JPH0742678A - Gyrotor type hydraulic system with fluid control path penetrated through rotor - Google Patents

Abstract

PURPOSE: To keep the balance of oil pressure acting on an end surface of a rotor, to reduce the abrasion of a connecting part between the rotor and a vibration rod connected to this rotor, and to cool the connecting part in a gerotor-type hydraulic device comprising a housing, the rotor having two flat axial end surfaces, a plurality of gerotor cells, an inlet and an outlet. CONSTITUTION: A gerotor-type hydraulic device comprises a main housing member 60, an abrasion plate 61, a gerotor set 62, a manifold 63 and a cover 64. The main housing member 60 comprises an inlet 66 continuously connected to an annular chamber 68. The annular chamber 68 is communicated to a radial through hole 69, and this through hole 69 is connected to a hollow part 70a of a driving shaft 70. A central opening 61a of the abrasion plate 61 forms a part of a fluid passageway. Six pairs of fluid passageways 82, 83 penetrating through a rotor 72 connect the central hole 61a to an annular fluid passageway 84. This annular fluid passageway 84 is opened toward the manifold 63.

Description

Detailed Description of the Invention

[0001]

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

[0002]

2. Description of the Related Art A conventional gerotor type hydraulic system will now be described with reference to FIGS.

The gerotor type hydraulic system 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, and a wear plate 21 that contacts one of the axially flat end surfaces of the rotor 28. , And a manifold 23 and an end face cover 24 that are in contact with the other of the two axial end faces of the rotor 28.

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 small chambers 29 are formed between the stator 22 and the rotor 28 as shown in FIG. The rotor 28 eccentrically rotates while drawing an orbit 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,
A high pressure is generated in the fluid between two fluid connections formed at one location of the housing 20, that is, between the inlet means (inlet) 30 and the outlet means (outlet) 31.

The flow of fluid from the housing 20 to the gerotor chamber 29 is a communication passage 33 formed in the wear plate 21.
(FIG. 2), the annular groove formed on the opposite side of the wear plate 21, that is, the annular fluid passage 34 (FIG. 3), and the rotor 2
8 is an annular groove, that is, an annular fluid passage 37.
This is done by commutating (Fig. 4).
Here, since the rotor 28 is eccentrically rotating, the annular fluid passage 37 and the annular fluid passage 34 communicate with each other in a part of the circumferential direction, and fluid communication with the gerotor small chamber 29 is ensured. .

[0007]

The above-mentioned gerotor type hydraulic system has the following problems.

First, there is a problem 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 movement, 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.

Secondly, there is a problem that the temperature of the gerotor type hydraulic device is increased by the flow of the fluid in the device. Particularly, in the conventional type in which the fluid reciprocates in the rotor, the amount of heat of the fluid is easily conducted to the device, and as a result, the temperature of the device, particularly the rotor, is raised. There is also a problem that the device, particularly the rotor, expands due to the amount of heat of the fluid.

Thirdly, since the fluid passage of the gerotor type hydraulic device is complicated, it is difficult to form such a fluid passage in the housing.

[0011]

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rotary fluid pressure device including a gerotor having a fixed stator and a rotor that rotates while orbiting inside the stator. 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, enhance communication fluid flow. Although the second embodiment also has a fixed stator and a rotor that rotates in an orbit, and the rotating portion of the rotor is used as the output shaft, the pressure fluid inlet in this embodiment has an inner diameter on one side of the rotor member. A counterbalancing groove is provided which 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 pressure-applying communication ring that is biased with a wave spring for initial contact and a drive pin connected between the rotor and the rotor.

Another object of the present invention is to provide a pressure application plate in the end cover of the housing to maintain a balance of pressures that provides the force exerted towards the manifold and gerotor. is there.

The present invention reduces the number of manufacturing operations required to manufacture a hydraulic system. The hydraulic system manufactured according to the present invention is simple, reliable, and highly efficient.

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

Yet another object is to cool the swing rod drive connection to reduce wear on the connection.

Another object of the present invention is to increase communication fluid flow.

Other objects and advantages of the present invention will be apparent from the accompanying drawings and the description thereof. The essential features of the invention are set forth in the appended claims.

Although the present invention has been described as a pump that uses only one fluid inlet and one fluid outlet, high pressure fluids have now been replaced by simply reversing the fluid inlet and outlet. It will be readily understood by those skilled in the art of this type of hydraulic system that the hydraulic system of the same structure operates as a motor if it is introduced at the place where it was the inlet.

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

[0021]

1 to 7, a first embodiment of the present invention is a main housing member 20 having a flat axial inner end face, and wear plates sequentially attached to the flat inner end face. 21, a gerotor set 22, a manifold 23, and an end face cover 24, all of which are integrally fixed by a plurality of bolts 25, each of which is omitted in FIG. Are shown in various other cross-sectional views. However, each of the bolts 25 has a head portion that is pressed against the right-hand side outer end of the end surface cover 24, and the members 24, 2 are attached from the head portion.
It is well understood by those skilled in the art that 3,22 and 21 are threaded through and their inner ends are securely screwed to the main housing member 20. Reference numeral 26 is an O-ring.

The gerotor set 22 best shown in FIGS. 1 and 4 includes an internal tooth member 27 which constitutes a stator,
It is composed of 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 C by the distance shown between the axes A and B,
The rotor 28 rotates in a trajectory around the central axis B of the stator 27. Rotor 28 with respect to stator 27
During this movement, the series of compartments 29 and 29a form a series of compartments 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 small chamber 29a having the minimum volume shown in FIG. 4 approaches zero. The rotor 28 rotates in the direction indicated by 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 a continuous annular groove in the main housing member 20 by means shown only by dashed lines.
That is, it is connected so as to communicate with the distribution passage 32.
The annular groove 32 has a large number of through holes, that is, the communication passages 3.
Although open to the wear plate 21 with three, the number of communication passages 33 is not critical and is sufficient to take up the required flow rate of fluid. Each of the communication passages 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 can be ring-shaped (FIGS. 1 and 3) or star-shaped (FIGS. 14 and 16). The annular fluid passage 34 is symmetrical, that is, it has a uniform diameter and a uniform depth. In contrast, the star-shaped annular fluid passage 34b is of a shape defined 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 locus represents the annular fluid passage 34.
It makes a star-shaped outline of b. Star-shaped annular fluid passage 34
b 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 communication passage 33a is a star-shaped annular fluid passage 34b.
To the annular fluid passage 34b.

Each inner tooth 27a of the stator 27 is inserted into each through hole 27b formed on the inner surface of the stator in a circumferential direction 180.
Provided by a cylinder 27a fitted over the same angle and maintained in equidistant positions as shown in FIG. It should be understood that the end faces of each cylinder 27a are at the same level as 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 in the circumferential direction, but an annular liquid inflow passage 37 is formed radially outside the annular sealing band 36. Swing rod 3
The axis of rotation of 8 is designated by the letter A in FIG.
The orbital axis of the orbital movement of the oscillating rod 38 relative 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 as indicated by the arrow D in FIG. 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. The rotor 28 functions as a main valve for this hydraulic device. The six flow passages, that is, the through holes 37a, are
7 are arranged at equal intervals in the circumferential direction and penetrate the rotor linearly 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 shown by reference numeral 37b, but the amount of projection is about 1/8 "in one embodiment. In the structure shown in the figure, another flow passage is provided around the central axis of the rotor 28 and around the connecting portion between the swing rod 38 and the rotor 28. In addition, the meshing surface between the spline and the gear is provided. , There is sufficient 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 when the hydraulic system is activated.
Communicates with.

The manifold 23 serves to connect the rotor valve to each chamber 29 of the gerotor. Manifold 2
3 is best illustrated in FIGS. 5, 5A and 6.
Seven mutually parallel through holes 40 penetrate through the surface of the manifold 23 facing the rotor 28 in parallel with the axis thereof. 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 to each other but are inclined radially. ing. The inner side of each through hole in the radial direction is not a straight line but is composed of a concave curve that is slightly inward with a slightly higher apex at its center 40a. Figure 5
As shown in FIG. 3, the outer side of the through hole 40 in the radial direction is composed of two straight lines joined at the center thereof, or a convex curve that slightly bulges outward in the radial direction.
The dimensions of each of these openings, as seen in FIG. 4, correspond circumferentially to the opening between the two cylindrical through holes 37a and in the radial direction the central hole and the annular fluid passage 37a. The dimensions are as between. When the hydraulic system is activated, these openings 40 in turn communicate with the flow passages in the rotor 28. This realizes the basic flow path switching action of the hydraulic system. As shown in FIGS. 6 and 6, the seven openings 41 formed at equal intervals on the side surface of the manifold 23 facing the gerotor are all described below with the respective fluid passages 41a inclined inward and downward as shown in FIG. 5A. To each one of the through-holes 40 by the respective fluid passages 42. As shown by the solid line in FIG. 6, the manifold 2
Three inclined fluid passages 42 drilled in 3 cooperate with the structures associated with each through-hole 41, each passage 41a and each through-hole 40 as described immediately above. Each of these cooperating paths is shown in dotted lines in FIG. 6 to indicate their cooperating condition. Seven sloped passages 42 traverse a portion of the manifold 23 and extend 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 to the axis has an equal interval between them. . 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 through holes 40 is associated with each of the passages 41a and 42. .

The long rigid rocker rod 38 clearly visible in FIG. 1 is shown in cross section in FIGS.
One end of the swing rod 38 is connected to the drive shaft 44 by a spline connecting portion 44.
connected via b. 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 connected to the rotor at the open center hole 35 of the rotor 28 via the spline connecting portion 44c. Each of the spline connection portions at both ends allows the swing rod 38 to orbit around the central axes A and B while allowing the fluid to continuously flow over each connection portion. Is composed of. In the discharge passage, an open center hole 35 of the rotor 28 that allows a flow passing over around the drive connecting portion of the swing rod 38, an open center hole 21a of the wear plate, and a hollow inner end portion 44a of the drive shaft. Is included, but eventually the outlet 3
It is completed by four radial discharge passages 45, 46 which are connected to 1 as indicated by the chain line.

Needle bearings suitable for bearing the drive shaft 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.

This embodiment has been described as a pump utilizing a drive shaft 44 for power attachment to draw low pressure fluid from the inlet 30 and discharge high pressure fluid 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 on the drive shaft 44.

The operation of the pump of the first embodiment 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 and the swing rod 3
8. Rotor 28 rotates and rotor 27 rotates
Draw a trajectory against and turn. As a result, the volume of each small chamber 29 on the left side of the eccentric line C gradually increases, so that a suction force is generated at the inflow port 30. The volume of each small chamber 29 on the right side of the eccentric line C in FIG. 4 gradually decreases at the same time, so that high-pressure fluid is discharged from the outlet 31. The fluid sucked from the inflow port 30 reaches the annular fluid passage 34 through the annular groove 32 and the passages 33a, then passes through the rotor 28, the annular fluid passage 37, and the cylindrical through hole 37a, and further, the manifold 23 From the trapezoidal opening, or through hole 40, through the manifold passages 41a and 42, then through the manifold through holes 41 to the rotor, is introduced into the gradually increasing chambers 29. The other small chambers 29 are discharged to the open center hole 35 of the rotor through the other through holes 41, the other passages 42 and 41a, and the other double trapezoidal opening of the manifold, that is, the through holes 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 before it wears the wear plate 21.
From the central hole 21a of the drive shaft 44 through the hollow portion 44a of the drive shaft 44, and finally through the radial passages 45 and 46.
Emitted from.

If the star-shaped annular fluid passage 34b is incorporated in the rotary fluid pressure gerotor apparatus, the fluid communication area between the annular fluid passages 34b and 37 is equal to that of the ring-shaped annular groove 34 (FIG. 3). Expanded from the case, the resistance to the flow of fluid becomes smaller. It should be noted that other passageways in the gerotor apparatus, such as annular fluid passageway 37, may also benefit from the star-shaped projections.

A second embodiment of the invention is illustrated in FIGS. FIG. 8 is a central longitudinal sectional view of the second embodiment,
Bearings and shaft seals similar to those shown in FIG. 8 have been omitted to simplify the drawing.

The wear plate 61, the gerotor set 62, the manifold 63, and the end face 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. As shown in, the device extends from the right-hand end and is firmly screwed into the screw hole of the main housing member 60. The main housing member 60 has an inlet 66 which is continuously connected to the annular chamber 68 via its lateral hole 67. The annular chamber 68 communicates with a number of radial through-holes 69 leading into the hollow portion 70a of the drive shaft 70 rotatably mounted in the main housing portion 60. The long and strong swing rod 71 has a spline connecting portion 71a with the drive shaft 70 at one end, and has another spline connecting portion 71b for connecting with the rotor member of the gerotor set 62 at the other end. Each of these spline connection parts 71
a and 71b, the swing rod 71 can be freely rotated,
The oscillating rod 71 is formed so as to be able to follow the revolving motion that draws the orbit of the rotor inside the stator due to the rotation of the oscillating rod 71.

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

Six pairs of suction fluid passages 82 and flow passages 83 penetrating the rotor 72 connect 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 has the through holes 4
In order to connect 0 and 41 to each other, it has seven arcuate slots 78A (FIG. 19) formed in its end surface.

Inlet 66A and inlet passage 67A have a larger diameter than in FIG. The drive shaft 7 has a large number of radial through holes 69A and 69B arranged in two rows that are different from each other.
It is drilled at 0. See FIG. With such a combination, the inflowing 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.

Instead of using an inclined passage 78 to connect each pair of through holes 40, 41 respectively, the manifold plate 2
3A is a groove hole 7 formed in the end surface of the rotor remote from the rotor.
8A. See FIG. The open side of each slot 78A is closed by an end face cover plate. See FIG.

Gerotor 62 is best illustrated in FIG. The gerotor 62 includes a stator 62a and a rotor 72.
Combining with. 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 firmly fitted in the plurality of cylindrical through holes 62c. It is formed. Since each through hole 62c extends inward to an interval larger than the radius of the cylinder 62b, each member 62b is shown in FIG.
It is firmly held in the position shown in. The rotor 72 has a large number of teeth 72a extending outward as shown. 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 is the central axis F of the stator 62a.
Has a central axis E eccentric to. Here each point E
A straight line G connecting F and F is called an eccentric line. The rotor 72 is provided with a generally annular ring groove forming a part of the intake fluid passage, that is, an annular fluid passage 84 at its end surface. The annular fluid passage 84 is eccentrically arranged 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.

Referring now to FIGS. 9, 10 and 11,
FIG. 11 shows the end face of the manifold 62 facing the gerotor structure 62. The circular discharge slot 74 of the rotor 72 is provided at the center thereof.
A discharge hole 75 that communicates with Seven through holes 76 communicating with the rotor 72 are opened on the concentric circle, and further, seven through holes 77 are opened along the outer concentric circle. The radial positions of the through holes 77 are determined so as to communicate with the expanding and contracting small chambers 80 formed between the rotor 72 and the stator 62a as shown in FIG.

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

The cooperative relationship between these parts is shown by a chain line 81 in FIG. According to this figure, one of the openings 77 is in a position cooperating with the small chamber 80a at the top end of FIG.
One through hole 7 located at a considerable distance via 8, 79
Working with 6. The distance is about 2.5 of each through hole 76 around the circle where each through hole 76 is arranged.
They are as far apart as the pitch. It will now be seen how each radially outer opening 84a of the annular fluid passageway 84 cooperates with each communication through hole 76. Each of the six openings 84a has a radially outermost portion 84b extending substantially in the circumferential direction, an intermediate portion 84c inclined inward in the radial direction and the circumferential direction at both ends thereof, and a circumferential direction from one end thereof. It is formed by the radially innermost partition portion 84d extending. 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 of the sloped passages 78, 79 of this connection. Clearly shows how the effluent fluid associated with the smallest chamber 80a is blocked before the influent fluid is transferred from the through hole 76. Minimum chamber 80 at the moment of shutting off
Since the fluid is confined in a, a pressure higher than the pressure flowing from the inflow port 66 is generated in the minimum chamber 80a. This high pressure causes the rotor 72 to be more fully sealed to each cylindrical member 62b on the opposite side of the axis. Minimum room 80
The high pressure in a also provides oil to the rolling parts of the rotor in the vicinity of the small chambers in the upper part shown in FIG. 9, so that the rotor floats on a thin film of hydrodynamic oil, resulting in a mechanical output of higher efficiency. 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 face opposite to the annular fluid passage 84. The balance ring groove 86 is connected to the opposite circular groove hole 74 via a narrow flow passage 87 penetrating the rotor. Therefore, the hydraulic 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 FIGS. 8 to 11 works. When power is input to the drive shaft 70, the rotor 72 moves to the stator 62.
Inside a, it rotates in the direction of the arrow shown in FIG. The inflow fluid flows from the inflow port 66 into the respective passages 67 and 68, and then passes through the hollow portion 70a of the drive shaft 70 and passes through the center hole 61a of the wear plate. The flow from there reaches the annular fluid passage 84 which opens towards the manifold 63 via each fluid passage 82 and the passage passage 83. Then, the flow passes through the respective 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 through holes 77, which through holes of the rotor and the stator. It communicates with one of the small chambers 80 in between. 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 chambers 80 flows from the manifold 63 through the discharge passages 74 and 75 to the outlet 85. Is discharged.

FIG. 12 shows another embodiment of the right side portion of FIG. In the figure, the same components as those shown in FIG. 1 are indicated by the corresponding symbols. In FIG. 12, the pressure plate 90 inserted in the recess formed in the end face cover 240 is added. The pressure supplied from the passage 91 connected to the discharge passage 45 of the end face cover 240 and the passage 92 connected to the inflow port 30 pushes it to the left when viewed in FIG. Each passage 91 and 92 has a ball check valve 93 adjacent to the pressure plate 90 so that the pressure plate 90 is always urged inwardly toward both the manifold 23 and beyond and to the gerotor set 22. . This provides head pressure towards the manifold and gerotor set. Such head pressure reduces the wear between the two parts 22 and 23 which engage and rub against each other.

FIG. 13 shows another embodiment. The feature added here is that the pressure applying communication ring 95 extending inward to the left when viewed in FIG. 13 is arranged with respect to the step portion 96 of the rotor for applying the initial pressure, and the communication ring is also provided. The point is that the wave spring 97 in the shape of a ring is press-fitted between the step portion 96 and the stepped 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 coupling 99 shown in FIG. 13 is generally a swing rod 38.
0 is an axial extension of each spline 440b connecting 0 to the rotor of the gerotor set 22. The pin fits snugly between each spline 440b and extends into a suitable axial hole 99a drilled in a portion of the communication ring 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 in phantom in FIG.

FIG. 20 shows a hydraulic system having symmetrical passages. Instead of passing through the open center hole 35 of the rotor, the internal flow passage in this device is folded back through a series of through holes 100 formed in the manifold plate 23B, and then the outlet 1
It is discharged from this gerotor apparatus through 01.

Each through hole 100 penetrates through the manifold plate 23B symmetrically with respect to the central axis of the gerotor apparatus. The swing rod 38 includes the manifold plate 23B and the through holes 100.
To achieve some physical contact such that it makes physical contact at the center of the circle defined by See FIG. 21.

Since the pressure and volume of the fluid that moves inside the gerotor apparatus fluctuates, a constant reciprocating fluid is formed over the rocking rod, the drive connecting portion 44C of the rotor, and the entire central cavity 102 of the gerotor apparatus. The flow constantly flows. 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. A star-shaped annular groove, or annular fluid passage 34, that communicates with the outer ring groove 103 connects this fluid passage to one of the fluid ports 30. The other annular fluid passage is the second ring groove 105. Another star-shaped annular groove communicating with the second ring groove 105, that is, a star-shaped annular fluid passage 106 connects the other fluid passage to the other fluid inlet / outlet 107.

The star-shaped annular fluid passage 106 is formed on the end face of the manifold plate between the inner through hole 40 and the outer through hole 41 of the manifold plate 23C. See FIG. 23. (Each of the through holes 40 and 41 has a series of communication passages 108.
Are connected to each other on opposite sides of the manifold plate 23C). It passes through the manifold plate 23C from any position of the star-shaped annular fluid passage 106, and further passes through the passage closing plate 110
A series of through-holes 109 that also pass through 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 1 for switching the flow path of the gerotor apparatus during its operation.
05 selectively communicate with each through hole 40 in the manifold.

FIG. 24 shows a hydraulic device of the type in which a fluid inlet / outlet is directly connected to a manifold plate. In this device, the communication between the fluid inlet and outlet and the flow passage switching action are realized between the end surface of the rotor and the manifold plate 23D. In this device, the fluid inlet / outlet 112 includes a ring groove 113 bored in the inner surface of the end plate 115, a closing plate 116, and intermediate plates 117, 1.
All of 18 and the manifold plate 23D are connected to a star-shaped communication annular groove, that is, a star-shaped communication annular fluid passage 119 through a series of through holes 114 that linearly penetrate. Annular groove 1
19 communicates with the annular groove 37b of the rotor. Fluid port 1
Reference numeral 20 denotes each intermediate plate 1 through the through hole 121 of the closing plate 116.
It is connected to a series of through-holes 122 penetrating 17 and 118 and the manifold plate 23D. The series of through holes 122 communicate with the open center hole 35 of the rotor.

The annular groove 37b and the passage 37A are the annular groove 37.
Provides hydraulic equilibrium to the rotor for fluid pressure at. The other end of the open center hole 35 of the rotor provides hydraulic equilibrium for the fluid passages in the open center hole.

The manifold plate includes a series of openings 40 and 41 in each series.
Have. A series of openings 40 extend through the manifold plate. The through hole 127 connected to the opening 40 is an extension of the opening 40 penetrating the manifold plate. 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.

The annular groove 37 of the rotor and the open center hole 35 selectively communicate with each opening or through hole 40 for switching the flow paths during operation of this device.

The actual inlet / outlet passages in the manifold outlet / inlet hydraulic system shown in FIG. 24 are determined through the selective use of a series of successive plates 115-118 and 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 desired, a sealing element may be interposed between the plates to ensure that the leakage between adjacent passages is within an acceptable amount, in which case the plates form a single unit after assembly. It is better to weld them to each other or to take other suitable sealing means.

FIG. 29 shows a hydraulic system 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 multilayer boards. 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), a second return (R2), a first cylinder (C1), First intermediate (M1), second pressure (P
2), first return (R1) and first pressure (P1).

The first cylinder (C1) and the second cylinder (C
Each passage of 2) is connected to both ends of a double-acting cylinder for steering not shown via respective passages 150, 151 in the power steering unit 127, 127a, respective fluid inlets and outlets 152, 153 and a high pressure hose not shown. To be done. Each passage of the first pressure (P1) and the second pressure (P2) has a power steering unit 127,
It is connected to the high pressure outlet of the hydraulic pump driven by the engine (not shown) through the passages 154 and 155 of 127a, the fluid inlet 156 and the high pressure hose. Each of the first return (R1) and second return (R2) passages passes through the passage 157, passage 158, fluid outlet 159, high pressure hose of the power steering units 127, 127a, and low pressure of a hydraulic pump (not shown). Connected to the entrance.

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

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

By the movement of the sliding members 129, 129a in the axial direction, the respective annular recessed grooves 128, 128a are made into the passages 130,
Selectively connected to 131. 29, the passage 130 is connected to the second pressure (P2) passage through the first intermediate (M1) passage and the unit 12
The central passage 131 of 7 is connected to the second cylinder passage.

The fluid from the through passage 130 is supplied to each plate 133, 1
Through the through passages 132 of 34 and 135 and the communication passage 138 of the next plate 136, it flows through to the seven outer through holes 139 annularly arranged to the last plate 137.

The fluid from each outer through hole 139 of the plate 137 communicates with some of the seven inner through holes 34 annularly arranged inside the outer through hole 139 through the adjacent annular grooves 37. Each inner through hole 34 penetrates each plate 137, 136 and 135 and communicates with the seven spiral passages 140 formed in the next plate 134. Each spiral passage 140 has seven through holes 41. Communicate with one of. Each through hole 41
All 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 through hole 41 on the rotating side is directly communicated 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 the state in which it does not rotate and is in the neutral position.

Each plate 133 to 1 in these hydraulic devices
The 37 are welded together to form an integral unitary structure.

In the hydraulic system shown in FIG. 29, each fluid inlet / outlet and each annular recessed groove (P1, R1, P2, M1, C1, R2 and C1) in the main body 127 of the power steering unit are shown.
And all fluid passages connecting them must be cast and / or machined. This involves a number of time-consuming and labor-intensive manufacturing operations.

In another device shown in FIG. 35, a series of plates 146 forming part of the housing 127a of the device.
Indicates the fluid inlet / outlet of this device and each annular recessed groove (P1, R1,
The structure of each fluid passage between P2, M1, C1, R2 and C1) is simplified. If you add a series of plates 147,
The structure of each fluid passage that connects the through hole 130 to each small chamber of the gerotor is also simplified.

Each of the individual plates of each series of plates 146, 147 is individually easy to fabricate (usually by stamping), yet reduces the number of remaining parts in the device or simplifies its construction. Designed. (For example, in the device disclosed herein, each fluid passage 14 of the housing 127a
8 and 149 are designed so that they can be manufactured by a single drilling operation that vertically pierces the flat surface of the housing 127a). Each series of plates 146 and 147 are then joined together to form a respective unitary unitary structure.

Each plate 147 for the fluid inlet and outlet of the gerotor,
Since each of the control unit main body plates 146 has a multi-layered plate structure, the manufacturing cost thereof is greatly reduced and the flexibility of various power control units can be increased.

While the preferred embodiments of the 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 first embodiment of the present invention.

FIG. 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 seen from the direction shown by the arrow line 4-4 in FIG.

5 is a horizontal cross-sectional view as seen from the direction indicated by arrows 5-5 in FIG. 1, and FIG. 5A is a partial cross-sectional view as seen from the direction indicated by arrows 5A-5A in 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 transverse cross-sectional view seen from the direction shown by the arrow line 7-7 in FIG.

FIG. 8 is a central longitudinal sectional view showing a second embodiment of the present invention.

9 is a transverse cross-sectional view of different portions viewed from the direction shown by each arrow line 9-9 in FIG.

10 is a transverse cross-sectional view of different portions viewed from the direction shown by each arrow line 10-10 in FIG.

FIG. 11 is a transverse cross-sectional view of different portions viewed from the directions shown by the arrow lines 11-11 in FIG.

FIG. 12 is a vertical cross-sectional view corresponding to the partial vertical cross section of the right-hand side end portion of FIG. 1 and showing a pressure applying communication annular groove particularly arranged in the end face cover in another embodiment.

13 is a vertical cross-sectional view corresponding to the partial vertical cross-section of the right-hand side end portion of FIG. 1, showing a pressure applying plate particularly attached to an end face cover in another embodiment.

14 is a central longitudinal section similar to that of FIG. 1, but specifically for a structure including a star-shaped annular fluid passage.

FIG. 15 is a transverse cross-sectional view of the portion seen from the direction indicated by arrow line 15-15 in FIG.

16 is a transverse cross-sectional view of the portion seen from the direction shown by arrow lines 16-16 in FIG.

FIG. 17 is a central longitudinal cross sectional view as in FIG. 8 of a hydraulic system having a shortened through hole and a different manifold passage.

18 is a transverse cross-sectional view showing the hydraulic device of FIG. 7 taken along the line 18-18 of FIG. 17 as viewed from the direction of FIG.

19 is a transverse cross-sectional view showing the manifold plate of FIG. 17 taken along the arrow line 19-19 of FIG.

20 is a central longitudinal cross-sectional view as shown in FIG. 14 showing a hydraulic device having symmetrical fluid inlets and outlets.

21 is a transverse cross-sectional view showing the manifold plate of the hydraulic apparatus with a symmetrical fluid inlet / outlet port 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.

23 is a transverse cross-sectional view showing the manifold plate of the reverse flow switching hydraulic device shown in FIG. 22, which is viewed from a direction shown by arrow lines 23-23 in FIG. 22.

FIG. 24 is a central longitudinal sectional view similar to FIG. 14, showing a hydraulic device in which a fluid inlet / outlet is directly connected to a manifold plate.

25 is a transverse cross-sectional view showing one end surface of the manifold plate of FIG. 24 as seen from the direction indicated by the arrow line 25-25 of FIG. 24.

26 is an end view showing the other end surface of the manifold plate of FIG. 24 as seen from the direction of arrows 26-26 of FIG. 24.

27 is an end view showing the outer end surface of the passage blocking plate of FIG. 24 as seen from the direction of arrows 27-27 in FIG.

28 is an end view showing the inner end surface of the end plate of FIG. 24 as seen from the direction indicated by the arrow line 28-28 of FIG. 24.

FIG. 29 is a central longitudinal sectional view similar to FIG. 14, showing an intermediate plate gerotor fluid inlet / outlet passage.

30 is a cross-sectional view showing a cross section of the fluid inlet / outlet passage of FIG. 29 as seen from the direction indicated by the arrow line 30-30 in FIG. 29.

31 is a cross-sectional view showing the next portion of the fluid inlet / outlet passage of FIG. 29 as seen from the direction indicated by the arrow line 31-31 in FIG. 29.

32 is a cross-sectional view showing a further next portion of the fluid inlet / outlet passage of FIG. 29, as seen from the direction of arrows 32-32 in FIG. 29.

33 is a cross-sectional view showing another part of the fluid inlet / outlet passage of FIG. 29 as seen from a direction indicated by arrows 33-33 in FIG. 29.

34 is a cross-sectional view showing a further next part of the fluid inlet / outlet passage of FIG. 29, as seen from the direction shown by arrow lines 34-34 in FIG. 29.

FIG. 35 is a central longitudinal sectional view showing another unit similar to the power steering unit shown in FIG. 29.

36 is an end view showing one of the multilayer plates of FIG. 35 as seen from the direction indicated by the arrow line 36-36 of FIG. 35.

37 is an end view showing another one of the multilayer plates of FIG. 35, as seen from the direction indicated by the arrow line 37-37 of FIG. 35.

38 is an end view showing still another multilayer board of FIG. 35, as seen from the direction of arrows 38-38 of FIG. 35.

39 is an end view showing still another different sheet of the multilayer board of FIG. 35, as seen from the direction shown by arrow lines 39-39 of FIG. 35.

[Explanation of symbols]

 20; 60: Main housing 21; 61: Wear plate 22; 62: Gerotor assembly 23; 63: Manifold plate 24; 64: End face cover 25; 65: Assembly bolt 26; 66: Fluid passage 27; 62a: Stator 28; 72 : Rotor 29; 80: Small chamber 29a; 80a: Smallest chamber 30; 66: Fluid inlet 31; 85: Fluid outlet 38; 71: Swing rod 44; 70: Drive shaft 44b, 44c; 71a, 71b: Spline connection part 47; 48: Bearings 49; 50: Shaft sealing device 127; 127a: Power steering unit 129; 129a: Sliding member

Claims (9)

[Claims] 1. A fluid control in a gerotor hydraulic system comprising a housing, a rotor having two flat axial end faces, a plurality of gerotor chambers, and an inlet and an outlet, which is 100%. A pair of flow passages through which the fluid flows, and a through hole that penetrates the rotor from one of the two flat axial end surfaces of the rotor and extends substantially on the axis of the rotor portion, One of the pair of flow passages extends from the other of the two flat axial end faces of the rotor to the through hole, the other of the pair of flow passages is in the rotor, and the pair of flow passages is A means for connecting one of the passages to one of the inlet and the outlet, a means for connecting the other of the pair of passages to the other of the inlet and the outlet, and when the hydraulic device is activated. Connect the pair of flow passages to the A gerotor type hydraulic system having fluid control constituted by means arranged in the housing for selective connection to each chamber of the gerotor. 2. The gerotor type hydraulic apparatus according to claim 1, wherein the other of the pair of flow passages penetrates the rotor from the other of the two flat axial end faces of the rotor, and the rotor portion. A second through hole substantially extending on the axis line of the gerotor type hydraulic device, wherein the second through hole is different from the through hole penetrating the rotor. 3. The gerotor type hydraulic device according to claim 1, wherein the other one of the pair of flow passages passing through the rotor is at one end thereof from the other of the two flat axial end faces of the rotor. Although it includes a through hole penetrating the rotor and extending substantially on the axis of the rotor portion,
The gerotor type hydraulic apparatus, wherein the second through hole of the rotor is different from the through hole that penetrates the rotor. 4. A fluid control in a gerotor type hydraulic system comprising a housing, a rotor having two flat axial end faces, a plurality of gerotor chambers, and an inlet and an outlet, said rotor comprising: A pair of flow passages consisting of one flow passage extending straight from one end surface to the other end and the other flow passage in the rotor; and a pair of flow passages when the hydraulic device is operated. A gerotor type hydraulic system having fluid control constituted by means arranged in said housing for selective connection to each chamber of said gerotor. 5. The gerotor type hydraulic device according to claim 4, wherein the one of the pair of flow passages surrounds the other of the pair of flow passages. . 6. The gerotor type hydraulic device according to claim 4, wherein the other one of the pair of flow passages surrounds one of the pair of flow passages. 7. A gerotor type hydraulic pressure comprising a housing, a rotor having a flat axial end surface that rotatably engages with the housing in one plane, a plurality of gerotor chambers, and an inlet and an outlet. A fluid control in the device, wherein a pair of flow passages disposed in the rotor, one flow passage of which surrounds the other flow passage, and a pair of the flow passages of the pair in the plane. Means for connecting one of the flow passages to one of the inlet and the outlet, means for connecting the other of the pair of flow passages to the other of the inlet and the outlet in the same plane, and the hydraulic pressure. In order to selectively connect the pair of flow passages to the chambers of the gerotor so that rectification and flow path switching action of the hydraulic device is realized on one side of the rotor when the device is operated. A gerotor type hydraulic system having fluid control constituted by means disposed in the housing in the same plane. 8. The gerotor type hydraulic apparatus according to claim 7, further comprising an input / output shaft and an oscillating rod, wherein the plane on which the rectification and the flow path switching action are realized is the oscillating rod. A gerotor type hydraulic device, which is on the same side as one side of the rotor drivingly connected to the input / output shaft. 9. The gerotor type hydraulic apparatus according to claim 7, further comprising an input / output shaft and an oscillating rod, and the oscillating rod is provided on the plane where the rectification and the flow path switching action are realized. A gerotor type hydraulic device, which is located on the side opposite to one side of the rotor drivingly connected to the input / output shaft.