SE530925C2 - Eccentric radial piston pump and eccentric radial piston motor - Google Patents

Description

The risk chamber ring 43 may be located so that they are eccentric. The eccentric cam ring 43 can move eccentrically while maintaining a parallel state with respect to the center axis of the cylinder block 40.

The eccentricity of the eccentric cam ring 43 is controlled by guide pistons 46, 47. The respective ends of the guide pistons 46, 47 can abut against the eccentric cam ring 43 and push it from both sides by the compressive force of springs 48, 49. The eccentric cam ring 43 may be eccentric with respect to the center axis of the pin 44 by pressure oil acting on the guide piston 46.

Pressure oil supplied to the control piston 46 is regulated by a power steering valve 50 which can be inclined in a circumferential direction for a housing 45.

Patent Document 1: Japanese Laid-Open Patent Publication No. 2004-68796.

Description of the Invention Problems to be Solved with the Invention In the eccentric radial piston pump or eccentric radial piston motor, the eccentricity of the center of the eccentric cam ring and the center of rotation of the housing of the radial piston pump or eccentric radial piston motor are controlled by the size of the eccentric cam movement. The compressive force generated by the piston is absorbed by the inner peripheral surface of the eccentric cam ring. The entire compressive force from the piston is therefore absorbed in such a way that a concentrated load is absorbed on the lower surface of the eccentric cam ring.

Therefore, when the rigidity of the eccentric cam ring is small, for example when the thickness of the eccentric cam ring is thin, the eccentric cam ring will be deformed into a triangular shape by the compressive force from the piston. That is, as shown in fi g. 14, therefore, the eccentric cam ring is circular in an unloaded condition and receives a compressive force (shown by arrows in Fig. 15) from the pistons, the insides of which cylinder holes are subjected to high pressure, so that the eccentric cam ring absorbs a deformation stress from its inside and deforms. The eccentric cam ring is thus deformed from being circular in an unloaded state according to fi g. 14 to a triangular shape when absorbing the deformation stresses according to fi g. 15.

In case deformation occurs in the eccentric chamber ring, the cylindrical surface of the piston jaw sliding along the inner peripheral surface of the eccentric chamber ring will not be in full contact with the inner peripheral surface of the deformed eccentric chamber ring along its entire surfaces, so a gap arises. . Due to this gap, the abutment between the piston jaw and the inner peripheral surface of the eccentric cam ring becomes non-uniform.

For example, when the piston jaw slides along the inner peripheral surface of the eccentric cam ring, and when it reaches a point where the outer diameter of the cylindrical surface of the piston jaw is larger than the inner diameter of the eccentric cam ring, only the two end edge sides in the circumferential direction of the piston jaw will slide the inner diameter of the eccentric cam ring, so that a large surface pressure is exerted on the two end edge sides. Due to the high surface pressure on the two end edge sides in the circumferential direction of the piston jaw, bending stresses are generated in the piston jaw. Furthermore, when it reaches a place where the outer diameter of the cylindrical surface of the piston jaw is smaller than the inner diameter of the eccentric cam ring, the abutment of the piston jaw becomes smaller, so that it is inclined to float.

As shown in fi g. 13, in the case of patent document 1, the thickness of the eccentric cam ring at the conventional eccentric radial piston pump or eccentric radial piston motor is designed to be thick to prevent deformation of the eccentric cam ring. However, in the case where the thickness of the eccentric cam ring is dimensioned thick, a problem arises that the outer dimension in the radial direction of the eccentric radial piston pump or eccentric radial piston motor becomes large. However, since the outer dimension in the radial direction at the eccentric radial piston pump or the eccentric radial piston motor must be designed as small as possible, it is contrary to the requirement to make the outer dimension in the radial direction large. An object of the present invention is to solve the problems of the prior art and to provide an eccentric radial piston pump and an eccentric radial piston motor in which the rigidity of the eccentric cam ring can be increased, even when the thickness of the eccentric cam ring is not dimensioned to be thick, and where the outer dimension in the radial direction can be dimensioned small.

Means of solving the problems The objects of the present invention can be achieved with the respective inventions according to claims 1-10.

According to the invention in claim 1, an eccentric radial piston pump is proposed, in which the displacement volume of pressure oil changes depending on the size of an eccentricity of an eccentric chamber ring, the pump being substantially characterized in that the eccentric chamber ring is slidably arranged between a pair of guide surfaces which are arranged opposite each other inside a housing of the eccentric radial piston pump, and a shaft, which inserts in the radial direction, is located on an inner peripheral surface of an end portion on an outlet side of the eccentric cam ring over a predetermined extent.

In the invention according to claim 2, the shape of the eye is defined, which is the main feature.

In the invention according to claim 3, the ratio of the thickness of the eccentric cam ring and the thickness of the flange is further defined, which is the main feature.

In the invention according to claim 4, it is further defined, inter alia, the design in a side end surface of the flange.

In the invention according to claim 5, an eccentric radial piston engine is defined, in which the displacement volume of pressure oil changes depending on the eccentricity of an eccentric cam ring, the engine being mainly characterized in that the eccentric cam ring is slidably arranged between a pair of guide surfaces, which are arranged 15 20 25 30 530 S25 5 are opposed to each other inside a housing of the eccentric radial piston engine, and a shaft projecting in the radial direction is arranged on an inner peripheral surface of an end portion on a high pressure side of the eccentric cam ring over a predetermined extent.

In the invention according to claim 6, the shape of the islet is defined.

Claim 7 of the invention defines the eccentric cam ring and the thickness of the flange.

Furthermore, they claim the invention's claim 8 b | .a. the design of a side end surface of the fl end.

The function of the housing By forming an eccentric radial piston pump and an eccentric radial piston motor according to the invention in an even radial direction on the inner peripheral surface of the eccentric chamber ring without increasing the thickness thereof, the rigidity of the eccentric chamber ring can be increased.

By further forming the flange on the inner peripheral surface of the end portion of the outlet side of the eccentric cam ring in the eccentric radial pump and by forming the flange on the inner peripheral surface of the end portion on the high pressure side of the eccentric chamber ring at the eccentric radial piston deformation of the eccentric cam ring by a pressure force from the piston.

According to the invention, the end may also be designed to cover the entire inner periphery of the inner peripheral surface of the end portion of the eccentric cam ring. By designing the axis covering the entire inner periphery of the inner peripheral surface of the end portion, deformation of the eccentric chamber ring can be prevented in a further powerful manner. 10 15 20 25 30 530 925 Brief description of the drawings Fig. 1 k) Fig.

Fig. B) Fig. 4 Fig. 5 Fig. 6 Fig. 7 Fig. 9 Fig. 10 Fig. 11 Fig. 12 Fig. 13 Fig. 14 Fig. 15 is a vertical cross-sectional view of an eccentric radial piston pump (first embodiment. Is. a vertical cross-sectional view of an eccentric cam ring (first embodiment) is a vertical cross-sectional view of another eccentric cam ring (first embodiment) is a vertical cross-sectional view of a further eccentric cam ring (first embodiment) is a perspective view of an eccentric cam ring (first embodiment). is an additional perspective view of an eccentric cam ring (first embodiment) is an additional perspective view of an eccentric cam ring (first embodiment) is a model view for analyzing the stiffness of an eccentric cam ring (first embodiment). is a view showing the force distribution of the analysis model (first embodiment) is a table showing the analysis results (first embodiment) is a schematic vertical cross-sectional view of an eccentric radial piston pump (second embodiment) is a schematic vertical cross-sectional view of an eccentric radial piston engine (third version). is a schematic vertical cross-sectional view of an eccentric radial piston pump (known design). shows an eccentric cam ring in an unloaded state (explanatory example). shows a deformed eccentric cam ring when the load is applied (explanatory example).

Reference numeral list GUI-ÄOO-Å eccentric radial piston pump eccentric cam ring cylinder block piston faPP 10 15 20 25 30 530 325 7 10. inlet port 11 outlet port 12 flange 15a, 15b piston 22, 23 drive mechanism 25a, 25b piston 28a, 28b pressure element 30, 31 engaging element 32 eccentric radial piston motor 33 pin 34, 35 port 40 cylinder block 41 piston 43 eccentric cam ring 44 pin 46, 47 steering piston B power steering 50 way of carrying out the invention A suitable embodiment of the present invention is described in more detail below with reference to the accompanying drawings. In the constructions of an eccentric radial piston pump and an eccentric radial piston motor according to the present invention, designs and arrangements by means of which the problems according to the invention can be solved can also be applied in other ways than by means of the designs and arrangements described below. Thus, the present invention is not limited to the embodiments described below, but various modifications are possible.

An eccentric radial piston pump or an eccentric radial piston motor according to the present invention also includes an eccentric radial piston pump / motor that can apply both pump function and motor function. 10 15 20 25 30 530 925 First embodiment Fig. 1 shows a schematic vertical cross-sectional view of an eccentric radial piston pump 1 according to an embodiment of the present invention. Fig. 2 shows a vertical cross-sectional view of an eccentric chamber ring 3. As shown in Fig. 1, the eccentric chamber ring 3 is placed in a housing 2, and a cylinder head 4 is rotatably arranged inside the eccentric chamber ring 3. In the cylinder block 4, a number of cylinder holes 7 are received in the radial direction of the block, and the respective pistons 5 are slidably mounted in the respective cylinder holes 7.

A piston jaw 6 is pivotally connected to the piston 5. The piston jaw 6 slides on a cam surface 3A of the eccentric cam ring 3 and slides on the cam surface 3A depending on the rotation of the cylinder block 4. The sliding of the piston jaw 6 on the cam surface 3A can cause reciprocating movement of piston 5.

A pin 8, arranged in the housing 2, is inserted in a pin receiving part 9 in the cylinder block 4 for rotatably supporting the cylinder block 4. In the pin 8 an inlet port 10 and an outlet port 11 are formed. By the rotation of the cylinder block 4, the piston 5 a repetitive intake and discharge.

In the suction process, the piston 5 is displaced in a direction in which the piston 5 projects from the cylinder hole 7 from the upper turning position to the lower turning position to suck pressure oil from the inlet port 10 to the inside of the cylinder hole 7. Upon discharge, the piston 5 is displaced from the lower turning position to the upper turning position for pressurizing the pressure oil in the cylinder hole 7. The pressure oil, which has received high pressure through the compression, is discharged from the outlet port 11.

As shown in fi g. 2, an annular shaft 12 is formed along the inner peripheral surface of the eccentric chamber ring 3. 1, the annular end 12, which is formed along the inner peripheral surface of the eccentric chamber ring 3, is shown as a shape in which it extends from the cam surface 3A to the center side of the eccentric chamber ring 3.

On the left and right sides of the housing 2, cylinder chambers 14a, 14b are formed, and in the respective cylinder chambers 14a, 14b, pistons 15a, 15b are slidably mounted and abut against the outer peripheral surface of the eccentric chamber ring 3.

The respective pistons 15a, 15b are biased by springs 16a, 16b, and the upper end portions of the pistons 15a, 15b abut against the outer peripheral surface of the eccentric chamber ring 3 under constant pressure against it.

By a changeover of a gear valve 18, pressure oil is fed from a hydraulic pump 19 to a side cylinder chamber 14a or cylinder chamber 14b, while pressure oil in the second side cylinder chamber 14b or cylinder chamber 14a can be fed to a tank 20.

The outer peripheral surface of the eccentric cam ring 3 slides against guide surfaces 13 formed on the upper and lower parts of the housing 2. By activating the pistons 15a, 15b by a changeover of the changeover valve 18, the eccentric cam ring 3 can be moved along the guide surfaces 13, and the size on the exoentricity with respect to the center of rotation of the cylinder block 4 can be set.

As shown in fi g. 2, the end 12 is formed on the inner peripheral surface of the end portion of the eccentric chamber ring 3, circularly towards the inside in the radial direction, so that the rigidity of the eccentric chamber ring 3 is increased by means of the flange 12.

Since the rigidity of the eccentric chamber ring 3 is increased by the design of the shaft 12 so that a deformation thereof can be prevented, the cam surface 3A of the eccentric chamber ring 3 can permanently maintain a certain shape. A sliding relationship between the piston jaw 6 and the cam surface 3A can therefore be maintained permanently in an excellent condition, and the piston jaw 6 can be prevented from lifting from the cam surface 3A.

The flange 12 may be formed integrally with the eccentric chamber ring 3 or be constructed as a separate part from the eccentric chamber ring 3. In the case fl the flange 12 is formed as a separate part, the flange 12 may be fixed on the inner peripheral surface of the eccentric chamber ring 3 by utilization of pressure or the like, or it can be fixed stationary on the eccentric chamber ring 3 by using fastening aids, such as welding or the like. The flange 12 must be designed in such a way that the insertion of the ns end 12 in the radial direction is chosen such that the kan end can obtain sufficient rigidity to prevent deformation of the eccentric chamber by a pressure from the piston 5. At the ratio between material and thickness of the shaft 12, the size of the insert can further be varied in the radial direction.

As shown in Fig. 3, where the ends 12 are formed on both end portions of the eccentric chamber ring 3, one end may be formed integrally with the chamber ring 3, while the other end 12 may be formed as a separate component of the eccentric chamber ring 3. The flange 12, which is designed as a separate component, can be designed in such a way that it has an end part which extends towards the inner peripheral surface of the eccentric chamber ring 3, as shown in fi g. 3, or the end 12 may be constructed in such a way that it has end portions extending towards the inner peripheral surface and the outer circumferential surface of the eccentric chamber ring 3, as shown in fi g. 4. The flange 12, designed as a separate component, can be erasxerted on the eccentric chamber ring 3 by using fixing methods which use pressure or the like or fixeration methods such as welding or the like.

The design of the 12 end 12 may have shapes shown in perspective view of the eccentric chamber ring 3 in fi g. 5-7, as opposed to circular flange shape. The shapes of fl änsen 12 i fi g. 5-7 are examples, and the present invention is not limited to these forms. These shapes can be used as according to the present invention, as long as it has a shape by means of which the rigidity of the eccentric chamber ring 3 can be increased, and the shape is thereby included in the present invention.

As shown in fig. 5, the flange 12 may be located on a part of the inner peripheral surface of one end portion of the eccentric chamber ring 3. In this case, the same flange 12 may be located on a part on which a pressure force from the piston 5 in the cylinder block 4 is exerted in large extent. Thus, the flange 12 may be located on the inner peripheral surface of the end portion on an outlet side of the eccentric cam ring 3.

The design, in which the end 12 is located on the inner peripheral surface of the end portion, may comprise both embodiments in which the end 12 is located inside the inner peripheral surface of the eccentric chamber 3 and in which a side surface of the end 12 and an end face of the eccentric chamber ring 3 is in firm contact with each other.

As shown in Fig. 6, the ends 12 can also be arranged on both end portions of the eccentric chamber ring 3 on which a compressive force is exerted from the piston 5 to a large extent. As further shown in fi g. 7, the flanges 12 may be located on the inner peripheral surface of the end portion on both sides of the eccentric chamber.

The flange 12 can thus be formed on an area of the inner peripheral surface of the end portion of the eccentric cam ring 3 which receives a large deformation load. By constructing it in this way, the eccentric chamber ring can be effectively prevented from being deformed by means of the shaft 12, which is arranged over a minimum required extension.

From the above, the edge 12, which is located on the inner peripheral surface of the end portion of the eccentric chamber 3, may be formed so as to cover the entire circle of the inner peripheral surface of the end portion of the eccentric chamber 3, or it may also be formed within an area of the eccentric chamber. the inner peripheral surface of the end portion of the eccentric chamber 3 which receives a large deformation load in the form of a compressive force from the piston 5, since the pressure oil inside the cylinder hole 7 has a high pressure.

In the case where the flange 12 is located on a part of the inner peripheral surface of the end portion of the eccentric chamber 3, it is necessary that the flange 12 is designed in such a way that concentrated load is not exerted on the boundary area between the portion where the flange 12 is located and the portion does not exist, i.e. the boundary portion between the flange 12 and one end portion surface of the eccentric chamber ring 3.

In the case where the end 12 is formed on inner peripheral surfaces of the two end portions of the eccentric chamber ring 3, the flange 12, which is located on at least one end side, may have a divided shape and formed as a body separate from the eccentric chamber 3. The flange 12 can, as shown in fi g. 6, nevertheless be designed in such a way that the insertion distance in the radial direction of the flange 12 on one end side is smaller than the insertion in the radial direction of the end 12 on the other end portion side. By means of this construction, the end parts, which are formed as separate parts by dividing the end 12 into a number of parts, in the assembly of the eccentric radial piston pump 1, can be assembled in order depending on the insertion and the assembly of the piston in the cylinder block.

Alternatively, the diameter of the outer circumference, including the piston jaws 6 when the respective pistons 5 are inserted into the respective cylinder holes 7 in the cylinder block 4 to the upper turning position, can be chosen to be a diameter of the outer circumference which allows insertion through the opening formed by the the upper end of the 12 end 12 on the side where the insertion in the radial direction of the 12 end 12 is reduced, and of the inner peripheral surface of the eccentric cam ring 3.

The flanges can therefore be arranged on both ends of the eccentric chamber ring, and the mounting where the pistons 5 are inserted into the cylinder block 4 on the inside of the eccentric chamber ring 3 can be carried out in a simple manner.

Suitably, the thickness of the flange 12 is approximately equal to the thickness of the eccentric chamber ring 3. Fig. 8 shows an analysis model view showing the relationship between the thickness t1 of the eccentric chamber ring 3 and the thickness t2 of the flange 12, where fi g. 8 shows the cross-sectional shape of an adjacent area of the eccentric chamber ring 3.

Respective models of the eccentric chamber ring 3, in which the ratio between the thickness t1 of the eccentric chamber ring 3 and the thickness t2 of the 12 end 12 is changed, were made under conditions where the inner diameter, the inner diameter of the flange and the cam width of the eccentric chamber ring 3 are fixed dimensions. the eccentric chamber ring 3 in fi g. 8, and an analysis by finite element method was performed with respect to combat stresses in the respective models. While the analysis was performed by finite element method, the ratio between the thickness t1 and the thickness t2 was changed under a ratio when the mass of the eccentric chamber 3 is substantially constant.

The distribution of the combat stress, which was calculated by the finite element method, became the stress distribution shown in fi g. Fig. 9 is a perspective view of the main part, where a portion, where the eccentric chamber ring 3 abuts against the guide surface 13 of the housing 2, is the center thereof. As shown in fi g. 9, the maximum stress 61 is generated at a part where the eccentric chamber 3 on the outlet side abuts against the guide surface 13 of the housing 2. It is further seen that the stress decreases from and to 03, and where G4 becomes larger depending on the distance from the part, where it abuts styrytan 13.

As further stated in fi g. 9, the generated stress can be attenuated small in the part where at least the maximum stress 01 is generated, or in a part where a stress greater than a desired stress (for example a stress greater than 63) is generated by designing another fl also on one end portion of the eccentric chamber 3. Although in fi g. 9 shows an example, where the flange 12 is formed on one side of the eccentric chamber ring 3, therefore the shaft 12 can for instance be formed on both end sides of the eccentric chamber ring 3, as shown in fi g. A6, so that the eccentric chamber ring 3 can have a construction which is even more difficult to deform.

Fig. 10 is a table showing analysis results for the combat stress, calculated by the finite element method under the above-mentioned conditions in the models described above. As shown in fi g. 10, the combat stress is minimal when the ratio between the thickness t1 of the eccentric chamber ring 3 and the thickness t2 of the flange 12 is 1: 1. Maximum combat stress, which is generated at this time, can also be within a permitted range. Furthermore, the outer dimension of the eccentric chamber ring 3 can be minimal, when the ratio between the thickness t1 and the thickness t2 is 1: 1.

When the ratio between the thickness t1 and the thickness t2 is 1: 1, the dimension of the eccentric radial piston pump 1 can be made small in the radial direction. Furthermore, the rigidity of the eccentric chamber 3 can be strong enough to prevent the eccentric chamber 3 from deforming.

By designing the thickness t1 of the eccentric chamber ring 3 substantially equal to the thickness t2 of the shaft 12, the eccentric chamber ring 3 can in this way be given a rigidity by means of which deformation can be prevented due to a pressure from the piston, and the size of the eccentric chamber 3 can be minimal . 10 15 20 25 30 530 525 14 Furthermore, the sliding stability of the piston jaw 6 can be achieved, and the eccentric radial piston pump 1 can be operated stably. The rigidity of the eccentric chamber ring 3 can be further increased without increasing the thickness t1 of the eccentric chamber ring 3. Thus, the outer dimension of the eccentric radial piston pump 1 can be designed small in the radial direction of the pump, and further, the volumetric efficiency can be improved. Even when a drive mechanism or the like for the eccentric chamber ring 3 is arranged inside the eccentric radial piston pump 1, the outer dimension of the eccentric radial piston pump 1 can be reduced in radial direction.

When the drive mechanism or the like, which affects the eccentricity of the eccentric chamber ring 3, is located outside the eccentric chamber ring 3 in its axial direction, the length of the eccentric radial piston pump 1 becomes long in its axial direction.

However, since the outer dimension of the eccentric radial piston pump 1 can be reduced in the radial direction of the pump, the maximum dimension, including the vertical and horizontal length and the height of the eccentric radial piston pump 1, can be designed small.

Furthermore, since the external dimension of the eccentric radial piston pump 1 is reduced in the radial direction, the surface on which the eccentric radial piston pump 1 is arranged can be reduced, so that it can be used efficiently even in a compact hydraulic machine or the like.

Second Embodiment Fig. 11 shows a schematic vertical cross-sectional view of another eccentric radial piston pump 1 according to an embodiment of the present invention. As a construction for making the eccentric chamber ring 3 eccentric in the first embodiment, the eccentric chamber ring 3 can be eccentric by actuating pistons 15a, 15b on the left and right side of the housing 2. In the second embodiment, on the other hand, engaging elements 30, 31, formed on a side surface of the 12 end 12 of the eccentric chamber ring 3, and drive mechanisms 22, 23 10 15 20 25 30, 530 925 15 which affect the eccentricity to influence the engaging elements 30, 31, so that the eccentric chamber ring 3 can become eccentric.

The second embodiment has this construction, which differs from the construction in the first embodiment. Other construction details are similar to those in the first embodiment. Thus, the same reference numerals denote corresponding components in the second embodiment, so an explanation of these is omitted. The engaging elements 30, 31, which are formed on a side surface of the flange 12, may be arranged thereon as elements which are fitted in a hole 12a, as shown in Figs. 2, or they may be integral with the shaft 12. The drive mechanism 22 is provided with a pair of pistons 25a, 25b which receive pressure oil from the hydraulic pump 19 to press on the engaging member 30 and springs 26a, 26b which press the pair pistons 25a, 25b towards the side of the engaging element 30. The drive mechanism 23 is provided with a pair of pressure elements 28a, 28b acting from both ends of the pressure element 31, and springs 29a, 29b exert a compressive force on the pair of pressure elements 28a, 28b.

The pair of pistons 25a, 25b and springs 26a, 26b drive mechanism 22 are located inside cylinder chambers 24a and 24b, respectively. By reversing the gear valve 18, pressure oil is fed from the hydraulic pump 19 to the cylinder chamber 24b, and when the pressure oil inside the cylinder chamber 24a is fed to the tank 20, the piston 25b is displaced to the left in fi g. 11, the eccentric chamber ring 3 also moving in a direction to the left in fi g. 11. When this gear valve 18 is reversed from its shown gear position to the opposite gear position, the eccentric chamber ring 3 can be moved in a direction to the right in fi g. 11.

The pair of pressure elements 28a, 28b in the drive mechanism 23 are actuated in a direction in which they come close to each other by the biasing force of the springs 29a, 29b located inside the spring chambers 27a and 27b, respectively. A rotation preventing mechanism of the eccentric chamber ring 3 is formed by the pair of pressure elements 28a, 28b. When the eccentric chamber ring 3 moves under the action of the pair of pistons 25a, 25b in the drive mechanism 22, the springs 29a, 29b are deformed, and the eccentric chamber ring 3 can be moved in parallel.

The current position of the cylinder chamber 24b and the position of the spring chamber 27a with the pressure element 28a can be reversed to form the drive mechanism 22 and the drive mechanism 23. In this case the drive mechanism 22 consists of the cylinder chamber 24a with the piston 25a and the spring chamber 27a with the pressure element 28a placed in the cylinder chamber 24b. 23 is formed by the cylinder chamber 24b with the piston 25b located at the location of the der chamber 27a and the 27 chamber 27b with the pressure element 28b.

Similarly, the current location of the cylinder chamber 24b and the location of the spring chamber 27b with the pressure member 28b can be reversed to form the drive mechanism 22 and the drive mechanism 23. Even when such an arrangement is made, pressure oil is selectively supplied from the gear valve 18 to the cylinder chamber 24a and the cylinder chamber 24b. so that the movement of the eccentric chamber ring 3 can be controlled.

In the construction according to the second embodiment, the pairs of pistons abutting against both sides of the engaging elements 30, 31 in kan g. 11 can be arranged on both sides of the respective engaging elements 30, 31.

As shown in fi g. 11, the outer shape of the eccentric radial piston pump 1 can be made small in the radial direction, since the drive mechanisms 22, 23 can be placed on the outside of the eccentric chamber ring 3 in its axial direction and even on the inner diameter side of the eccentric chamber ring 3.

Since the drive mechanisms 22, 23 in this case affect the eccentricity of the eccentric chamber ring 3 and are located on the outside of the eccentric chamber ring 3 in its axial direction, the length of the eccentric radial piston pump 1 becomes longer in its axial direction. Since the outer dimension of the eccentric radial piston pump 1 in its radial direction can be made small, the maximum dimension, including vertical and horizontal lengths and the height of the eccentric radial piston pump 1, can be made small. l instead of the construction where the hole 12a in fi g. 2 is used as a hole for attaching the engaging elements 30, 31, which engage with the drive mechanisms 22, 23, the hole 12a can be used as a rotary stop to stop the rotation of the eccentric chamber 3. In place of the structure where the hole 12a is formed on a side surface of ns end 12, a rotary stop can furthermore be formed in one piece with the eccentric chamber.

Third Embodiment Fig. 12 shows a schematic vertical cross-sectional view of an eccentric radial piston engine 32 according to an embodiment of the present invention. The third embodiment has a construction similar to that of the eccentric radial piston pump 1 in the first embodiment, except that it shows the construction of the eccentric radial piston motor 32. As for the similar construction with the eccentric radial piston pump 1, the explanation of the reference numerals will therefore be is omitted below using the reference numerals used in Fig. 1.

The eccentric radial piston motor 32 has a construction in which the cylinder block 4 and a pin 33 rotate continuously connected. The pressure oil channels in the pin 33, which communicate with the ports 34 and 35, respectively, are thus formed with the same diameter.

The eccentric radial piston pump 1 is in this context constructed in such a way that the pin 8 does not rotate when the cylinder block 4 rotates. As for the pressure oil ducts in the pin 33, the diameter of the duct communicating with the inlet port 10 is larger than the diameter of the duct communicating with the outlet port 11. The eccentric radial piston pump 1 may be designed in such a way that the diameter of the channel communicating with the inlet port 10 is the same as that of the channel communicating with the outlet port 11. At the eccentric radial piston pump / motor more specifically, it is necessary that the diameter of the channel communicating with the inlet port 10 be the same as that of the channel communicating with the outlet port 11.

Although fi g. 1 shows a construction example, where the inlet port 10 is arranged on a lower part of the drawing and where the outlet port 11 is arranged in an upper part of the drawing, the location of the inlet port 10 and the outlet port 11 can be reversed with respect to the locations in fi g. 1.

At the eccentric radial koiv motor 32 in fi g. 12 communicates port 34 on the underside in fi g. 12, for example, with the pressure oil of a high-pressure side, while the port 35, located at the top, communicates with the pressure oil on a low-pressure side. When the port 35, which communicates with the low pressure side on the upper side, comes to a lower side by the rotation of the cylinder block 4 and the pin 33, this time it communicates with the pressure oil on the high pressure side.

At the same time, the port 34 communicates with the high pressure side on the underside with the pressure oil on the low pressure side. The ports 34, 35 thus communicate alternately with the pressure oil on the high pressure side and the pressure oil on the low pressure side depending on the rotation of the cylinder block 4 and the pin 33.

High pressure oil is fed from the port 34 or port 35 which communicates with the pressure oil on the high pressure side and into the cylinder hole 7. When high pressure oil is fed into the cylinder hole 7, the piston 5 in the cylinder hole 7 is caused to rotate the cylinder block 4.

Similar to the description of the eccentric radial piston pump 1 in the first embodiment, the flange 12 may be constructed so as to project in a radial direction over a predetermined area of the inner peripheral surface of the end portion on at least the high pressure side of the eccentric chamber ring 3. Through the construction of the flange 12, the rigidity of the eccentric chamber ring 3 can be increased so that the chamber ring 3 is not deformed. 10 15 20 25 30 530 925 19 The flange 12 can be designed in a similar way as in fi g. 2-7. As described in connection with the first embodiment, as far as the shapes can increase the rigidity of the eccentric chamber 3, these shapes can be used as a shape according to the present invention.

By arranging the flange 12 on the eccentric cam ring 3, operating functions similar to those in the first embodiment can be applied, where the eccentric cam ring 3 with the end 12 is used at the eccentric radial piston pump 1.

The results of the analysis models, described in connection with fi g. 8-10, can be applied to the eccentric radial piston motor 32 without any modifications.

The construction of the eccentric radial piston motor 32 may be similar to that of the eccentric radial piston pump 1 of FIG. 11, other than the construction of Fig. 12.

In this case, it is desirable that the diameters of the channels in the pin, which communicate with the inlet port 10 and the outlet port 11, have the same diameter. As in the description of the second embodiment, an element engaging with a rotational stop is used when the eccentric cam ring is made eccentric, or an engaging element with respect to a drive mechanism which provides an eccentricity of the eccentric chamber can be arranged on a side surface of the end 12 of the eccentric chamber 3.

Although the construction of the eccentric radial piston pump 1 and the construction of the eccentric radial piston motor 32 described above in embodiments, the construction of the eccentric radial piston pump or the eccentric radial piston motor described in the embodiments includes the construction of an eccentric motor / eccentric pump.

Industrial applicability The technical idea of the present invention can be applied to a device or the like to which the technical idea of the present invention is applicable.

Claims (8)

10 15 20 25 30 530 325 20 Patent claims Eccentric radial coil pump (1), in which a displacement volume of pressure oil changes depending on an eccentricity of an eccentric cam ring (3), characterized in that the eccentric cam ring (3) is slidably arranged between a pair of guide surfaces, which are arranged opposite each other inside a housing (2) of the eccentric radial piston pump (1), and a flange (12) projecting in the radial direction, located on an inner peripheral surface of an end portion on an outlet side of the eccentric cam ring (3) ) over a predetermined extent. Eccentric radial coil pump according to claim 1, characterized in that the flange (12) is designed to cover the entire inner periphery of an inner peripheral surface of the end part. Eccentric radial coil pump according to Claim 1 or 2, characterized in that the thickness (t1) of the eccentric cam ring (3) is substantially equal to the thickness (t2) of the flange (12). Eccentric radial coil pump according to one of Claims 1 to 3, characterized in that a rotation-preventing engaging element (30, 31) is used when the eccentric ring (3) is made eccentric, and / or is an engaging element (30, 31) which engages with a drive mechanism (22; 23) which affects the eccentricity of the eccentric chamber ring (3), arranged on an outer side surface of the flange (12) which is parallel to an eccentric direction of the eccentric chamber ring (3). Eccentric radial piston engine (32), in which a displacement volume of pressure oil changes depending on an eccentricity of an eccentric cam ring (3), characterized in that the eccentric cam ring (3) is slidably arranged between a pair of guide surfaces, which are arranged opposite each other inside a housing (2) of the eccentric radial piston motor (32), and a flange (12) projecting in the radial direction is arranged on an inner peripheral surface of an end portion on a high pressure side of the eccentric cam ring ( 3) over a predetermined extent. 10 530 325 21 Eccentric radial piston engine according to claim 5, characterized in that the flange (12) is designed to cover the entire inner periphery of the inner peripheral surface of the end part. Eccentric radial piston engine according to claim 5 or 6, characterized in that the thickness (t1) of the eccentric cam ring (3) is substantially equal to the thickness (t2) of the flange (12). Eccentric radial piston engine according to one of Claims 5 to 7, characterized in that a rotation-preventing engaging element (31, 32) is used when the eccentric cam is made eccentric, and / or is an engaging element (31, 32) which engages with a drive mechanism. (31, 32) which affects the eccentricity of the eccentric chamber, arranged on an outer side surface of the flange (12), which is parallel to an eccentric direction of the eccentric chamber (3).