a selected inlet channel (B1 to B6, B). 8. Pump element according to at least one of claims 5 and 6, characterized in that at least in some inlet channels (B1, B6) in the outside of the sleeve body (H) there are provided pockets (T1 to T6) which are limited in the circumferential direction, run approximately axially and are open to the outside and extend axially to the same axial region of the sleeve body to which the passage (F) of the housing (G) is aligned. 9. Pump element according to at least one of claims 5 to 7, characterized in that the passage (F) has an axial length or leads into a pocket formed in the inside of the housing (G) with an axial length which bridges the axial offsets between the edging channels (B 1 to B6). 10. Pump element according to at least one of claims 1 to 9, characterized in that the contours of the axially offset in the cylinder (Z) The openings of the inlet channels (B1 to B6) overlap each other in the circumferential direction. 11. Pump element according to at least one of claims 1 to 10, characterized in that a check valve (R) opening in the flow direction to the pressure outlet (D) is provided in the cylinder (Z), and that the pressure outlet (D) comprises at least one approximately radial bore and one external circumferential groove (11) in the wall of the sleeve body (H), which is aligned with an approximately radial outlet (12) in the wall of the housing (G). 12. Pump element according to claim 1, characterized in that the sleeve body (H) has an end section (24) with a rotary handle (25 ¹ ) which projects beyond the housing (G). 13. Pump element according to claim 12, characterized in that a clamping nut (27) which can be tightened against the housing (G) can be screwed onto the end section (24). 14. Pump element according to claim 12, characterized in that rotary positioning means (28, 29, 20) are provided between the housing (G) and the end portion (24) of the sleeve body (H). 15. Pump element according to claim 14, characterized in that a disk (28) is non-rotatably arranged on the end section (24), which disk has positioning notches (29) on the circumference for a fixing element (20) mounted in the housing (G), and that the positioning notches (29) are aligned with the inlet channels (B 1 to B6) in such a way that when the fixing element (20) engages in a positioning notch (29), a selected inlet channel (B 1 to B6) is connected to the supply. 16. Pump element according to at least one of the preceding claims, characterized in that the reciprocating piston (K) is acted upon in the suction direction by a return spring (1) supported on the sleeve body (H), and that the sleeve body (H) is supported axially on the housing (G) in the pressure direction of the reciprocating piston (K) and can be clamped against the housing (G) by the clamping nut (27). 17. Pump element according to at least one of the preceding claims, characterized in that the pump element (E) is inserted from the outside with the housing (G) into an outwardly open receiving bore (30) of a pump module housing (C) of a cylinder oil lubrication pump for medium and large diesel engines (P), in which an eccentric shaft (33, 34) acting on the reciprocating piston (K) is arranged, that the pump module housing (C) has internal channels which connect a lubricating oil supply to the passage (F) of the housing (G) and the pressure outlet (12) of the housing (G) to a lubrication connection, and that the rotary handle (25·) of the delivery quantity adjustment device (V) is arranged on the outside of the pump module housing (C) in a freely accessible manner.