JPH0694870B2 - A gel-rotor type hydraulic device having a fluid control passage passing through the rotor - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has a gerotor formed between a housing and a rotor, the housing having a housing, and a rotor performing an eccentric rotational motion while drawing an orbit inside the housing. The present invention relates to a gerotor type hydraulic device in which a small chamber expands and contracts due to an eccentric rotational movement of a rotor to discharge the fluid flowing into the device at high pressure. Its main application is as a pump, but it can also be used as a motor.

2. Description of the Related Art Here, a conventional gerotor type hydraulic device will be described with reference to FIGS.

The gerotor type hydraulic device includes a housing 20 and a rotor 28.

The housing 20 is configured as a unit, and includes a stator 22 (a gerotor set) that surrounds the rotor 28 in the radial direction, a wear plate 21 that contacts one of the axially flat end faces of the rotor 28, and the rotor 28. A manifold 23 and an end face cover 24 that are in contact with the other of both axial end faces.

The rotor 28 is arranged eccentrically in the rotor cavity of the stator 22 of the housing 20 and is slidable with respect to both the wear plate 21 and the manifold 23.

A plurality of gerotor chambers 29 are formed between the stator 22 and the rotor 28 as shown in FIG. The rotor 28 is eccentrically rotated while drawing a trajectory by the rotational driving force via the drive shaft 44 and the swing rod 38, and expands and contracts the gerotor small chamber 29.
As a result, pressure is generated in the gerotor small chamber 29, and between the two fluid connecting portions formed at one location of the housing 20, that is, from the inlet means (inlet) 30 to the outlet means (outlet).
Between 31 produces high pressure in the fluid.

The flow (movement) of the fluid from the housing 20 to the gerotor small chamber 29 passes through the communication passage 33 (FIG. 2) formed in the wear plate 21, and then the annular groove formed on the opposite side of the wear plate 21, that is, the annular shape. The fluid passage 34 (FIG. 3) and the annular groove formed in the rotor 28, that is, the annular fluid passage 37 (FIG. 4) communicate with each other. Here, since the rotor 28 is eccentrically rotated, the annular fluid passage 37 and the annular fluid passage 34 communicate with each other in a part of the circumferential direction, and the fluid communication with the gerotor small chamber 29 is ensured. .

Problems to be Solved by the Invention The above-mentioned gerotor type hydraulic device has the following problems.

The problem is that the communication area between the fluid passage of the housing and the fluid passage of the rotor is small. That is, since the rotor makes an eccentric rotational motion, the communication between the fluid passage of the housing and the fluid passage of the rotor occurs only in the range where both fluid passages overlap in the axial direction, and as a result, a sufficient steady flow rate is secured. Can not do it.

SUMMARY OF THE INVENTION An object of the present invention is to provide a rotating fluid pressure device including a gerotor having a fixed stator and a rotor that rotates while drawing an orbit inside the stator. Increasing the fluid passageway to and from the rotor fluid passageway. The rotation of the rotor member that rotates while drawing a trajectory generates power to the shaft member or receives input of power. This rotor has an annular liquid inflow passage on one side thereof, and has both a pressure fluid supply inlet and an outlet on the opposite side thereof. Annular grooves with star-shaped projections, or annular fluid passages, increase fluid flow through communication.

Although the present invention has a fixed stator and a rotor that rotates in an orbit, and the rotating portion of the rotor is used as an output shaft, the pressure fluid inlet in this gerotor type hydraulic device is provided on one side of the rotor member. A balancing zone groove is formed at the inner diameter and communicates with the inlet and outlet grooves on the opposite side of the rotor to provide a hydraulically balanced rotor.

Another object of the present invention is to provide a hydraulically balanced rotor.

Other objects and advantages of the present invention will be apparent from the accompanying drawings and the description thereof.

Although the present invention is described as a pump that uses only one fluid inlet and one fluid outlet, the high pressure fluid is now at the inlet only by simply reversing the fluid inlet and outlet. It will be readily understood by those skilled in the art of hydraulic equipment of this type that the hydraulic equipment of the same structure operates as a motor, if it is installed in the existing place.

The term "housing" as used in the following description and in the appended claims includes not only the main housing member, but also the pressure plate, gerotor assembly, manifold, and end cover, each of the latter. All parts are connected to the main housing member by a plurality of bolts.

Examples The features of the present invention are best illustrated in Figures 14-16. Note that FIGS. 8 to 11, FIG. 12, FIG. 13, and FIG.
Figures 19 to 20, Figures 20 and 21, Figures 22 and 23,
24 to 28, and FIGS. 29 to 34 also show a configuration including the features of the gerotor type hydraulic device of the present invention.

1 to 7 are not embodiments of the present invention, the basic structure of the gerotor type hydraulic device will be described first with reference to the drawings.

As shown in FIGS. 1 to 7, a gerotor type hydraulic system includes a main housing member 20 having a flat axial inner end surface, a wear plate 21 and a gerotor 21 which are sequentially attached to the flat inner end surface. The set 22, the manifold 23, and the end face cover 24 are included, and all of these parts are integrally fixed by a plurality of bolts 25, but each bolt is omitted in FIG. Are shown in various sectional views. But that each bolt
25 has a head portion that is pressed against the right-hand side outer end of the end face cover 24, and penetrates each member 24, 23, 22 and 21 from the head portion, and its inner end is firmly screwed to the main housing member 20. What is well understood by those skilled in the art. Reference numeral 26 is an O-ring.

The gerotor set best shown in FIGS. 1 and 4
22 is composed of an internal tooth member 27 that constitutes a stator and an external tooth member 28 that cooperates as a rotor inside the internal tooth member 27. The rotor 28 rotates about its own axis A as shown in FIG. Since this axis A is eccentric with respect to the central axis B of the stator 27 in the direction of the eccentric line C by the distance shown between each axis A and B, this rotor 28 has a trajectory around the central axis B of the stator 27. Draw and rotate. While the rotor 28 moves in this manner with respect to the stator 27,
The series of small chambers 29 and 29a form a series of small chambers between the rotor 28 and the stator 27, the volume of which constantly changes continuously. The volume of each small chamber 29 gradually increases on one side of the eccentric line C, and the volume of each small chamber gradually decreases on the opposite side. The smallest chamber 29a shown in FIG. 4 approaches the cello. The rotor 28 rotates in the direction indicated by the arrow D in FIG.
The rotor 28 has two flat axial end faces.

The inlet means (inlet) to the housing is shown at 30. The fluid outlet means (outlet) is shown at 31. The inlet means is connected in communication with a continuous annular groove or distribution passageway 32 in the main housing member 20 by means indicated only by dashed lines. The annular groove 32 opens into a large number of through holes, that is, the wear plate 21 having the communication passages 33, but the number of the communication passages 33 is not important and is sufficient to take the necessary flow rate of the fluid. . Each communication passage 33 is connected to a small-diameter annular groove formed on the opposite end surface of the wear plate 21, that is, the annular fluid passage 34 by the communication passage 33a. The annular fluid passage 34 opens into the rotor cavity towards the gerotor set 22.

The annular fluid passage 34 is ring-shaped and symmetrical, that is,
It has a uniform diameter and a uniform depth.

The inner teeth 27a of the stator 27 are provided by the cylinders 27a fitted into the respective through holes 27b formed in the inner surface of the stator over 180 ° in the circumferential direction, and at equal intervals as shown in FIG. Maintained in position. It should be understood that the end faces of each cylinder 27a are flush with the end faces of the stator 27. The rotor 28 has an open center hole 35 surrounded by an annular sealing band 36 which is not interrupted circumferentially,
An annular liquid inflow passage 37 is formed radially outside the annular sealing band 36. The axis of rotation of the swing rod 38 is designated by the letter A in FIG. The pivot axis of the orbital movement of the oscillating rod 38 with respect to the stator 27 is designated by the letter B in FIG. A straight line C connecting the points A and B is shown here as an eccentric line. The direction of movement of the rotor 28 is indicated by the arrow D in FIG.
As shown by. While rotating in this direction, the volume of each small chamber 29 on the left side of the eccentric line C gradually increases, but the volume of each small chamber 29 on the right side of the eccentric line gradually decreases as shown in FIG. Rotor 28
Serves as the main valve for this hydraulic system. The six flow passages, that is, the through holes 37a are arranged at equal intervals in the circumferential direction of the annular fluid passage 37 and linearly penetrate the rotor in a direction parallel to the axis of the rotor 28. A part of each of the flow passages 37a projects inward in the radial direction from the annular fluid passage 37 as indicated by reference numeral 37b, but the amount of projection is, for example, about 1/8 ″. In the structure, other flow passages are provided on the central axis line of the rotor 28 and around the connecting portion between the swing rod 38 and the rotor 28. Note that a sufficient mating surface between the spline and the gear is provided. There is a clearance so that fluid flow is unobstructed in this type of drive connection and the annular fluid passage 34 and the annular fluid passage 37 are in communication when the hydraulic system is activated.

The manifold 23 serves to connect the rotor valve to each chamber 29 of the gerotor. Manifold 23 is best illustrated in FIGS. 5, 5A and 6. Seven mutually parallel through holes 40 pass through the surface of the manifold 23 facing the rotor 28 and parallel to its axis. This set of through holes has a unique cross-sectional shape, as best shown in FIGS. The shape of each through hole 40 is referred to as a "double trapezoid" here.

Referring to FIG. 5, one of the through holes 40 looks like two trapezoids having substantially no central partition facing each other, and both ends thereof are not parallel but are inclined radially. . The inner side of each through hole in the radial direction is not a straight line,
It is composed of a slightly curved inward concave curve with a slightly higher apex at the center 40a. As shown in FIG. 5, the radial outside of the through hole 40 consists of two straight lines joining at the center, or, preferably, from one convex curve that bulges slightly outward in the radial direction. Composed. The dimensions of each of these openings correspond circumferentially to the opening between the two cylindrical through-holes 37a, as seen in FIG. 4, and in the radial direction the central hole and the annular fluid. The dimensions are such that there are between passages 37. When the hydraulic system is actuated, these openings 40 in turn communicate with the flow passages in rotor 28. This realizes the basic flow path switching action of the hydraulic system. As shown in FIGS. 5 and 6, the seven openings 41 formed at equal intervals on the side surface of the manifold 23 facing the gerotor are all fluid passages 41a inclined inward and downward as shown in FIG. 5A. And each fluid passage 4 described next
2 and 1 respectively connect to one of the through holes 40.
The seven slanted fluid passages 42 formed in the manifold 23 as shown by the solid line in FIG. 6 have been described immediately before with the structures related to the through holes 41, the passages 41a and the passages 40. To work together. Each of these cooperating paths is shown in dotted lines in FIG. 6 to indicate their cooperating condition. Seven inclined passages 42 extend through a portion of the manifold 23 from one side to the other. Each of the inclined passages 42 has a slight inclination angle with respect to the axis of the gerotor, and as shown in FIGS. 5 and 6, the radial dimension connecting the inclined passages with the axis is equal to each other. Have. Therefore, each of the inclined passages 42 in the manifold merges with or intersects with one of the passages 41a on the way through the manifold 23, so that each of the seven flow passages 40 has each passage 41a.
And one each of 42.

The long rigid rocker rod 38 clearly visible in FIG. 1 is shown in section in FIGS. 2 and 3. Swing rod 38
One end of is connected to the drive shaft 44 via a spline connecting portion 44b. The drive shaft 44 is shown to have a solid outer end and a hollow inner end 44a. The opposite end of the swing rod 38 is the rotor
In the open center hole 35 of 28, it is connected to the rotor via the spline connecting portion 44c. Each spline connection part at both ends is
The oscillating rod 38 is configured to be able to swirl around the respective central axes A and B while drawing an orbit, and the fluid can be continuously passed over around the respective connecting portions. In the discharge passage, an open center hole 35 of the rotor 28 which allows a flow passing around the drive connecting portion of the swing rod 38 and an open center hole 21a of the wear plate.
And a hollow inner end 44a of the drive shaft, but is finally completed by four radial discharge passages 45, 46 which are connected to the outlet 31 as shown by the chain line.

Needle bearings suitable for bearing the drive side 44 inside the main housing member 20 are located at 47 and 48. Further, as indicated by reference numerals 49 and 50, suitable shaft sealing means are provided at the portion where the drive shaft 44 projects outward from the main housing member 20.

The gerotor type hydraulic device has been described as a power generation pump utilizing the drive shaft 44. This pump has an inlet
The low-pressure fluid is sucked from 30 and the high-pressure fluid is discharged from the outlet 31. If the inflow port 30 and the outflow port 31 are used in reverse as described above, this hydraulic device operates as a motor for generating power to the drive shaft 44.

The operation of the gerotor hydraulic device as a pump will be described below. The power is input to the left protruding end of the drive shaft 44 when viewed in FIG. As a result, the drive shaft 44, the swing rod 38,
As the rotor 28 rotates, the rotor turns in a trajectory with respect to the stator 27. As a result, the volume of each small chamber 29 on the left side of the eccentric line C in FIG. 4 gradually increases, so that suction force is generated at the inflow port 30. Since the volumes of the small chambers 29 on the right side of the eccentric line C gradually decrease at the same time, the outlet 31
High-pressure fluid is discharged from the. The fluid sucked from the inflow port 30 reaches the annular fluid passage 34 through the annular groove 32 and each passage 33a, and then the rotor 28, the annular fluid passage 37, and the cylindrical through hole 37.
a and trapezoidal openings of the manifold 23,
That is, it passes from the flow passage 40 through the manifold passages 41a and 42, then reaches the rotor through the manifold openings 41, and is introduced into the gradually increasing small chambers 29. Each of the other small chambers 29 is discharged to the open center hole 35 of the rotor through each of the other openings 41, the other passages 42 and 41a, and the other double trapezoidal opening of the manifold, that is, the flow path 40. The fluid then cools and lubricates it while flowing around the play in the drive connection of the oscillating rod 38 and rotor 28, after which the central hole 21 of the wear plate 21
From a, it passes through the hollow portion 44a of the drive shaft 44, and finally passes through the radial passages 45 and 46 and is discharged from the outlet 31.

Next, a characteristic configuration of the present invention will be described. The characteristic construction of the present invention is best shown in FIGS. 14 and 16. The star-shaped annular fluid passage 34b is shaped by the area through which each annular fluid passage 37 of the rotor 28 traverses while the rotor 28 rotates. That is, when a point on the outer circumference of the annular fluid passage 37 moves due to the rotation of the rotor 28, the point draws a constant locus on the end surface of the wear plate 21. This orbit defines the star-shaped contour of the annular fluid passage 34b. The star-shaped annular fluid passage 34b has a variable diameter and depth, and has a maximum width and a maximum depth at each protruding point of the annular fluid passage 34b. Each passage
33a communicates with the annular fluid passage 34b at each projecting point of the star-shaped protruding annular fluid passage 34b.

When the star-shaped annular fluid passage 34b is incorporated into the rotary fluid pressure gerotor apparatus, the fluid communication area between the annular fluid passages 34b and 37 is larger than that in the case of the simple annular ring groove 34 (FIG. 3). As a result, the resistance to the flow of fluid becomes smaller. Other passages in the gerotor apparatus may also be, for example, annular fluid passages.
Note that things like 37 can also benefit from the star-shaped projections.

Also, FIG. 20 (reference numeral 34), FIG. 22 and FIG. 23 (reference numeral 34,1
06), as shown in FIG. 25 (reference numeral 119), the annular fluid passages 34, 10
By making the stars 6119 in the shape of a star, the flow resistance of the fluid can be reduced.

A gerotor type hydraulic system according to the present invention is illustrated in FIGS. FIG. 8 is a central longitudinal sectional view of a gerotor type hydraulic device, and bearings and shaft sealing devices similar to those shown in FIG. 1 are omitted for simplicity of the drawing.

The wear plate 61, the gerotor set 62, the manifold 63, and the end cover 64 fixed to the main housing member 60 are all firmly and integrally fastened by a plurality of bolts 65, each of which is shown in FIG. Thus, it extends from the right-hand end of the device and is firmly screwed into the threaded hole in the main housing member 60. The main housing member 60 has an inlet 66 which is continuous with an annular chamber 68 through its lateral hole 67. The annular chamber 68 communicates with a number of radial through holes 69 which are introduced into the hollow portion 70a of the drive shaft 70 which is rotatably mounted in the main housing member 60. The long and strong rocking rod 71 has a spline connecting portion 71a with the drive shaft 70 at one end thereof, and has another spline connecting portion 71b for connecting with a rotor member of the gerotor set 62 at the other end thereof. Each of these spline connections 71
a and 71b, the swing rod 71 can rotate freely, and at the same time, the swing rod 7
The swing rod 71 is formed so as to be able to follow a turning operation that draws the rotor trajectory inside the stator due to the rotation of 1.

The circular open center hole 61a of the wear plate 61 has a size sufficient to allow the required movement of the swing rod 71 and at the same time forms a part of the passage for the fluid to be sucked.

Six pairs of intake fluid passages 82 and flow passages passing through the rotor 72
83 connects the central hole 61a of the wear plate 61 to the annular fluid passage 84. The annular fluid passage 84 is open towards the manifold 63.

FIG. 17 is similar to the device shown in FIG. In the device of FIG. 17, one end of the flow passage 83 is in the area of the spline drive connection 71b. This is to serve to cool and lubricate the connecting portion 71b. In addition,
The manifold plate 23A connects the through holes 40 and 41 to each other, and therefore has seven arcuate slots 78A (19th slot) formed in the end surface thereof.
Figure).

Inlet 66A and inlet passage 67A have a larger diameter than in FIG. A large number of radial through holes 69A and 69B arranged in two rows that are staggered from each other are formed in the drive shaft 70. 18th
See figure. With such a combination, the inflow fluid can be introduced into the area around the rocking rod without obstruction without the need for a continuous annular chamber 68 as shown in FIG.

Inclined passage 78 for connecting each pair of through holes 40, 41 respectively
Instead of using, the manifold plate 23A has a slot 78A formed in its end face remote from the rotor. See FIG. 19. The open side of each slot 78A is closed by an end face cover plate. See Figure 17.

Gerotor 62 is best illustrated in FIG. Gerotor 62 comprises a combination of stator 62a and rotor 72. The stator 62a has a large number of teeth extending inward.
Each of the teeth can be partially formed by directly machining the stator, and can also be formed by the six cylindrical members, that is, the cylinders 62b, which are partially fitted into the large number of cylindrical through holes 62c. It is formed. Each through hole 62c is a cylinder
The members 62b are firmly held at the positions shown in FIG. 9 because they extend inward to a distance larger than the radius of 62b. The rotor 72 has a number of teeth extending outward as shown.
With 72a. The teeth co-operate with the inwardly extending stator teeth 62b. The number of teeth is one less than the number of teeth of the above-described stator 62a extending inward.

The rotor 72 has a central axis E that is eccentric to the central axis F of the stator 62a. Here, a straight line G connecting each point E and F
Is called the eccentric line. The rotor 72 has a generally annular ring groove forming a portion of the intake fluid passage, i.e., an annular fluid passage 84.
Is drilled on its end face. The annular fluid passage 84 is arranged concentrically around the axis E. A circular slot 74 formed concentrically inside the annular fluid passage 84 constitutes a passage for discharging fluid from the rotary fluid pressure device.

With reference now to FIGS. 9, 10 and 11, FIG. 11 shows the end face of the manifold 62 facing the gerotor structure 62. A discharge hole 75 communicating with the circular discharge groove hole 74 of the rotor 72 penetrates through the center thereof. Seven through holes 76 communicating with the rotor 72 are opened on the concentric circle, and further seven openings 77 are opened along the concentric circle on the outer side. Each of these openings 77
As shown in FIG. 9, its radial position is determined so that it can communicate with the expanding and contracting small chambers 80 formed between the rotor 72 and the stator 62a.

FIG. 10 shows the end face of the manifold 63 facing the end face cover 64. According to this drawing, each through hole 76 is a slanted passage 7
It can be seen that each of them is connected to one of the through holes 77 by 8, 79. Each pair of inclined passages 78, 79 are connected at both open ends 79a.

The cooperative relationship of these parts is shown by a chain line 81 in FIG. According to this drawing, one of the openings 77 is in a position cooperating with the small chamber 80a at the top end of FIG. 9 and is in a relatively distant position via the inclined passages 78 and 79 shown schematically here. It cooperates with one through hole 76.
The separated distances are around the circle where each through hole 76 is arranged, and are separated by about 2.5 pitches of each through hole 76. Next, each radial outer opening of the annular fluid passage 84
We will see how 84a cooperates with each through-hole 76. Each of the six openings 84a has a radially outermost portion 84b extending substantially in the circumferential direction, and an intermediate portion 84c inclined inward in the radial direction and the circumferential direction at both ends thereof.
And a radially innermost partition portion 84d extending in the circumferential direction from one end thereof. Although the cross section of each through hole 76 is referred to herein as a double trapezoid, the cross section of the opposite half is generally trapezoidal with its wide side edges open towards each other. Turning now to FIG. 9, when the smallest chamber 80a at its top is in communication with its associated through hole 77,
The other end 76, shown in phantom, connecting through each inclined passage 78, 79 of this connection makes it clear how the discharge fluid associated with the smallest chamber 80a is blocked before the inflow fluid is transferred from the through hole 76. Shows. Minimum chamber 80a at the moment of shutting off
Since the fluid is confined in the minimum chamber 80a, the inlet 66
A pressure higher than the pressure flowing in from is generated. This high pressure causes the rotor 72 to have cylindrical members 62b on opposite sides of the axis.
Is more fully sealed against. The high pressure in the minimum chamber 80a also provides oil to the rolling parts of the rotor in the vicinity of the upper small chambers shown in FIG. 9, so that the rotor floats on a thin film of hydrodynamic oil, resulting in higher efficiency. Mechanical output is obtained. It can also be seen that the shape of each portion 84a of the annular fluid passage 84 substantially coincides with the radially outer edge of the double trapezoidal through hole 76.

A counter ring groove 86 is formed in the rotor 62a at the end surface opposite to the annular fluid passage 84. The counterbalancing ring groove 86 is a circular groove hole on the opposite side through a narrow flow passage 87 penetrating the rotor.
Connected to 74. Therefore, the oil pressures on both end surfaces of the rotor 72 are balanced by the balance ring groove 86.

Now let's clarify how this hydraulic system, as shown in Figures 8-11, works. When power is input to the drive shaft 70, the rotor 72 rotates inside the stator 62a in the direction of the arrow shown in FIG. Inflow fluid is inlet 66
To the respective passages 67, 68, and then the hollow portion 7 of the drive shaft 70.
After passing through 0a, it passes through the center hole 61a of the wear plate. The flow from there passes through each fluid passage 82 and flow passage 83 to an annular fluid passage 84 which opens towards the manifold 63. Then, the flow passes through the inclined passages 78 and 79 of the manifold 63 and reaches from the inlet of each through hole 76 on one side of the eccentric line G to each of the other openings 77, which are between the rotor and the stator. It communicates with one of each small room 80. Meanwhile, one of the small chambers 80 on the opposite side of the eccentric line G communicates with the corresponding through hole 76, so that the fluid discharged from the small chamber 80 flows from the manifold 63 through the discharge passages 74, 75 to the outlet 85. Is discharged.

FIG. 12 shows a modification of the right side portion of the gerotor type hydraulic device of FIG. In the figure, the first
The same components as those shown in the figures are designated by the same reference numerals. In FIG. 12, the pressure plate 90 inserted in the recess formed in the end face cover 240 is added. The end surface cover 240 is pressed to the left when viewed in FIG. 12 by the pressure acting on the passage 91 connected to the discharge passage 45 and the passage 92 connected to the inflow port 30. Since each passage 91 and 92 has a ball check valve 93 adjacent to the pressure applying plate 90, the pressure applying plate 90
Is always pressed towards the manifold 23 and gerotor set 22. This creates a pressure towards the gerotor assembly. Such pressure acts between the two parts 22 and 23 which engage and rub against each other to reduce the wear of these parts 22,23.

FIG. 13 shows another modified example of the gerotor type hydraulic apparatus of FIG. The feature added here is that in order to apply an initial pressure, a pressure application communication ring 95 that extends inward to the left when viewed in FIG. The point is that a ring-shaped wave spring 97 is press-fitted between the ring and the step portion 96. The corrugated spring is made of, for example, a ring-shaped metal spring having an uneven surface that wobbles back and forth from a generally common plane when walking along a circle. Leakage between the parts is prevented by the sealing ring 98. The pin connection 99 shown in FIG. 13 is generally an axial extension of each spline 440b connecting the rocker rod 380 and the rotor of the gerotor set 22. This pin fits snugly between each spline 440b as well as the communication ring
Extend into a suitable axial hole 99a drilled in a portion of 95. This pin connection is somewhat loose in order to allow the pivotal connection of the rotor to be used as a means for adjusting the opening / closing distance of the connection shown by the dashed line in FIG.

FIG. 20 shows a hydraulic system having symmetrical passages. The internal flow passage in this device has a series of through holes 100 formed in the manifold plate 23B instead of passing through the open center hole 35 of the rotor.
After being folded back through the sheet, it is discharged from the gerotor apparatus through the outlet 101.

Each through hole 100 penetrates the manifold plate 23B symmetrically with respect to the central axis of the gerotor apparatus. The oscillating rod 38 realizes some physical contact with the manifold plate 23B at the center of the circle defined by each through hole 100. See FIG. 21.

Since the pressure and volume of the moving fluid fluctuate inside the gerotor apparatus, the swing rod-rotor drive connecting portion 44C
And a constant reciprocating fluid flow constantly over the entire central cavity 102 of the gerotor apparatus. This fluid acts to lubricate and remove contaminants from the gerotor device.

FIG. 22 is a similar sectional view showing a hydraulic device having a check valve. In this reverse-flow hydraulic device, the outer ring groove 103 on one side of the rotor 28A is connected to the open center hole 35 of the rotor via an inclined flow passage 104. Outer ring groove 103
A star-shaped annular groove, or annular fluid passageway 34, communicating with the fluid passageway connects the fluid passageway to one of the fluid ports 30. The other annular fluid passage is the second ring groove 105. This second ring groove 1
The other star-shaped annular groove communicating with 05, that is, the star-shaped annular fluid passage 106 connects the other fluid passage to the fluid inlet / outlet 107.

This star-shaped annular fluid passage 106 is an inner opening of the manifold plate 23C.
Formed on the end face of the manifold plate between 40 and the outer opening 41. See FIG. 23. (The openings 40 and 41 are connected to each other on the opposite side of the manifold plate 23C by a series of communication passages 108). A series of through holes 109 penetrating the manifold plate 23C from any position of the star-shaped annular fluid passage 106 and also penetrating the passage closing plate 110 are connected to the recessed portion 111 of the end face cover. One of the fluid inlet / outlet ports 107 is connected to the recessed portion 111.

The open center hole 35 of the rotor and the second ring groove 105 selectively communicate with each opening 40 in the manifold to switch the flow path during operation of the gerotor apparatus.

FIG. 24 shows a hydraulic device of a type in which a fluid inlet / outlet is directly connected to a manifold plate. In this device, the communication of the fluid inlet and outlet and the flow path switching action are realized between the end surface of the rotor and the manifold plate 23D.

In this device, the fluid inlet / outlet 112 is provided with a ring groove 113 bored in the inner surface of the end plate 115, a closing plate 116, intermediate plates 117 and 118, and a series of through holes 114 that linearly penetrate through the manifold plate 23D. A star communication annular groove, ie, a star communication annular fluid passageway 119. The annular groove 119 communicates with the annular groove 37b of the rotor. The fluid inlet / outlet 120 is connected to a series of through holes 122 penetrating the intermediate plates 117 and 118 and the manifold plate 23D through the through holes 121 of the closing plate 116. Series of through holes 122
Communicates with the open center hole 35 of the rotor.

The annular groove 37b and the passage 37A bring about a hydraulic balance of the rotor with respect to the fluid pressure in the annular groove 37. Open center hole of rotor
The other end of 35 provides hydraulic equilibrium for the fluid passage in the open center hole.

The manifold plate has a series of openings 40 and 41. A series of openings 40 extend through the manifold plate. The through-hole 127 connecting to the opening 40 is the opening 4 penetrating the manifold plate.
It is an extension of 0. The openings 40 and the through holes 127 of each pair are connected to each other through a series of communication passages 108 formed in the intermediate plate 117.

In this device, the rotor annular groove 37 and the open center hole 35 selectively communicate with the manifold opening 40 to switch the flow of fluid to the gerotor compartment.

The actual outlet / inlet passage in the manifold outlet / inlet hydraulic system shown in FIG. 24 is a series of plates 115 to 118 and
Determined through selective use of 23D. Each of the above plates is designed to be easily manufactured individually. See Figures 25-28. During assembly, the plates are placed in the proper sequence with respect to the other plates to form the desired outlet and inlet passages for the hydraulic system.

If necessary, a sealing element can be interposed between each plate to ensure that the leakage between adjacent passages is within the allowable amount.
In that case, the plates should be welded together after assembly to form a single unit, or some other suitable sealing means should be provided.

FIG. 29 shows a hydraulic device of the type in which fluid inlets and outlets are arranged on a large number of intermediate plates. This device is incorporated into the power steering unit 127. FIG. 35 shows a similar unit 127a having a body structure of a multilayer board. The functions of the fluid passages inside these multi-layer plate structure devices are the same. Therefore, each of these devices will be described collectively.

The fluid passages arranged as a large number of annular recessed grooves 128, 128a around the sliding members 129, 129a include a second cylinder (C2) and a second cylinder (C2).
The order is return (R2), first cylinder (C1), first intermediate (M1), second pressure (P2), first return (R1), and first pressure (P1).

Each passage of the first cylinder (C1) and the second cylinder (C2) is a double-acting type for steering not shown via each passage 150, 151 in the power steering unit 127, 127a, each fluid inlet / outlet 152, 153 and a high pressure hose not shown. Connected to both ends of the cylinder respectively.

The passages of the first pressure (P1) and the second pressure (P2) are high pressure outlets of a hydraulic pump driven by an engine (not shown) through the passages 154 and 155 of the power steering units 127 and 127a, the fluid inlet 156 and the high pressure hose. Connected to. The first return (R1) and second return (R2) passages are both power steering units 127, 127a.
Through a passage 157, a passage 158, a fluid outlet 159 and a high pressure hose to a low pressure inlet of a hydraulic pump (not shown).

The central passage 131 of the power steering unit 127, 127a communicates with the drive hole 141 of this device and the inner fluid passage. The first middle (M1) passage of the power steering unit 127, 127a is the through passage of this device.
130 communicates with the outer fluid passage.

In operation, the selective rotation of the input shaft 142 causes the sliding members 129, 129a via the pin spiral groove connection 143 within the limits of the motion allowed by the torsion spring connection 144 with the swing rod 145.
Is converted into the axial movement of the swing rod, but thereafter is converted only into the direct rotation of the swing rod.

By the axial movement of the sliding members 129, 129a, each annular recessed groove 12
8,128a is selectively connected to each passage 130,131. In the rotational position shown in FIG. 29, the passage 130 is connected to the second pressure (P2) passage via the first intermediate (M1) passage, and
The central passage 131 of the unit 127 is connected to the second cylinder passage.

The fluid from the through passage 130 passes through the through passage 132 of each plate 133, 134 and 135.
And through the communication passage 138 of the next plate 136 to the seven outer through holes 139 annularly arranged on the last plate 137.

The fluid from each outer through hole 139 of this plate 137 is annularly arranged inside the outer through hole 139 through the adjacent annular groove 37.
It communicates with some of the inner through holes 34 of the book. Each inner through hole
34 passes through each of the plates 137, 136 and 135 and communicates with the seven spiral passages 140 formed in the next plate 134.
Respectively communicate with one of the seven through holes 41. Each through hole
All 41 pass through the plates 135, 136 and 137 and finally open into the chambers of the gerotor of the units 127, 127a.

Each outer through-hole 139 is in communication with each through-hole 41 on the side connecting to each gradually increasing small chamber of the gerotor through each through-hole 34, but is connected to each gradually decreasing small chamber. The fluid from each of the through holes 41 on the side directly communicates with the central passage 131 of this unit via the drive shaft 141 at the center of the rotor.

When rotating in the opposite direction everything is reversed.

FIG. 35 shows a state in which it does not rotate and is in a neutral position.

The plates 133-137 in these hydraulic systems are joined together to form an integral unitary structure.

In the hydraulic system shown in FIG. 29, each fluid inlet / outlet, each annular recessed groove (P1, R1, P2,
M1, C1, R2 and C1) and the respective fluid passages connecting them must all be cast and / or machined.
This involves a number of time-consuming and labor-intensive manufacturing operations.

In another device shown in Figure 35, the housing of this device
A series of plates 146 forming part of 127a simplifies the structure of each fluid passage between the fluid inlet and outlet of this device and each annular recessed groove (P1, R1, P2, M1, C1, R2 and C1). . Adding a series of plates 147 also simplifies the structure of each fluid passage that connects the through-hole 130 to each chamber of the gerotor.

Each individual plate of each series of plates 146, 147 is designed to be easily individually manufactured (usually by stamping) and yet reduce the number of remaining parts in the device or simplify its construction. (For example, in the device disclosed herein,
Each fluid passage 148 and 149 in the housing 127a has a housing 127a
It is designed so that it can be manufactured by only one drilling operation that vertically drills from a flat surface. Each series of plates 146 and 147 are then joined together to form a respective unitary unitary structure.

Since each plate 147 for the fluid inlet / outlet of the gerotor and each plate 146 for the control unit body are both multi-layer grooved structures, the manufacturing cost thereof can be greatly reduced and the flexibility for various power control units can be increased. it can.

While the preferred embodiments of the present invention have been illustrated and described above, this is merely an example and should not be construed as limiting.

[Brief description of drawings]

FIG. 1 is a central longitudinal sectional view showing a conventional gerotor type hydraulic device having a basic structure. 2 is a cross-sectional view as seen from the direction indicated by the arrow line 2-2 in FIG. FIG. 3 is a cross-sectional view seen from the direction shown by the arrow line 3-3 in FIG. FIG. 4 is a cross-sectional view as seen from the direction indicated by the arrow line 4-4 in FIG. FIG. 5 is a cross-sectional view as seen from the direction indicated by the arrow line 5-5 in FIG. FIG. 5A is a partial sectional view as seen from the direction indicated by arrows 5A-5A in FIG. FIG. 6 is a cross-sectional view as seen from the direction indicated by the arrow line 6-6 in FIG. FIG. 7 is a cross-sectional view as seen from the direction indicated by the arrow line 7-7 in FIG. FIG. 8 is a central longitudinal sectional view showing a gerotor type hydraulic device in which the rotor can maintain hydraulic balance on both sides thereof. 9 and 10 and 11 are respectively the arrow lines 9 of FIG.
-9, 10-10, and 11-11 are cross-sectional views of different parts as seen from the directions shown. FIG. 12 is a partial vertical cross-sectional view of a gerotor type hydraulic device in which the right-hand side end portion of FIG. FIG. 13 is also a partial vertical cross-sectional view of a gerotor type hydraulic device in which the right-hand side end portion of FIG. 1 is modified, and particularly a vertical cross-sectional view showing a pressure applying plate attached to an end face cover. FIG. 14 is a central longitudinal sectional view of a gerotor type hydraulic apparatus according to the present invention, and particularly a central longitudinal sectional view of a structure including a star-shaped annular fluid passage. FIG. 15 is a cross-sectional view of the portion seen from the direction indicated by the arrow line 15-15 in FIG. FIG. 16 is a transverse cross-sectional view of the portion seen from the direction indicated by the arrow line 16-16 in FIG. FIG. 17 is a central longitudinal sectional view as in FIG. 8 of a hydraulic system having a shortened through hole and a different manifold passage. FIG. 18 is a transverse cross-sectional view showing the hydraulic system of FIG. 7 taken along the arrow 18-18 of FIG. FIG. 19 is a cross-sectional view showing the manifold plate of FIG. 17 taken along the arrow line 19-19 of FIG. FIG. 20 is a central vertical cross-sectional view as shown in FIG. 14 showing a hydraulic device having symmetrical fluid inlets and outlets. FIG. 21 is a cross-sectional view showing a manifold plate of the hydraulic device with a symmetrical fluid inlet / outlet shown in FIG. 20 from the direction shown by the arrow line 21-21 in FIG. 20. FIG. 22 is a central longitudinal sectional view similar to FIG. 8 showing a reverse flow switching type hydraulic device. FIG. 23 is a view of the 22nd line as seen from the direction indicated by the arrow line 23-23 in FIG.
FIG. 3 is a cross-sectional view showing a manifold plate of the reverse flow switching type hydraulic device shown in the drawing. FIG. 24 is a central longitudinal sectional view similar to FIG. 14 showing a hydraulic device in which a fluid port is directly connected to a manifold plate. Fig. 25 is the 24th view seen from the direction shown by the arrow line 25-25 in Fig. 24.
FIG. 3 is a cross-sectional view showing one end surface of the manifold plate shown in the figure. FIG. 26 is a view taken from the direction shown by the arrow line 26-26 in FIG.
FIG. 6 is an end view showing the other end surface of the manifold plate in the figure. FIG. 27 is a view taken from the direction shown by the arrow line 27-27 in FIG.
FIG. 6 is an end view showing an outer end surface of the passage blocking plate in the figure. FIG. 28 is a view taken from the direction shown by the arrow line 28-28 in FIG.
The end view which shows the inner end surface of the end plate of a figure. FIG. 29 is a central longitudinal sectional view similar to FIG. 14 showing the fluid passageway of the gerotor plate in the intermediate plate. FIG. 30 is a view taken from the direction shown by the arrow line 30-30 in FIG.
Sectional drawing which shows the cross section of the fluid inlet-outlet path of a figure. Fig. 31 is the 29th view seen from the direction shown by the arrow line 31-31 in Fig. 29.
Sectional drawing which shows the following site | part of the fluid inlet-outlet path of a figure. FIG. 32 shows the view of the arrow 29-32 in FIG.
Sectional drawing which shows the further next site | part of the fluid inlet-outlet path of the figure. FIG. 33 is a view taken from the direction shown by the arrow line 33-33 in FIG.
Sectional drawing which shows another part of the fluid inlet and outlet passage of the figure. FIG. 34 is a view taken from the direction shown by the arrow line 34-34 in FIG.
Sectional drawing which shows the further next site | part of the fluid inlet-outlet path of the figure. FIG. 35 is a central longitudinal sectional view showing another unit similar to the power steering unit shown in FIG. 29. FIG. 36 is a view of the line 35-35 seen from the direction shown by the arrow line 36-36 in FIG.
The end view which shows one sheet of the multilayer board of the figure. FIG. 37 is a view of the line 35-35 seen from the direction shown by the arrow line 37-37 in FIG.
The end view which shows another one sheet of the multilayer board of the figure. FIG. 38 is a view of the line 35-35 seen from the direction shown by the arrow line 38-38 in FIG.
FIG. 6 is an end view showing still another one of the multilayer plates shown in the figure. FIG. 39 is a view of the line 35-35 seen from the direction indicated by the arrow line 39-39 in FIG.
FIG. 11 is an end view showing still another one of the multilayer plates shown in the figure. 20; 60: Main housing member 24; 64: End face cover 28; 72: Rotor 29; 80: Small chamber 30; 66: Fluid inlet 31; 85: Fluid outlet 34b …… Housing fluid passage 37 …… Rotor fluid passage 37a ; 83; 87; 104 ...... Passage passage

Continuation of front page (56) Reference JP-A-57-124091 (JP, A) JP-A-54-81435 (JP, A) JP-A-48-51303 (JP, A) JP-A-50-38823 (JP , A) JP-B-45-4466 (JP, B1) JP-B-53-32525 (JP, B2)

Claims (14)

[Claims] 1. A housing (20) and a rotor (28),
The rotor (28) rotates while drawing an orbit with respect to the housing (20), and during one rotation, the fluid passage (34b) of the housing (20) and the fluid passage (37) of the rotor (28). In a gerotor type hydraulic device configured to always move fluid between the housing, one of the fluid passage (34b) of the housing (20) and the fluid passage (37) of the rotor (28) is the housing. The fluid passage (34b) of (20) or the fluid passage (37) of the rotor (28) is substantially formed in a shape described by a certain point, and the shape is the rotor (28). ) Substantially corresponds to the rotational movement while orbiting with respect to the housing (20), and the fluid passage conforming to the shape is a ring groove whose width increases and decreases periodically in the circumferential direction, The passage (34
b, 37) A gerotor type hydraulic system designed to increase the fluid passage between them. 2. A gerotor type hydraulic system according to claim 1, wherein said ring groove is star-shaped and each tip of said ring groove faces toward a small chamber of said gerotor apparatus. 3. Always 100 during one revolution of the rotor (28) between the fluid passage (34b) on the face of the housing (20) and the fluid passage (37) on the opposite face of the rotor (28). % Fluid communication is performed, and the fluid passage (34b) of the housing (20) or the fluid passage (3 of the rotor (28).
7) one of the fluid passageways (3
4b) or some point of the other of the fluid passages (37) of the rotor (28) is substantially formed in a shape drawn in a surface corresponding to the one fluid passage, the shape being the rotor (28). 28), which substantially corresponds to the movement of the fluid passages (34b, 37) formed as described above, so as to increase the communication between the fluid passages (34b, 37). The gerotor type hydraulic device according to claim 1. 4. A gerotor type hydraulic system according to claim 3, wherein said one fluid passage (34b, 37) is formed substantially in a star shape. 5. The movement of the fluid constantly occurring between the fluid passage (34b) of the housing (20) and the fluid passage (37) of the rotor (28) during one rotation of the rotor (28) is caused by the movement of the housing. A first fluid passageway (34b) on the face of (20) and a single fluid passageway (37) on the opposite face of said rotor (28). Section gerotor type hydraulic system. 6. A fluid passageway (34b) for the housing (20).
Is a ring groove fluid passageway (34) on the surface of the housing (20).
b), wherein the fluid passage (37) of the rotor (28) is a generally circular ring groove (37) on the opposite surface of the rotor (28). Hydraulic system. 7. A housing (20) and a rotor (28),
The rotor (28) rotates while drawing an orbit with respect to the housing (20), and the fluid passage (34b) of the housing (20) and the ring-shaped single fluid of the rotor (28) during one rotation of the rotor (28). The fluid is constantly moved between the passages (37), and the valve passages (40, 41, 42) of the rotor (28) provided on one side of the rotor (28) are enlarged or reduced. A gerotor type hydraulic device having a valve malhold (23) for selectively communicating with a gerotor small chamber, wherein the fluid passage (37) of the rotor (28) is extended to the fluid passage (34b) of the housing (20). One of which is formed in a shape substantially corresponding to the rotational movement of the rotor (28) while orbiting with respect to the housing (20), and the fluid passage corresponding to the shape is formed in the circumferential direction. Cyclically wide Reduced to a ring groove, said passage (34b,
37) A gerotor-type hydraulic system adapted to increase fluid communication between. 8. A gerotor type hydraulic system according to claim 7, wherein said ring groove is star-shaped and each tip of said ring groove faces toward a small chamber of said gerotor apparatus. 9. The rotor (72) comprises a pair of flow passages (83, 87) through which 100% of the fluid flows, and one of the two flat axial end faces of the rotor (72). (72) has a hole (74) that extends substantially on the axis of the rotor (72) to the middle of (72), and from the other of the two flat axial end faces of the rotor (72) to the hole (74). One (87) of the pair of flow passages extends, the other (83) of the pair of flow passages of the rotor (72) is in the rotor (72), and the pair of flow passages further comprises: A means for connecting one of the passages (87) to one of the inlet or the outlet, a means for connecting the other of the pair of passages to the other of the inlet (66) or the outlet (85), In the housing for selectively connecting the pair of flow passages (83, 87) to the chamber of the gerotor when a hydraulic system is activated. Single and a placed unit to the surface, gerotor type hydraulic device of paragraph 7 claims chromatography data (72). 10. The other of the pair of flow passages (83) is on the axis of the rotor (72) from the other of the two flat axial end faces of the rotor (72) to the middle of the rotor (72). 10. A second hole (82) extending substantially through, the second hole (82) being different than the hole (74) of the rotor (72). Gerotor type hydraulic system. 11. The other of the flow passages (83) extends through the rotor (72) and has one end thereof substantially extending from the other of the two flat end faces of the rotor on the axis of the rotor. 10. The gerotor type hydraulic apparatus according to claim 9, wherein there is an extending hole (82), and the second hole (82) is different from the hole (74) of the rotor (72). 12. A pair of flow passages, wherein one of the rotors (72) extends straight from one surface of the rotor (72) to the other surface and the other extends in the rotor (72). 83,8
7), and one of the pair of flow passages (87)
To one of the inlet (66) or the outlet (85) and the means (1) on one side of the rotor (72) to connect the other (83) of the pair of flow passages to the inlet (66). ) Or means on the other side of the rotor (72) to connect to the other of the outlets (85) and the pair of flow passages (83, 87) when the hydraulic system is activated. Means disposed in the housing on a single face of the rotor (72) for selective connection to a small chamber of 100% of the fluid from the flow passage (83,87). 8. A gerotor type hydraulic system according to claim 7 adapted to pass through said means within said housing. 13. The method according to claim 12, wherein one of the pair of flow passages surrounds the other of the pair of flow passages.
Section gerotor type hydraulic system. 14. The twelfth aspect of the present invention, wherein the other of the pair of flow passages surrounds one of the pair of flow passages.
Section gerotor type hydraulic system.