Gear Pump

Abstract

A gear pump includes a drive shaft, a rotatable pump element mounted on the drive shaft, a side wall member disposed on one side of the pump element, and formed with a shaft hole through which the drive shaft extends, and a side plate disposed on the other side of the pump element. The gear pump further includes a connecting section connecting the drive shaft with the pump element in a manner to prevent relative rotation and to allow relative axial movement between the drive shaft and the pump element. The connecting section includes a drive recess formed in the pump element, and a drive projection projecting radially outwards from the drive shaft, and engaging in the drive recess to prevent the relative rotation. The drive projection is arranged to limit the axial movement of the drive shaft relative to the pump element with one of the side wall member and the side plate.

Description

BACKGROUND OF THE INVENTION

The present invention relates to gear pumps.

A published Japanese patent application 2007-278085 shows a gear pump in which a bearing for supporting a drive shaft is arranged to restrict axial movement of the drive shaft. This bearing includes an inner race, an outer race and rolling elements confined between the inner and outer races. The axial movement of the drive shaft is restricted with the arrangement in which the drive shaft is fixed to the inner race by press fitting, and the outer race is supported in a casing in such a manner as to prevent axial movement.

SUMMARY OF THE INVENTION

The operation of press-fitting the inner race over the drive shaft in the above-mentioned gear pump tends to make difficult the assembly process. Moreover, the use of the bearing as means for limiting the axial movement tends to increase the size of the pump with a size increase of the bearing.

Therefore, it is an object of the present invention to provide a gear pump adequate for assembly process, and size reduction.

According to one aspect of the present invention, the axial movement of a drive shaft is limited with at least one drive projection projecting radially outwards from the drive shaft, and engaging with a gear mounted on the drive shaft.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view showing a front side of a gear pump according to a first embodiment of the present invention.

FIG. 2 is a perspective view showing a rear side of the gear pump of FIG. 1.

FIG. 3 is a front view of the gear pump of FIG. 1.

FIG. 4 is a sectional view taken across a line A4-A4 in FIG. 3.

FIG. 5 is a sectional view taken across a line A5-A5 in FIG. 3.

FIG. 6 is an enlarged view showing a pump assembly in the section of FIG. 4.

FIG. 7 is an enlarged view showing the pump assembly in the section of FIG. 5.

FIG. 8 is a perspective view showing the front side of an intermediate member shown in FIGS. 6 and 7.

FIG. 9 is a perspective view showing the rear side of the intermediate member (or seal member).

FIG. 10 is a front view of the intermediate member.

FIG. 11 is a rear view of the intermediate member.

FIG. 12 is sectional view taken across a line A12-A12 shown in FIG. 11.

FIG. 13 is a perspective view showing the front side of a first side plate member shown in FIGS. 6 and 7.

FIG. 14 is a perspective view showing the front side of the first side plate.

FIG. 15 is a front view showing the first side plate.

FIG. 16 is a rear view of the first side plate.

FIG. 17 is a top view of the first side plate.

FIG. 18 is a view showing the arrangement of a first gear and the first side plate shown in FIGS. 6 and 7, used for illustrating operations of the gear pump according to the first embodiment.

FIG. 19 is a view showing the arrangement of the first gear, the first side plate, the intermediate member (shown by a two dot chain line), and a holding member (shown by a one dot chain line).

FIG. 20 is a sectional view taken across a line A20-A20 shown in FIG. 19.

FIG. 21 is a perspective view showing the rear side of a second side plate shown in FIGS. 6 and 7.

FIG. 22 is a perspective view showing the rear side of the second side plate.

FIG. 23 is a front view of the second side plate.

FIG. 24 is a rear view of the second side plate.

FIG. 25 is a top view of the second side plate.

FIGS. 26A, 26B and 26C are schematic views for illustrating dimensions of a connecting section around a drive shaft in the gear pump shown in FIGS. 1˜7, and for illustrating relative positioning with drive pins of the connecting section.

FIG. 27 is a sectional view showing a gear pump according to a second embodiment.

FIG. 28 is a sectional view showing a gear pump according to a third embodiment.

FIG. 29 is a sectional view showing a gear pump according to a fourth embodiment.

FIG. 30 is a view for illustrating operations of the gear pump of FIG. 29.

FIG. 31 is a sectional view similar to FIG. 6, but showing a gear pump according to a further embodiment of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1˜26 show a gear pump according to a first embodiment of the present invention. As shown in FIGS. 1˜5, the gear pump 1 of the first embodiment is adapted to be used as an actuator for a brake pressure control system of a motor vehicle. Gear pump 1 in the illustrated example is a tandem gear pump. Gear pump 1 includes, as main components, a housing 2 and a pump assembly 3 enclosed in housing 2.

Housing 2 includes a pump chamber 4 for receiving pump assembly 3. In this example, housing 2 is rectangular as viewed in FIG. 3, and approximately in the form of a rectangular parallelepiped as shown in FIGS. 1 and 2. Outside surfaces of housing 2 are formed with various mount holes 2a for mounting selector valves and sensors (not shown). Pump chamber 4 is opened approximately at the center of the front side of housing 2. Pump chamber 4 is cylindrical and approximately in the form of a stepped circular cylinder extending rearwards from an open end formed in the front surface of housing 2 to a bottom of pump chamber 4 on the rear side, and having an annular shoulder surface 4b facing forwards toward the open end and forming an annular step in pump chamber 4.

Pump assembly 3 extends from a front side adapted to be connected with a drive source which is a motor (not shown) in this example, to a rear side on which a first pump 8 is located. As shown in FIGS. 6 and 7, pump assembly 3 includes a cover member 6, an intermediate member 7 (which may be referred to as seal member or partition member), the first pump 8, a second pump 9, etc. It is possible to consider that pump assembly 3 further includes a plug member 5. (Pump assembly 3 may further include a drive shaft 10.) Plug member 5 is a circular plate-like member formed with a central hexagonal through hole 5a extending from a front surface to a rear surface 5d of plug member 1. The rear surface 5d is an abutment surface abutting on cover member 6. Plug member 5 includes an annular axial projection 5b surrounding the rear abutment surface 5d and projecting axially rearwards. Plug member 5 further includes an externally threaded portion 5c formed in the outer circumferential surface. With the externally threaded portion 5c, the plug member 5 is screwed into an internally threaded portion 4a formed in pump chamber 4 of housing 2.

Cover member 6 is a circular plate-like member including a front surface 6e which is an abutment surface abutting against plug member 5, and an annular recess 6f surrounding the front abutment surface 6e and forming a step. When plug member 5 is screwed in pump chamber 4, the rear abutment surface 5d of plug member 5 abuts against the front abutment surface 6e of cover member 6, and the annular projection 5b of plug member 5 fits over a front end portion of cover member 6 in the annular recess 6f of cover member 6.

Cover member 6 further includes a circumferential radial projection 6g projecting radially outwards to have an outside diameter approximately equal to the inside diameter of pump chamber 4, and the outside diameter of the annular projection 5b of plug member 5, so that the projection 6g and 5b are fit in the inside cylindrical surface of pump chamber 4. Cover member 6 further includes an annular seal groove 6h located on the rear side of projection 6g. A first annular seal S1 is disposed axially between annular axial projection 5b of plug member 5 and radial projection 6g of cover member 6, to seal a clearance radially between the outside surface of cover member 6 and the inside surface of pump chamber 4. A second annular seal S2 is disposed in the seal groove 6h to seal a clearance between cover member and the inside surface of pump chamber 4. First and second seals S1 and S2 are disposed at two separate positions spaced axially in the front and rear (axial) direction.

A stepped through hole 6b is formed at an eccentric position of cover member 6. Stepped through hole 6b includes a larger diameter (front) portion and a smaller diameter (rear) portion having an inside diameter smaller than the inside diameter of the large diameter portion. A drive shaft 10 is inserted in this stepped through hole 6b with a clearance 6a in the smaller diameter portion. Annular seal members S3 are disposed, respectively, in the larger diameter portion and the smaller diameter portion of stepped through hole 6b to seal a clearance around drive shaft 10. Cover member 6 further includes a cylindrical recessed portion 6d recessed from the rear end of cover member 6 toward the front end, and an annular axial projection 6c surrounding the recessed portion 6d, and projecting axially rearwards. In annular axial projection 6c, there is formed an annular stepped portion 6i defined by an annular shoulder surface facing rearwards.

Intermediate member (or seal member) 7 is a circular plate-like member as shown in FIGS. 8˜12. Intermediate member 7 includes a through shaft hole 7a and two insertion holes 7b and 7c. Insertion holes 7b and 7c are located on the lower side of through hole 7a as viewed in FIGS. 7˜12, and aligned in a line extending in parallel to a center line of through shaft hole 7a as best shown in FIG. 7. Through shaft hole 7a is a circular hole having a circular cross section, and extending through seal member 7 axially in the front and rear direction. Insertion holes 7b and 7c are also circular holes each having a circular cross section. Insertion holes 7b and 7c are opened, respectively, from the front and rear side surfaces of intermediate member 7, and extended toward each other in the thickness direction up to a bottom wall separating insertion holes 7b and 7c, as shown in FIG. 12 and FIG. 7. On each of the front and rear sides, intermediate member 7 includes a side seal portion 7d surrounding the through hole 7a and insertion hole 7b or 7c, and projecting axially around the corresponding holes so as to fringe the holes. Each of the side seal portions 7d includes a pair of engagement projections 7e projecting to one side.

The side seal portion 7d on each of the front and rear sides includes a ring receiving annular recess 7f recessed in the thickness direction, around through hole 7a coaxially, as shown in FIGS. 8 and 9. Furthermore, on the rear side, there is formed a smaller diameter ring receiving annular recess 7g recessed deeper continuously in the thickness direction from the annular recess 7f of the rear side, coaxially around through hole 7a, as shown in FIG. 9. Moreover, intermediate member 7 includes an annular seal groove 7h recessed radially inwards from the outer circumferential surface of intermediate member 7, and a front annular axial projection 7i projecting axially forwards from the front side.

Intermediate member 7 is pushed rearwards through cover member 6 by the axial force produced by plug member 5 when screwed into pump chamber 4, as shown in FIGS. 6 and 7. As a result, the annular front projection 7i is fit in the step portion 6i formed on the radial inner side of annular rear projection 6c of cover member 6, and an outer region of the rear side surface of intermediate member 7 abuts on the forwardly facing annular shoulder surface 4b formed in pump chamber 4, so that seal member 7 is positioned reliably at a predetermined position. Drive shaft 10 is received, and supported rotatably in the through shaft hole 7a of intermediate member 7. Support shafts 11a and 11b are forcibly fit and fixed, respectively, in insertion holes 7b and 7c.

An annular rotation seal member (or shaft seal member or shaft sealing element) 12 (such as X ring) is disposed in the rear side annular seal receiving recess 7g to provide a sealing barrier around drive shaft 10 for sealing off a later-mentioned first pump chamber P1. Furthermore, a first seal ring 13a is disposed in annular seal receiving recess 7f on the rear side in such a state as to close the annular recess 7g of rotation seal member 12. A second seal ring 13b is disposed in annular recess 7f on the front side. Seal rings 13a and 13b are made of material harder and better in durability than seal member 7. First and second seal rings 13a and 13b can serve as first and second stopper members. In this example, seal rings 13a and 13b are metallic members such as sintered metal member or hard metal member or a member of super hard alloy. An annular seal S4 is disposed in annular seal groove 7h of intermediate member 7 and arranged to contact tightly with the inside circumferential surface of pump chamber 4 to secure a sealing separation between first and second pump chambers P1 and P2.

The first pump chamber P1 is defined, as a closed space, between intermediate member 7 and the bottom of pump chamber 4, in a recessed portion 4c recessed axially rearwards from the shoulder surface 4b of housing 2. First pump 8 is provided in first pump chamber P1. The second pump chamber P2 is defined, as a closed space, between the bottom of recessed portion 6d of cover member 6 and intermediate member 7. Second pump 9 is provided in second pump chamber P2.

A first gear (or gearing) 15 is disposed in first pump chamber P1, between intermediate member 7 and a first side plate 14 so that the front and rear sides and the tooth tops are sealed by these members. As shown in FIGS. 13˜17, the first side plate 14 is a member made of a resin, and shaped like a (rounded) triangle as viewed in the front view. First side plate 14 includes three through holes 14a, 14b and 14c formed, respectively, in three corners of triangular first side plate 14. First side plate 14 further includes a side seal portion 14d surrounding the through holes 14a and 14b on the front side, and projecting axially forwards.

A seal block 14e is formed in first side plate 14. Seal block 14e is shaped like a triangle, and projects axially forwards from the front surface of first side plate 14. Seal block 14e of first side plate 14 includes: a passage portion 14f forming an open portion extending continuously from the through hole 14c toward the center of first side plate 14; a pair of tooth top seal portions 14g which are formed on both sides of the passage portion 14f, which are continuous with a part of the side seal portion 14d, and which are in the form of a curved surface; and engagement portions 14h located on the front side of the respective tooth top seal portions 14g. Seal block 14e further includes a curved groove 14i which is recessed rearwards and which extends around the through hole 14c and tooth top seal portions 14g. In the rear side, as shown in FIG. 16, the first side seal plate 14 is formed with a seal groove 14j extending curvedly so as to describe a triangle, and surrounding the three through holes 14a, 14b and 14c.

As shown in FIG. 7, drive shaft 10 is received rotatably with a predetermined radial clearance in the through hole 14a of first side plate 14, and the rear side support shaft 11a is received in the through hole 14b with a predetermined radial clearance. A seal S5 is received in the rear side seal groove 14j, and thereby arranged to seal off the first pump chamber P1 from a lower pressure region.

First gear (or gearing) 15 is composed of a driving gear (or toothed wheel serving as a pump element) 15a mounted on drive shaft 10, and a driven gear (or toothed wheel serving as a further pump element) 15b mounted on support shaft 11a. The teeth 15c and 15d of driving and driven gears 15a and 15b are engaged with each other in an engagement region 15e, as best shown in FIG. 18. As shown in FIGS. 6 and 18, drive shaft 10 is formed with a radial hole or recessed portion 10d recessed radially inwards at the position supporting the driving gear 15a. A radially extending driving pin 10a (serving as a first or second drive projection) is inserted in this radial hole 10d. In this example, driving pin 10a is cylindrical. Driving pin 10a may be fixed by press fitting or may be merely inserted in radial hole 10d.

Driving pin 10a is engaged in a recess (drive recess) 15f (serving as a first or second drive recess) formed in the inside circumference of driving gear 15a in the form of a cutout extending through the driving gear 15a in the widthwise direction of driving gear 15a. Drive shaft 10 includes a forward end portion 10b adapted to be connected with the drive source which, in this example, is a motor (not shown) (as shown in FIG. 7). This forward end portion 10b is shaped to have a noncircular cross section such as a square cross section, and arranged to serve as a portion to be connected with the rotation shaft of the motor. Thus, drive shaft 10 is adapted to be driven by the rotation of the motor.

Thus, driving pin 10a is arranged to prevent the rotation of driving gear 15a relative to drive shaft 10, and to cause the driving gear 15a to rotate as a unit with drive shaft 10. When drive shaft 10 is driven, the driving gear 15a rotates in the same direction as drive shaft 10, and the driven gear 15b is rotated in the opposite direction by driving gear 15a.

As shown in FIG. 18, the tops of teeth 15c and 15d of driving and driven gears 15a and 15b are shaped and adapted to contact liquid-tightly and slidably with the respective tooth top seal portions 14g of seal block 14e of first side plate 14. As shown in FIG. 19, the first and second engagement projections 7e on the rear side of intermediate member 7 are engaged, respectively, with the engagement portions 14h of seal block 14e in such a tight manner that the curved concave surfaces of engagement portions 14h are in contact with the curved convex surfaces of the respective engagement projections 7e. With this arrangement, the tops of teeth 15c and 15d of driving and driven gears 15a and 15b are sealed, with side seal portion 14d of first side plate 14. Furthermore, a holding member 16 extending so as to describe a triangle is fit in groove 14i on the outer circumference of seal block 14e and on the corresponding side seal portion 7d of seal member 7 (as shown in FIG. 7).

Pump chamber 4 of housing 2 is provided with an inlet port (not shown) communicating with the through hole 14c of first side plate 14, and an outlet port (not shown) communicating with first pump chamber P1.

Second pump 9 is disposed on the front side of intermediate member 7 so that first and second pumps 8 and 9 are symmetrical with respect to a cross section of intermediate member 7 at the middle between pumps 8 and 9. A second gear (or gearing) 18 of second pump 9 is sealed between intermediate member 7 on the rear side and a second side plate 17 on the front side. As shown in FIGS. 21˜25, second side plate 17 includes through holes 17a, 17b and 17c, a side seal portion 17d, a seal block 17e, a passage portion 17f, tooth top seal portions 17g, engagement portions 17h, a groove 17i and a seal groove 17j, like first side plate 14. Furthermore, a holding member 16 extending so as to describe a triangle is fit in groove 17i on the outer circumference of seal block 17e and on the corresponding side seal portion 7d of seal member 7 (as shown in FIG. 7).

As shown in FIG. 7, drive shaft 10 is received rotatably with a predetermined radial clearance in the through hole 17a of second side plate 17, and the front side support shaft 11b is received in the through hole 17b with a predetermined radial clearance. A seal S6 is received in the front side seal groove 17j, and thereby arranged to seal off the second pump chamber P2.

Second gear (or gearing) 18 is composed of a driving gear (toothed wheel serving as a pump element) 18a mounted on drive shaft 10, and a driven gear (toothed wheel serving as a further pump element) 18b mounted on the support shaft 11b, like first gear 15. The teeth 18c and 18d of driving and driven gears 18a and 18b are engaged with each other in an engagement region 18e.

As shown in FIG. 6, drive shaft 10 is formed with a radial hole or recess recessed radially inwards at the position supporting the driving gear 18a. A radially extending drive pin 10c is inserted in this radial hole 10e. In this example, drive pin 10c is a cylindrical pin projecting radially outwards in a radial direction from the center axis of drive shaft 10. Drive pin 10c may be fixed by press fitting or may be merely inserted in radial hole 10e. Drive pin 10c is engaged in a drive recess 18f formed in the inside circumference of driving gear 18a. Drive pin 10c can serve as a drive projection. In this example, drive recess 18f is in the form of a cutout or notch extending through the driving gear 18a in the widthwise direction of driving gear 18a.

Thus, drive pin 10c is arranged to prevent the rotation of driving gear 18a relative to drive shaft 10, and to cause the driving gear 18a to rotate as a unit with drive shaft 10. When drive shaft 10 is driven, the driving gear 18a rotates in the same direction as drive shaft 10, and the driven gear 18b is rotated in the opposite direction by driving gear 18a.

In second pump 9, pump chamber 4 of housing 2 is provided with an inlet port (not shown) communicating with the through hole 17c of second side plate 17 through an oil passage formed in cover member 6, and an outlet port (not shown) communicating with second pump chamber P2 through an oil passage formed in cover member 6. In the other respects, the second pump 9 is constructed in the same manner as first pump 8.

Dimensions in the vicinity of drive shaft 10 are determined in the following manner, as illustrated in FIGS. 26A, 26B and 26C. In FIG. 26A, D1 is a (radial) distance from the center of drive shaft 10 to the radial outer end of driving pin 10a (or driving pin 10c) extending radially outwards, D2 is the radius of the annular rotation seal member 12, and D3 is the radius of first seal ring 13a (or second seal ring 13b). As schematically shown in FIG. 26A, these dimensions D1, D2 and D3 are determined so that D1<D2<D3. Generally, at least one of the following three conditions is met. First, drive projection (10a, 10c) is so sized that the drive projection does not project radially outwards beyond the stopper member (13a, 13b), and the stopper member extends radially outwards beyond the drive projection. Second, the stopper member (13a, 13b) is greater in cross sectional size than rotation seal member 12. Third, the rotation seal member 12 extends radially outwards beyond the drive projection (10a, 10c).

The diameter D4 of driving pin 10a (or driving pin 10c) is smaller than or equal to the thickness D5 of driving gear 15a (or driving gear 18a). Generally, the drive projection (10a, 10c) is thinner in axial dimension than the driving gear (15a, 18a) so that the drive projection does not project laterally or axially beyond the driving gear.

The (axial) depth H1 of each ring receiving portion 7f is substantially equal to the (axial) thickness H2 of first seal ring 13a (or second seal ring 13b).

The spacing L2 between the driving pins 10a and 10c (distance between the confronting closer (or inner) sides of driving pins 10a and 10c) is greater than the distance L1 between the far (or outer) sides of the seal rings 13a and 13b.

The diameter of the though hole 14a or 17a of each of the side plates 14 and 17 is greater than the diameter of drive shaft 10. The diameter of each of through holes 14b and 17b is greater than the diameter of support shaft 11a or 11b. Drive shaft 10 and support shafts 11a and 11b are inserted in the respective holes 14a, 17a, 14b and 17b of side plates 14 and 17 with slight clearance.

The thus-constructed gear pump 1 is assembled in the following manner. First, rotation seal member 12 is fit in seal receiving portion 7g of intermediate member (or seal member) 7 preliminarily equipped with seal S4, and thereby fixed provisionally.

Then, drive shaft 10 is inserted through the through hole 7a of intermediate member 7, and thereafter support shafts 11a and 11b are inserted, respectively, in insertion holes 7b and 7c. Thus, a subassembly of intermediate member 7, drive shaft 10 and support shaft 11a and 11b is formed.

Then, seal rings 13a and 13b are inserted, respectively, in ring receiving portions 7f of intermediate member 7. In this case, the rotation seal member 12 is pressed by first seal ring 13a, and thereby the rotation seal member 12 is pressed tightly to drive shaft 10.

Then, the driving pins 10a and 10c are inserted and fixed in radial holes or recessed portions 10d and 10e of drive shaft 10, respectively. Thereafter, driving gears 15a and 18a are mounted on drive shaft 10 in the state in which the driving pins 10a and 10c are engaged in the recesses 15f and 18f of driving gears 15a and 18a, respectively.

Thereafter, driven gears 15b and 18b are mounted on support shafts 11a and 11b, and engaged with driving gears 15a and 18a, respectively.

Then, side plates 14 and 17 are incorporated into the subassembly of intermediate member 7 by inserting drive shaft 10 and support shafts 11a and 11b into side plates 14 and 17 equipped preliminarily with seals S5 and S6 and holding members 16 and 19, respectively. In this case, first side plate can be readily positioned relative to intermediate member 7 by engaging the engaging portions 14h of first side plate 14 with engagement projections 7e of intermediate member 7 so that the assembly step becomes easier. Furthermore, with holding member 16, it is possible to hold the intermediate member 7 and first side plate 14 together temporarily. Holding member 16 can be readily mounted on intermediate member 7 and first side plate 14 by first mounting the holding member 16 on intermediate member 7, and then expanding the holding member 16 onto first side plate 14.

Similarly, second side plate can be readily positioned relative to intermediate member 7 by engaging the engaging portions 17g of second side plate 17 with engagement projections 7e of intermediate member 7 so that the assembly step becomes easier. Furthermore, with holding member 19, it is possible to hold the intermediate member 7 and second side plate 17 together temporarily. Holding member 19 can be readily mounted on intermediate member 7 and second side plate 17 by first mounting the holding member 19 on intermediate member 7, and then expanding the holding member 19 onto second side plate 17.

Then, cover member 6 is incorporated into the subassembly of intermediate member 7 by inserting drive shaft 10 into the through hole 6a of cover member 6, and at the same time fitting the annular projection 6c of cover member 6 into intermediate member 7. Thus, the pump assembly 3 is assembled.

The thus-assembled pump assembly 3 is inserted into pump chamber 4 of housing 2. Then, plug member 5 is screwed into pump chamber 4 and thereby fixed in housing 2. In this case, with the axial force produced by screwing the plug member 5, the intermediate member 7 is pressed against the step portion 4b in pump chamber 4, and thereby positioned stably, so that the positions of parts can be determined accurately in the axial direction or front and rear direction, and the gear pump becomes able to prevent unsteadiness or shakiness due to pressure fluctuations of the operation fluid, as mentioned later. Moreover, with the annular projection 5b, plug member 5 presses seal S1, and thereby improves the sealing between cover member 6 and pump chamber 4 of housing 2.

In this way, parts of the gear pump 1 are sub-assembled preliminarily and inserted, in the form of pump assembly 3, into housing 2. Therefore, the gear pump 1 according to the first embodiment can make simple and easier the assembly process.

The gear pump 1 is operated in the following manner. When drive shaft 10 is driven by the motor in a rotational direction shown by an arrow in FIG. 18, then the driven gear 15b is rotated by driving gear 15a in first pump P1. With this movement, the operating fluid of a lower pressure (or negative pressure) is sucked, through the through hole 14c of seal block 14e of first side plate 14, from the inlet port, and the operating fluid of a higher pressure is let out into pump chamber P1. The operating fluid of the higher pressure is discharged from the corresponding outlet port.

In second pump P2, the driven gear 18b is rotated by drive shaft 10, through the driving gear 18a, as in first pump P1. With this movement, the operating fluid of a lower pressure is sucked through the through hole 17c of seal block 17e of second side plate 17, and the operating fluid of a higher pressure is let out into second pump chamber P2. This operating fluid of the higher pressure is discharged from the corresponding outlet port.

Thus, the first and second pumps 8 and 9 can perform inlet operations of sucking the operating fluid and outlet operations of discharging the operation fluid under pressure in two separate hydraulic systems. Gear pump 1 in the illustrated example of the first embodiment can function as a tandem external gear pump.

In general, the first and second pumps 8 and 9 are used, respectively, for first and second hydraulic systems such as first and second brake systems of a vehicle. For example, one of the first and second hydraulic systems is for the front left wheel and rear right wheel of the vehicle, and the other system is for the front right wheel and rear left wheel of the vehicle.

The tooth top seal portions 14g and 17g are formed integrally in side plates 14 and 17, respectively. Therefore, this gear pump 1 can reduce the number of constituent parts, and the manufacturing cost, and facilitate the assembly process. The side plates 14 and 17 made of resin is advantageous for improving the production accuracy and the sealing performance.

The sealing ability is improved in the following manner. The teeth of 15c and 15d of gears 15a and 15b in first pump 8 are arranged to rotate while contacting with the tooth top seal portions 14g of first side plate 14 liquid-tightly. Accordingly, as shown in FIG. 18, there are formed a lower pressure fluid chamber B1 enclosed by the passage portion 14f of through hole 14c communicating with the inlet port, driving gear 15a, driven gear 15b and a part of intermediate member 7, and the pump chamber P1 becomes a higher pressure fluid chamber B2.

Accordingly, seal block 14e is pushed by a pushing force from second fluid chamber B2 toward first fluid chamber B1 (toward the tooth top seal portions 14g) and sideways. Therefore, the engagement portions 14h of seal block 14e push the engagement projections 7e of intermediate member 7 to ensure the close contact between intermediate member 7 and seal block 14e of first side plate 14, and thereby ensures the sealing ability between the higher pressure side and the lower pressure side. Furthermore, with the above-mentioned pushing force, the tooth top seal portions 14g abut properly on the tops of the respective teeth 15c and 15d of gears 15a and 15b, and thereby improve the sealing performance between the higher pressure side and the lower pressure side.

Additionally, the holding member 16 provides a holding force or binding force which acts to force the tooth top seal portions 14g to abut properly against the tops of teeth 15c and 15d of gears 15a and 15b and to improve the sealing. Thus, holding member 16 can improve the sealing between the higher and lower pressure sides and the sealing around the through hole 14c and intermediate member 7.

Second pump 9 is operated in the same manner, and arranged to provide the same effects as first pump 8.

The sides surfaces of the gears are sealed in the following manner. The front and rear side surfaces of each gear 15a or 15b are sealed by the corresponding side seal portion 14d of first side plate 14 and side seal portion 7e of intermediate member 7.

In this case, the axial dimension (or diameter) D4 of driving pin 10a (driving pin 10c) is smaller than or equal to the axial dimension (or thickness) D5 of driving gear 15a (driving gear 18a). Therefore, driving pin 10a (10c) is received within the thickness of driving gear 15a (18a) without projecting from the driving gear on each side, so that the sealing performance is secured on both sides of each of the gears 15 and 18.

The depth H1 of each ring receiving portion 7f is substantially equal to the thickness H2 of first seal ring 13a (second seal ring 13b). Therefore, seal rings 13a and 13b can be held stably, and the sealing performance of driving gear 15a (18a) can be improved.

The diameter of the through hole 14a or 17a of each side plate 14 or 17 is set greater than the diameter of drive shaft 10. The diameter of the through hole 14b or 17b of each side plate 14 or 17 is set greater than the diameter of support shaft 11a or 11b.

Therefore, the drive shaft 10 and support shafts 11a and 11b are inserted loosely with a slight clearance in the respective through holes 14a, 17a, 14b and 17b of side plates 14 and 17. Therefore, even if drive shaft 10 or support shaft 11a or 11b is inclined, the side plates 14 and 17 are not interfered with the inclined shaft and not acted upon by an undesired external force. Therefore, intermediate member 7 and side plates 14 and 17 can maintain the stable abutment and contact therebetween for sealing, and thereby improve the reliability of the gear pump.

Drive shaft 10 and gears 15 and 18 are positioned relative to one another in the following manner. In the first embodiment, when drive shaft 10 moves axially, the driving pins 10a and 10c moves axially together with drive shaft 10. This axial movement is limited by the seal ring 13a or 13b on the trailing side abutting against the leading side of the driving pin 10a or 10c on the trailing side of this movement.

As shown in FIG. 26A, the distance L2 between the inner sides of driving pins 10a and 10c is set greater than the distance L1 between the outer sides of seal rings 13a and 13b. Therefore, when drive shaft 10 moves to the left as shown by an arrow in FIG. 26B, only the left side surface of first driving pin 10a abuts on the first seal ring 13a on the trailing side which is the right side in the case of the leftward axial movement, and the leftward movement of drive shaft 10 is limited by this abutment between first driving pin 10a and first seal ring 13a.

In the case of rightward movement of drive shaft 10 as shown by an arrow in FIG. 26C, only the right side surface of second driving pin 10c abuts on the second seal ring 13b on the trailing side which is the left side in the case of the rightward axial movement, and the rightward movement of drive shaft 10 is limited by this abutment between second driving pin 10b and second seal ring 13b.

The thicknesses are so determined that, when driving pin 10a (or driving pin 10c) on one side abuts against the first seal ring 13a (or second seal ring 13b), the driving pin 10c (or driving pin 10a) on the opposite is out of contact with the side plate 17 (or side plate 14).

Thus, the gear pump of the first embodiment makes it possible to determine the axial position of drive shaft 10 relative to the first and second gears 15 and 18, to allow axial movement of drive shaft 10 relative to first and second gears within a predetermined range in the thickness of the first and second gears 15 and 18 (15a, 18a), and to limit the axial movement in the first (rearward) direction with the drive projection (10c) on the second (front) side and in the second (forward) direction with the drive projection (10a) on the first (rear) side to prevent extraction in the axial direction.

The drive projections 10a and 10c are arranged to abut against the respective seal rings 13a and 13b only with the inner sides of the drive projections 10a and 10c which confront each other axially across intermediate member 7 so that, at the time of abutment, each drive projection 10a or 10c receives an axial force only in one axial direction. Therefore, it is possible to improve the durability of each drive pin 10a or 10c.

In a comparative example in which the first and second seal rings 13a and 13b and intermediate member 7 are a single integral member, it is necessary to make the intermediate member 7 by using hard metal in order to attain the durability. Therefore, the comparative example increases the manufacturing cost and the weight of the gear pump.

By contrast to the comparative example, the intermediate member 7 according to the first embodiment is a member separate from the seal rings 13a and 13b. Therefore, the intermediate member 7 may be made of a resin or other material which is advantageous in cost reduction and weight reduction. Moreover, as compared to another comparative example in which the first and second seal rings 13a and 13b are provided in the respective side plates 14 and 17 (instead of intermediate member 7), this embodiment makes it possible to determine the axial position of drive shaft 10 relative to each gear 15 or 18 accurately and easily by controlling the dimension of intermediate member 7 only. 73

First seal ring 13a is arranged to close the seal receiving portion 7g. Therefore, first seal ring 13a prevents contact between drive pin 10a and rotation seal member 12, and thereby protect the rotation seal member 12 by preventing abrasion and injury.

This arrangement of first seal ring 13a can improve the sealing separation between pump chambers Pa and P2, and thereby improve the reliability of the gear pump. It is optional to form a similar seal receiving portion 7g at the side of second seal ring 13b and provide a similar rotation seal member 12 in this seal receiving portion 7g in the same manner as in the first pump to achieve the same effect.

It is possible to form a seal receiving portion 7g at the middle of through hole 7a, by a first method of forming the intermediate member 7 of a metallic material by joining two separate parts of the metallic material shaped to form the seal receiving portion between the two separate parts, or by a second method of forming the intermediate member of a resin by using a slide (or slide mold)? inserted in the through hole. However, these methods deteriorates the productivity, and incurs the size increase. Moreover, it is difficult to insert the rotation seal 12 in the seal receiving portion 7g at the middle of intermediate member 7. By contrast, in the first embodiment, the seal receiving portion 7g can be formed from one side of intermediate member 7, so that the gear pump of the first embodiment is advantageous for the productivity and the assembly process

As shown in FIG. 16A, the radial length D1 from the center line of drive shaft 10 to the top of drive pin 10a (or 10c) is smaller than the radius D2 of seal ring 13a (or 13b). Therefore, by decreasing the projecting length of drive pin 10a (10c), it is possible to decrease the size or radius of driving gear 15a (18a) and hence to decrease the size of the gear pump 1.

FIG. 27 shows, in section, a gear pump 1 according to a second embodiment of the present invention. The following explanation is directed only to points different from the first embodiment, and repetitive explanation is omitted as to similar component parts to which the same reference numerals are given.

In the gear pump 1 of FIG. 27, the seal rings 13a and 13b are omitted, and the intermediate member 7 is a metallic integral member formed of metallic material, by cold forging.

An annular bearing member 21 of resin or metallic material and an annular seal S7 are disposed in a stepped recess portion 20 which is formed in intermediate member 7 at the position at which the rotation seal 12 is disposed in the case of FIG. 6 in the first embodiment. The stepped recess portion 20 includes a larger portion having a larger size (larger diameter), and a smaller portion which has a smaller size (smaller diameter) smaller than the size of the larger portion and which is formed continuously from the larger portion on the front side or deeper side of the larger portion. Annular seal S7 is fit in the smaller portion of stepped recess portion 20, and the annular bearing member 21 is disposed in the larger portion, axially between the annular seal S7 and first gear 15. Drive shaft 10 is received in the shaft hole 7a of intermediate member 7 loosely with a radial clearance 22. Drive shaft 10 is fit forcibly and fixed in the annular bearing member 21. Therefore, drive shaft 10 is supported rotatably by intermediate member 7 in recess portion 20 through bearing member 21. Seal S7 is arranged to contact tightly with drive shaft 10 and to separate the first and second pump chambers P1 and P2 sealingly. Bearing member 21 may be replaced by a bearing such as a metal ball bearing.

Bearing member 21 is arranged to limit the axial movement of drive shaft 10 by abutting against the inner side of drive pin 10a, and intermediate member 7 is arranged to limit the axial movement of drive shaft 10 by abutting against the inner side of drive pin 10c. In this way, the gear pump of the second embodiment can provide the same advantageous effects.

FIG. 28 shows, in section, a gear pump according to a third embodiment of the present invention. The following explanation is directed only to points different from the first embodiment, and repetitive explanation is omitted as to similar component parts to which the same reference numerals are given.

As shown in FIG. 28, the first seal ring 13a is provided in first side plate 14, and the second seal ring 13b is provided in second side plate 17, unlike the gear pump of FIG. 6 in the first embodiment.

The first seal ring 13a limits the axial movement of drive shaft 10 by abutting against the outer side of drive pin 10a (moved together with drive shaft 10 in the direction away from intermediate member 7), and the second seal ring 13a limits the axial movement of drive shaft 10 by abutting against the outer side of drive pin 10c (moved together with drive shaft 10 in the direction away from intermediate member 7). In this way, the gear pump of the third embodiment can provide the same advantageous effects.

FIG. 29 shows a gear pump 1 according to a fourth embodiment of the present invention. The gear pump 1 shown in FIG. 29 includes many component parts having substantially identical counterparts in the gear pump of the first embodiment. Therefore, the same reference numerals are given to components parts similar to the corresponding component parts of gear pump 1 of the first embodiment, repetitive explanation is omitted, and the following explanation is directed only to points different from the first embodiment.

The gear pump 1 of the fourth embodiment is an internal gear pump unlike the first embodiment in which the external gear pump is employed. In the example of FIG. 29, the gear pump 1 is a tandem internal gear pump.

In the example shown in FIG. 29, the first and second side plates 14 and 17 are cup-shaped members which are identical in the shape. Instead of the seal blocks 14e and 17e, each side plate 14 or 17 includes an outer annular seal portion or wall 40 or 41 projecting from a bottom wall or end wall, axially toward intermediate member 7 and fitting over one of side seal portions 7d of the intermediate member 7.

In the space surrounded by the outer annular seal portion 40 of first side plate 14 and located axially between the first side seal portion 7d of intermediate member 7 and the end wall of first side plate 14, there is provided the first gear 15 forming the first pump P1. In the space surrounded by the outer annular seal portion 41 of second side plate 17 and located axially between the second side seal portion 7d of intermediate member 7 and the end wall of second side plate 17, there is provided the second gear 18 forming the second pump P2. An annular seal S8 encloses the outer annual seal portion 40 and thereby seals the first pump P1, and an annular seal S9 encloses the outer annual seal portion 41 and thereby seals the second pump P2.

These annular seals S8 and S9 are stretched partially around the side plates 14 and 17, respectively, (though not shown), like the holding members 16 and 19, and thereby arranged to hold or bind the intermediate member 7 and first and second side plates 14 and 17.

As shown in FIG. 30, the first gear 15 of first pump 8 includes an outer rotor 42 (serving as a pump element) including an internally toothed portion 42a formed in the inside circumference, and an inner rotor 43 (serving as a pump element) including an externally toothed portion 43a form in the outside circumference. Inner rotor 43 is disposed eccentrically in outer rotor 42, and the externally toothed portion 43a is engaged with the internally toothed portion 42a in an engagement region 44, so that a pump chamber 45 is formed between outer and inner rotors 42 and 43.

Drive projection 46 is formed integrally in drive shaft 10 at each of positions confronting the inner rotors 43 of first and second pumps 8 and 9. Each drive projection 46 projects radially outwards. In this example, each drive projection 46 is in the form of a rectangular column. Drive projections 46 are fit, respectively, in drive recesses 43b formed in inner rotors 43. Each drive recess 43b is in the form of a cutout formed in the inner rotor 43. The axial dimension of each drive projection 46 is smaller than the thickness of inner rotor 43.

Thus, in each pump 8 or 9, the inner rotor 43 is mounted on drive shaft 10 and connected with drive shaft 10 so as to prevent relative rotation. Therefore, inner rotor 43 is driven by drive shaft 10, and outer rotor 42 is rotated by inner rotor 43 in the same rotational direction. Outer rotor 42 is fit rotatably in the outer seal portion 40 of the side plate 14 or 17 so that the outside circumference of outer rotor 42 is in sliding contact with the inside circumference of the outer seal portion 40 during the rotation of outer rotor 42 in outer seal portion 40.

First side plate 14 is formed with through holes 47 and 48 at positions confronting the pump chamber 45 as shown in FIGS. 29 and 30. Each through hole 47 or 48 may be in the form of a groove shaped like a crescent. Through hole 47 is connected with an inlet port 50 of pump chamber 4, through a hollow portion 49 formed between first side plate 14 and the wall of pump chamber 4. Through hole 48 is connected with an outlet port 51 of pump chamber 4.

Second side plate 17 and second gear 18 of second pump 9 are constructed in the same manner as first side plate 14 and first gear 15 in first pump 8. Second side plate 17 is formed with through holes 52 and 53.

Through hole 52 is connected with an inlet port 55 of pump chamber 4, through a fluid passage 54 formed in cover member 6. Through hole 53 is connected with an outlet port 58 of pump chamber 4 through an interspace 56 formed between the cover member 6 and second side plate 17 and a fluid passage 57 formed in cover member 6.

On the first (rear) side of intermediate member 7 toward first gear 15, there is provided a bearing member 21 like the gear pump of the second embodiment. On the second (front) side of intermediate member 7 toward second gear 18, there is provided a rotation seal member 12 like the gear pump of the first embodiment. A seal S11 is provided around through hole 48 of first side plate 14 and arranged to provide a sealing between the space 49 and the through hole 48. A seal S12 is provided around through hole 52 of second side plate 17 and arranged to provide a sealing between the space 56 and the through hole 52.

Gear pump 1 according to the fourth embodiment is operated in the following manner. When drive shaft 10 is driven in the rotational direction shown by an arrow in FIG. 30, by a motor, the outer rotor 42 is driven through inner rotor 43 in each pump 8 or 9. In this case, each pump produces a pumping action with the volume change of pump chamber 45 in each of gears 15 and 18. Therefore, in first pump 8, the fluid of a lower pressure is introduced from inlet port 50 through the through hole 47 of first side plate 14. The introduced fluid is pressurized, and outputted to outlet port 51 through the through hole 48 of first side plate 14.

In second pump 9, the fluid of a lower pressure is introduced from inlet port 55 through the through hole 52 of second side plate 17. The introduced fluid is pressurized, and outputted to outlet port 58 through the through hole 53 of second side plate 17.

Thus, the first and second pumps 8 and 9 can perform inlet operations of sucking the operating fluid and outlet operations of discharging the operation fluid under pressure in two separate hydraulic systems. Gear pump 1 in the illustrated example of the fourth embodiment can function as a tandem internal gear pump.

The outer seal portion 40 or 41 is formed integrally in each of first and second side plates 14 and 17. The tooth top seal portion 14g or 17g is formed integrally in each of first and second side plates 14 and 17. Therefore, it is possible to reduce the number of required component parts, and the manufacturing cost, and to facilitate the assembly process. The use of side plates 14 and 17 made of resin is advantageous in improving the manufacturing accuracy and the sealing performance. Moreover, the sealing performance with intermediate member 7 can be secured with holding members 16 and 19.

In the fourth embodiment, for either or both of the first and second gears 15 and 18 (42, 43), it is possible to employ the drive pin (10a, 10c) which is inserted in the radial hole (10d, 10e) formed in the drive shaft 10 and which is engaged in the drive recess (43b), instead of the integrally formed drive projection 46.

The present invention is not limited to the illustrated examples. Various variations and modifications are possible within the purview of the present invention. For example, it is possible to change the materials and configurations of some constituent parts. As shown in FIG. 31, it is possible to omit the seal ring (13b) on the side on which the rotation seal member 12 is not provided.

According to the illustrated embodiments, a gear pump has a basic construction which comprises: a drive shaft (adapted to be connected with a drive source such as a motor); a rotatable pump element mounted on the drive shaft and arranged to perform a pumping action; a side wall member (such as the intermediate or partition member 7) disposed on one side of the pump element, and formed with a shaft hole (7a) through which the drive shaft extends; a side plate disposed on the other side of the pump element so that the pump element is interposed axially between the side wall member and the side plate; and a connecting section serving as means for connecting the drive shaft with the pump element in a manner to prevent relative rotation and to allow relative axial movement between the drive shaft and the pump element. The connecting section includes a drive recess formed in the pump element, and a drive projection projecting radially outwards from the drive shaft. The drive projection is arranged to engage in the drive recess to prevent the relative rotation to drive the pump element with the drive shaft, and arranged to limit the axial movement of the drive shaft relative to the pump element with one of the side wall member and the side plate. The drive recess may be so shaped as to allow the drive projection of the drive shaft to move axially through the pump element. The thus-constructed pump can determine the axial position of the drive shaft relative to the pump element with the drive projection for transmitting a driving torque from the drive shaft to the pump element, facilitate the assembly process of the pump, and reduce the size of the pump.

The gear pump may further include a stopper member (such as 13a or 13b) in addition to the above-mentioned basic construction. The stopper member is disposed axially between the drive projection and an abutment member which is one of the side wall member and the side plate, held in the abutment member, and arranged to limit the axial movement of the drive shaft by abutting on the drive projection. The stopper member may be made of a harder material harder than the material of the abutment member. With this construction, it is possible to reduce the cost and the weight of the abutment member.

The stopper member in the illustrated examples is an annular member including an outer circumference having a radius (such as D3) greater than a radial distance (such as D1) of the drive projection from the center of the drive shaft to the top of the drive projection. This construction makes it possible to reduce the size of the pump element (such as driving gear 15a or 18a or inner rotor 43), and hence to reduce the gear pump 1.

The stopper member, in the illustrated examples, is received in a recess formed in the abutment member which is one of the side wall member and the side plate, and the depth (such as H1) of the recess (7f) is substantially equal to the thickness (such as H2) of the stopper member. Therefore, the stopper member can be supported in a stable state, and improve the sealing performance.

The gear pump may further comprise a shaft seal member (12) disposed in a stepped recess (7f, 7g) formed around the shaft hole (7a) in the side wall member (7), and arranged to seal a circumferential clearance between the drive shaft and the inside surface of the shaft hole (7a). The stopper member (13a in FIG. 6 and FIG. 31, 13b in FIG. 29) is also received in the stepped recess so that the shaft seal member (12) is interposed or confined or pressed between the bottom of the stepped recess and the stopper member, and the stopper member is arranged to abut on the drive projection to limit the axial movement of the drive shaft. Therefore, the stopper member can protect the shaft seal member (12), improve the durability of the shaft seal member, and contribute to the reduction of the size of the side wall member (7).

In the illustrated examples, the axial width (such as D4) of the drive projection (10a, 10c, 46) is smaller than the thickness (such as D5) of the pump element (15a, 18a, 43). With this construction, the drive projection (10a, 10c, 46) does not project laterally (in the axial direction of the drive shaft) from either of the side surfaces of the pump element (15a, 18a, 43), so that the sealing performance on both sides is secured.

In the illustrated embodiments, a gear pump is of a dual type such as a tandem type, and comprises: a drive shaft (10); a first gear (15 or 18) (including a rotatable pump element); a side wall member disposed on one side of the first gear, for serving as an intermediate or partition member (7), and formed with a shaft hole (7a) receiving the drive shaft; a first side plate (14 or 17) disposed on the other side of the first gear so that the first gear is interposed axially between the side wall member (7) and the first side plate. The gear pump further comprises a second gear (18 or 15) (including a rotatable pump element) and a second side plate (17 or 14) disposed so that the second gear is interposed axially between the second side plate and the side wall member which is the intermediate member (7) disposed between the first and second gears. The gear pump further comprises a connecting section serving as means for connecting the drive shaft with each gear (15, 18) in a manner to prevent relative rotation and to allow relative axial movement between the drive shaft and the gear. The connecting section includes at least one drive recess formed in the first or second gear, and at least one drive projection projecting radially outwards from the drive shaft. The drive recess may be so shaped as to allow the drive projection of the drive shaft to move axially in the drive recess, and the drive projection is arranged to engage in the drive recess to prevent the relative rotation to drive the gear with the drive shaft, and arranged to limit the axial movement of the drive shaft relative to the gear with one of the side wall member and the first and second side plates. In the illustrated preferred embodiments, the connecting section includes first and second drive projections (10a, 10c, 46) and first and second drive recesses (15f, 18f, 43b) for the first and second gears. The thus-constructed pump can determine the axial position of the drive shaft with the drive projections for transmitting a driving torque from the drive shaft to the first and second gears, facilitate the assembly process of the pump, and reduce the size of the pump.

According to the first embodiment (FIG. 6), the second embodiment (FIG. 27), the fourth embodiment (FIG. 29), and the fifth embodiment (FIG. 31), the drive projections are arranged to limit the axial movement of the drive shaft with the intermediate member (7). This arrangement makes it possible to determine the relative axial position of the drive shaft and each gear, accurately and readily only by controlling the dimensions of intermediate member (7) accurately, as compared to the arrangement in which the drive projections are arranged to determine the relative position of the drive shaft with the first and second side plates (14, 17).

The first and second drive projections may be arranged in the following manner. The first drive projection (10a or 10c; 46) is arranged to limit the relative axial movement of the drive shaft in a first (axial) direction, and the second drive projection (10c or 10a; 46) is arranged to limit the relative axial movement of the drive shaft in a second (axial) direction opposite to the first direction. In this arrangement, each drive projection receives a force only from one side, so that the durability is improved. Thus, the drive projection or projections (10a, 10c, 46) can serve as a limiting means for limiting the axial movement of the drive shaft (10), together with the intermediate member (7) or the side plate (14, 17).

According to the first embodiment (FIG. 6), the second embodiment (FIG. 27), the fourth embodiment (FIG. 29), and the fifth embodiment (FIG. 31), the side wall or intermediate wall member (7) is interposed axially between the first and second drive projections (10a, 10c), and arranged to limit the axial movement of the drive shaft both in the first and second directions. The first drive projection is arranged to limit the axial movement of the drive shaft in the second direction by abutting against the intermediate wall member (7) directly or through an abutment means (such as 13a, 13b, 21) for limiting the axial movement, and the second drive projection is arranged to limit the axial movement of the drive shaft in the first direction opposite to the second direction by abutting against the intermediate wall member (7) directly or through an abutment means (such as 13b, 13a, 21). In the example shown in FIGS. 26A, 26B and 26C, when the first drive projection (10a) is at the limit position limiting the axial movement of the drive shaft in the second (leftward) direction (as in FIG. 26B), the first drive projection (10a) is located within the (axial) width of the first pump element (15a) of the first gear (15), and the second drive projection (10c) is located within the (axial) width of the second pump element (18a) of the second gear (18), so that there is an axial (narrower) clearance preventing abutment of the second drive projection against the second side plate (17) and an axial (wider) clearance preventing abutment of the second drive projection against the intermediate wall member (7). When the second drive projection (10c) is at the limit position limiting the axial movement of the drive shaft in the first (rightward) direction (as in FIG. 26C), the second drive projection (10c) is located within the (axial) width of the second pump element (18a) of the second gear (18), and the first drive projection (10a) is located within the (axial) width of the first pump element (15a) of the first gear (15), so that there is an axial (narrower) clearance preventing abutment of the first drive projection against the first side plate (14) and an axial (wider) clearance preventing abutment of the first drive projection against the intermediate wall member (7).

According to one of possible interpretations of the illustrated embodiments according to the present invention, the following claims are possible.

X1. A gear pump comprising: a drive shaft adapted to be connected with a drive source; a first gear driven by the drive shaft and arranged to form a first pump; a second gear driven by the drive shaft and arranged to form a second pump; an intermediate member disposed between the first and second gears, and formed with a shaft hole extending through the intermediate member and receiving the drive shaft; a first side plate so disposed that the first gear is interposed between the first side plate and the intermediate member; a second side plate so disposed that the second gear is interposed between the second side plate and the intermediate member; and a connecting section connecting the drive shaft with the first and second gears in a manner to prevent relative rotation and to allow relative axial movement, the connecting section including first and second drive recesses formed, respectively, in the first and second gears, and first and second drive projections projecting radially outwards from the drive shaft, engaging in the first and second drive recesses, respectively, and determining a relative axial position of the drive shaft relative to the first and second gears, together with at least one of the intermediate member and first and second side plates.

X2. The gear pump as recited in Claim X1, wherein the first drive projection is arranged to limit the relative axial movement of the drive shaft in a second direction, and the second drive projection is arranged to limit the relative axial movement of the drive shaft in a first direction opposite to the second direction.

X3. The gear pump as recited in Claim X1 or X2, wherein the first gear includes a rotatable first pump element mounted on the drive shaft slidably in an axial direction, and formed with the first drive recess in the form of a cutout engaging with the first drive projection of the drive shaft to allow the axial movement of the driver shaft relative to the first gear, and to prevent the relative rotation so that the drive shaft and the first pump element rotate as a unit; and the second gear includes a rotatable second pump element mounted on the drive shaft slidably in the axial direction, and formed with the second drive recess in the form of a cutout engaging with the second drive projection of the drive shaft to allow the axial movement of the drive shaft relative to the second gear, and to prevent the relative rotation so that the drive shaft and the second pump element rotate as a unit.

X4. The gear pump as recited in Claim X3, wherein an axial width of the first drive projection is smaller than a thickness of the first pump element of the first gear, and the axial width of the second drive projection is smaller than the thickness of the second pump element of the second gear.

X5. The gear pump as recited in Claim X1, wherein at least one of the first and second drive projections includes a drive pin fixedly inserted in a radial hole formed in the drive shaft.

X6. The gear pump as recited in one of Claims X1˜X5, wherein the intermediate member is arranged to determine the relative axial position of the drive shaft relative to the first and second gears by limiting axial movement of the first and second drive projections.

X7. The gear pump as recited in one of Claims X1˜X5, wherein the gear pump further comprises a first stopper member disposed axially between the intermediate member and the first side plate, and arranged to limit the axial movement of the drive shaft in one direction by abutting axially against the first drive projection, and a second stopper member disposed axially between the intermediate member and the second side plate, and arranged to limit the axial movement of the drive shaft in the other direction by abutting axially against the second drive projection.

X8. The gear pump as recited in Claim X7, wherein the first stopper member is provided between the intermediate member and the first drive projection, and the second stopper member is provided between the intermediate member and the second drive projection, and each of the first and second stopper members is made of a material harder than a material of the intermediate member.

X9. The gear pump as recited in Claim X7, wherein each of the first and second stopper members is an annular member extending radially outwards beyond the first and second drive projections.

X10. The gear pump as recited in Claim X7, wherein each of the first and second stopper members is fit in a recessed portion formed in one of the intermediate member and the side plates.

X11. The gear pump as recited in one of Claims X1˜X5, wherein the intermediate member includes a seal receiving portion opening toward one of the first and second gears, and the gear pump further comprises a shaft seal member arranged to seal a clearance between an outer circumference of the drive shaft and the through hole of the intermediate member and received in the seal receiving portion of the intermediate member, and a stopper member closing the seal receiving portion.

X12. The gear pump as claimed in one of Claims X1˜X5, wherein the intermediate member is arranged to abut directly against one of the first and second drive projections and thereby to limit the axial movement of the drive shaft.

X13. The gear pump as claimed in one of Claims X1˜X5, wherein the first and second side plates are arranged to determine the relative axial position of the drive shaft relative to the first and second gears by limiting axial movement of the first and second drive projections.

X14. The gear pump as claimed in one of Claims X1-X5, wherein the gear pump further comprises a housing including an inside cavity extending from an open end to a bottom, and having a step shoulder surface facing toward the open end of the inside cavity, and a plug member closing the open end of the inside cavity of the housing, the intermediate member is positioned axially in the inside cavity of the housing by abutment against the step shoulder surface of the housing, one of the first and second side plates is clamped axially between the bottom of the inside cavity of the housing and the intermediate member, and the other of the first and second side plates is clamped axially between the intermediate member and the plug member.

X15. A gear pump comprising: (i) a drive shaft; (ii) a rotatable pump element mounted on the drive shaft; (iii) a side wall member disposed on one side of the pump element, and formed with a shaft hole through which the drive shaft extends; (iv) a side plate disposed on the other side of the pump element, so that the pump element is interposed axially between the side wall member and the side plate; and (v) a connecting section connecting the drive shaft with the pump element in a manner to prevent relative rotation and to allow relative axial movement between the drive shaft and the pump element, the connecting section including a drive recess formed in the pump element, and a drive projection projecting radially outwards from the drive shaft, the drive recess being so shaped as to allow the drive projection of the drive shaft to move axially in the drive recess, and the drive projection being arranged to engage in the drive recess to prevent the relative rotation to drive the pump element with the drive shaft, and being arranged to limit the axial movement of the drive shaft relative to the pump element with one of the side wall member and the side plate.

X16. The gear pump as recited in Claim X15, wherein the drive recess is a cutout so shaped as to allow the drive projection of the drive shaft to move axially in the drive recess through the pump element.

This application is based on a prior Japanese Patent Application No. 2008-229191 filed on Sep. 8, 2008. The entire contents of this Japanese Patent Application are hereby incorporated by reference.

Although the invention has been described above by reference to certain embodiments of the invention, the invention is not limited to the embodiments described above. Modifications and variations of the embodiments described above will occur to those skilled in the art in light of the above teachings. The scope of the invention is defined with reference to the following claims.

Claims

1. A gear pump comprising: a drive shaft adapted to be connected with a drive source;a first gear driven by the drive shaft and arranged to form a first pump;a second gear driven by the drive shaft and arranged to form a second pump;a seal member disposed between the first and second gears, and formed with a shaft hole extending through the seal member and receiving the drive shaft, the seal member being arranged to seal one of side surfaces of the first gear and one of side surfaces of the second gear;a first side plate arranged to seal the other of the side surfaces of the first gear;a second side plate arranged to seal the other of the side surfaces of the second gear; anda connecting section connecting the drive shaft with the first and second gears in a manner to prevent relative rotation and to allow relative axial movement, the connecting section including first and second drive recesses formed, respectively, in the first and second gears, and first and second drive projections projecting radially outwards from the drive shaft, engaging in the first and second drive recesses, respectively, and determining a relative axial position of the drive shaft relative to the first and second gears, together with at least one of the seal member and first and second side plates.

2. The gear pump as claimed in claim 1, wherein the seal member is arranged to determine the relative axial position of the drive shaft relative to the first and second gears, with the first and second drive projections.

3. The gear pump as claimed in claim 2, wherein the gear pump further comprises a stopper member which is made of a material harder than a material of the seal member, and which is disposed between one of the drive projections and the seal member so that the relative axial position of the drive shaft is determined through the stopper member.

4. The gear pump as claimed in claim 3, wherein the stopper member is an annular member, and a radial dimension from a center axis of the drive shaft to an outer end of the drive projection adjacent to the stopper member is smaller than a radius of the stopper member.

5. The gear pump as claimed in claim 1, wherein the gear pump further comprises a stopper member disposed axially between an adjacent projection which is one of the drive projections and an adjacent side wall member which is one of the seal member and the first and second side plates, and the stopper member is fit in a recessed portion which is formed in the adjacent side wall member, and which has a depth substantially equal to a thickness of the stopper member.

6. The gear pump as claimed in claim 1, wherein the first drive projection is arranged to determine the relative axial position of the driver shaft on one side, and the second drive projection is arranged to determine the relative axial position on the other side.

7. The gear pump as claimed in claim 6, wherein the first and second drive projections are arranged to determine the relative axial position of the drive shaft, with the seal member.

8. The gear pump as claimed in claim 7, wherein the gear pump further comprises a stopper member which is made of a material harder than a material of the seal member, and which is disposed between one of the drive projections and the seal member so that the relative axial position of the drive shaft is determined through the stopper member.

9. The gear pump as claimed in claim 8, wherein the stopper member is an annular member, and a radial dimension from a center axis of the drive shaft to an outer end of the drive projection adjacent to the stopper member is smaller than a radius of the stopper member.

10. The gear pump as claimed in claim 1, wherein the seal member includes a seal receiving portion opening toward one of the first and second gears, and the gear pump further comprises a shaft sealing element arranged to seal a clearance between an outer circumference of the drive shaft and the through hole of the seal member and received in the seal receiving portion of the seal member, and a stopper member closing the seal receiving portion, the seal member and one of the drive projections being arranged to determine the relative axial position of the drive shaft through the stopper member.

11. The gear pump as claimed in claim 1, wherein an axial width of the first drive projection is smaller than a thickness of the first gear, and the axial width of the second drive projection is smaller than the thickness of the second gear.

12. A gear pump comprising: a drive shaft adapted to be connected with a drive source;a first gear driven by the drive shaft and arranged to form a first pump;a first pump chamber in which the first gear is received;a second gear driven by the drive shaft and arranged to form a second pump;a second pump chamber in which the second gear is received;a partition member arranged to separate the first and second pump chambers, formed with a shaft hole extending through the partition member and receiving the drive shaft, and disposed axially between one of side surfaces of the first gear and one of side surfaces of the second gear;a first side plate arranged to confront the other of the side surfaces of the first gear;a second side plate arranged to confront the other of the side surfaces of the second gear; anda connecting section connecting the drive shaft with the first and second gears in a manner to prevent relative rotation and to allow relative axial movement, the connecting section including a drive pin which is provided in the drive shaft and which extends radially outwards from the drive shaft, and a recess which is formed in one of the first and second gears, and which is engaged with the drive pin, the drive pin forming a limiting means for limiting the axial movement of the drive shaft, together with one of the partition member and the side plates.

13. The gear pump as claimed in claim 12, wherein the limiting means is provided between the drive pin and the partition member.

14. The gear pump as claimed in claim 13, wherein the gear pump further comprises a stopper member which is made of a material harder than a material of the partition member, and which is disposed between the drive pin and the partition member.

15. The gear pump as claimed in claim 14, wherein the stopper member is an annular member, and a radial dimension from a center axis of the drive shaft to an outer end of the drive pin is smaller than a radius of the stopper member.

16. The gear pump as claimed in claim 15, wherein the partition member is formed with a recessed portion receiving the stopper member and having a depth substantially equal to a thickness of the stopper member.

17. The gear pump as claimed in claim 12, wherein the drive pin includes a first drive pin to drive the first gear and a second drive pin to drive the second gear, the first drive pin is arranged to limit the relative axial movement of the drive shaft in a second direction, and the second drive pin is arranged to limit the relative axial movement of the drive shaft in a first direction opposite to the second direction.

18. The gear pump as claimed in claim 17, wherein the limiting means is formed by the first and second drive pins and the partition member.

19. The gear pump as claimed in claim 18, wherein the gear pump further comprises a stopper member which is made of a material harder than a material of the partition member, and which is disposed between one of the drive pins and the partition member.

20. The gear pump as claimed in claim 19, wherein a radial dimension from a center axis of the drive shaft to an outer end of the drive pin is smaller than a radius of the stopper member.

21. The gear pump as claimed in claim 12, wherein the partition member includes a seal receiving portion opening toward one of the first and second gears, and the gear pump further comprises a shaft sealing element arranged to seal a clearance between an outer circumference of the drive shaft and the through hole of the partition member and received in the seal receiving portion of the partition member, and a stopper member closing the seal receiving portion, the partition member and the drive pin being arranged to determine the relative axial position of the drive shaft through the stopper member.

22. A gear pump comprising: a drive shaft adapted to be connected with a drive source;a first gear driven by the drive shaft and arranged to form a first pump;a first pump chamber in which the first gear is received;a second gear driven by the drive shaft and arranged to form a second pump;a second pump chamber in which the second gear is received;a partition member arranged to separate the first and second pump chambers, and disposed axially between one of side surfaces of the first gear and one of side surfaces of the second gear;a first side plate arranged to confront the other of the side surfaces of the first gear;a second side plate arranged to confront the other of the side surfaces of the second gear; andfirst and second drive pins projecting radially outwards from the drive shaft and engaging, respectively, in a first drive recess formed in the first gear and a second drive recess formed in the second gear so that the first and second gears are driven, respectively, through the first and second drive pins in a manner allowing relative axial movement,the first drive pin being arranged to limit axial movement of the drive shaft in a second direction, with the first side plate or the partition member, and the second drive pin being arranged to limit the axial movement of the drive shaft in a first direction opposite to the second direction, with the second side plate or the partition member.

23. A gear pump comprising: a drive shaft;a gear driven by the drive shaft;a side wall member disposed on one side of the gear;a side plate disposed on the other side of the gear, so that the gear is interposed, and sealed so as to restrain leakage of an operating fluid, between the side wall member and the side plate; anda connecting section connecting the drive shaft with the gear in a manner to prevent relative rotation and to allow relative axial movement between the drive shaft and the gear, the connecting section including a drive projection which is provided in the drive shaft and which projects radially outwards from the drive shaft and a drive recess which is formed in the gear and which is engaged with the drive projection, an axial dimension of the drive projection being smaller than or equal to a width of the gear, the drive projection being arranged to limit the axial movement of the drive shaft relative to the gear, with one of the side wall member and the side plate.