Improved gerotor type hydraulic motor

Abstract

The present invention relates to a Gerotor type fluid pump or Gerotor type fluid motor (100) having a gerotor plate segment (108). The gerotor plate segment (108) includes an internal recess (220) for a valve drive shaft (172) that orbits and rotates within the gerotor plate segment (108). The gerotor plate segment (108) further includes a plurality of circumferentially arranged fluid pass ports (136) for selectively fluidly connecting a spool segment (110) and a gerotor type fluid displacement segment (106) of the Gerotor type fluid pump / Gerotor type fluid motor (100). The internal recess (224) includes at least two axially aligned segments (221, 222) of different diameters designed in a non-detachable manner.

Description

Technical Field

[0001] The present invention relates to a distribution plate segment for a rotary fluid pressure device, comprising a recess for receiving a valve drive shaft that orbits and rotates within the distribution plate segment, and further comprising a plurality of circumferentially arranged fluid passage ports for selectively fluidly connecting a valve core segment and a Gerotor-type fluid displacement segment of the rotary fluid pressure device.

[0002] The present invention also relates to a rotary fluid pressure device, which includes at least one valve core segment, at least one distribution plate segment, at least one Gerotor-type fluid displacement segment, and a valve drive shaft. Background Technology

[0003] In numerous technical fields, pressurized fluids are used for a variety of purposes. To obtain such pressurized fluids, it is necessary to pressurize unpressurized fluids using hydraulic pumps or, generally, fluid-working machinery (especially machinery that can operate interchangeably as fluid pumps and fluid motors). Due to the widespread use of pressurized fluids, and therefore the use of fluid pumps to pressurize these fluids, a wide variety of fluid pumps have been proposed in the prior art. Similarly, a wide variety of fluid motors have been proposed to convert the energy stored in pressurized fluids back into mechanical energy. Generally, a suitable fluid pump design is selected from the various available fluid pump designs in the prior art, based on technical requirements (and also monetary factors). Some of the considerations influencing the selection of a fluid pump design include: available mechanical energy; the manner in which the mechanical energy is available (e.g., the contrast between high torque and low speed versus low torque and high speed), the required fluid pressure, and the required fluid flow rate. The same applies to fluid motors.

[0004] One of the fundamental designs of fluid pumps is the so-called Gerotor design. Here, an axially offset revolving component revolves and rotates around the surrounding housing, creating a reciprocating volume that typically alternates between essentially zero and a certain maximum design volume. Therefore, fluid can be pumped at high output pressures, but the fluid flow rate is usually relatively limited. The Gerotor pumping component typically rotates and revolves at relatively low speeds and high torques. However, Gerotor pumps are typically designed to include planetary gears, so actuation of the Gerotor pump is accomplished at low input torque and high input speed, where actuation is translated into high torque and low speed by the planetary gears. Specifically, the Gerotor component is a planet, while the drive shaft is a sun.

[0005] A possible design for such a Gerotor-type fluid pump is disclosed in US Patent 11,377,953 B2. Admittedly, this design works well in practice. However, experience shows that several components of the Gerotor-type fluid pressure device disclosed in this US patent are problematic during the assembly process at the manufacturing plant, as it is prone to assembly errors. In particular, experience has shown that the actuator retaining ring used to axially fix the valve drive shaft in place is often missing during assembly, especially in a manner that does not push the valve core segment away from the adjacent distribution plate segment. This lack of a actuator retaining ring often leads to a significant deterioration in pumping performance and efficiency.

[0006] The lack of a properly assembled drive retaining ring is particularly problematic because it is often overlooked during test bench operations on the manufacturing side. Customers then suffer from mechanical problems and end up with costly refurbishments of their final machines built using defective Gerotor pumps. This is not only a costly issue but also a significant problem in terms of severely undermining customer trust and satisfaction.

[0007] Even if a missing drive retaining ring is discovered during test bench operation, the Gerotor pump will require a rather tedious reassembly at the assembly plant.

[0008] Given these issues, if there is a sufficient possibility that the problems can be avoided, then even a slight and moderate increase in component costs and / or assembly costs is tolerable.

[0009] Therefore, it is not surprising that people want to design a Gerotor-type pump that is less prone to errors and safer during device assembly. Summary of the Invention

[0010] Therefore, the object of the present invention is to provide a distribution plate segment for a rotary fluid pressure device, the distribution plate segment including a recess for receiving a valve drive shaft that revolves and rotates within the distribution plate segment, wherein the distribution plate also includes a plurality of circumferentially arranged fluid passage ports for selectively fluidly connecting a valve core segment and a Gerotor-type fluid displacement segment of the rotary fluid pressure device in an improved manner than such distribution plate segments known in the prior art.

[0011] Another object of the present invention is to provide a rotary fluid pressure device comprising at least a valve core segment, at least a distribution plate segment, and at least a Gerotor-type fluid displacement segment, and further comprising a valve drive shaft designed and arranged to convert the revolution and rotation of the Gerotor-type fluid displacement segment into the rotational motion of the valve core segment, thereby improving upon such rotary fluid pressure devices known in the prior art.

[0012] The distribution plate segment for a rotary fluid pressure device according to claim 1 solves at least one of these objectives.

[0013] Similarly, the rotary fluid pressure device according to claim 4 solves at least one of these objectives.

[0014] It is recommended to design and arrange a distribution plate segment for a rotary fluid pressure device, the distribution plate segment including a recess for receiving a valve drive shaft that revolves and rotates within the distribution plate segment, the distribution plate also including a plurality of circumferentially arranged fluid passage ports for selectively fluidly connecting the valve core segment and the Gerotor-type fluid displacement segment of the rotary fluid pressure device in such a manner that the recess includes at least two axially aligned segments with different diameters.

[0015] Specifically, rotary fluid pressure devices can also be referred to as Gerotor-type fluid pressure devices due to the Gerotor-type design of the fluid displacement segments. Such designs are known in the prior art, for example, as described in US 11,377,953 B2. The disclosure of this disclosure is incorporated herein by reference in its entirety. The design of recesses with at least two axially aligned segments is typically carried out in a manner where various components (if present) are fixedly connected to each other, particularly in a non-removable manner. This applies at least to the portions of the distribution plate segments adjacent to the recesses. Thus, in the process of assembling the distribution plate segments (especially in assembling the individual segments) to ultimately realize the rotary fluid pressure device, it is not possible to omit the valve drive shaft support ring as in the case of US 11,377,953 B2. As mentioned earlier, at first glance, this small change has a significant impact because the absence of the valve drive shaft support ring is typically not detected during relatively short test bench runs. When the entire mechanical system using the rotary fluid pressure device is running in the field, this, in turn, will lead to a major efficiency loss and / or fluid pump performance loss for the customer of the rotary fluid pressure device. As mentioned earlier, this presents a significant problem for end customers, thereby severely damaging buyers' trust in rotary fluid pressure device suppliers.

[0016] It is worth noting that the proposed designs typically present more challenges in terms of manufacturing and assembly. This is because standard structural components are often used less frequently, and specialized tools and machinery must be employed to manufacture the distribution plate segments. In particular, the valve drive shaft support rings used to date are readily available and inexpensive on the market, as they are standard structural components in many applications. However, the special design of the recessed portion of the distribution plate is more complex, often involving non-removable components around the recess, requiring additional manufacturing steps, etc.

[0017] Furthermore, the handling of parts becomes more complex during the assembly of the resulting rotary fluid pressure device, as heavier parts must be handled with high precision relative to each other. This is particularly true for mounting the valve drive shaft on the narrow section of the recessed portion segmented by the distribution plate. It should be noted that the diameter difference between the smaller diameter portion of the recess and the outer diameter of the corresponding end portion of the valve drive shaft is typically very small.

[0018] Nevertheless, the additional investment (and the resulting additional costs) brought about by this proposal are generally well compensated for by the benefits.

[0019] While different transient regimes are possible, it is recommended that the distribution plate segments be designed and arranged in such a way that the concave portion comprises a stepped change between at least two axially aligned segments with different diameters. In other words, there are typically two (possibly more) sections, where the diameter remains substantially constant within the respective sections. Preferably, there are exactly two axially aligned segments with a stepped change between them. It should be noted that a stepped change in a strictly mathematical sense is impossible to manufacture, at least not in a manufacturing sense. However, despite this deviation from a strict mathematical form, the concept of a stepped change will still be used in the context of this application. This will be apparent to those skilled in the art.

[0020] It should be noted that at least two axially aligned segments may exhibit more or less the same diameter within their respective cross sections. However, even within one, two, or more segments, the diameter may vary (e.g., the tapered shape of the corresponding segments).

[0021] In particular, it is recommended that the distribution plate segments be designed and arranged as single-piece units, with the housing designed and arranged as the dividing plate segments. This is especially suitable for the portions of the distribution plate segments adjacent to the recesses. In this way, the resulting distribution plate segments, and the final rotary fluid pressure device, may become particularly stable and therefore may exhibit a particularly long lifespan. Furthermore, the risk of misalignment of sub-components when connecting them together can be mitigated. The single-piece unit design can be achieved through molding techniques (possibly with some finishing work, such as polishing), through material removal techniques (e.g., turning on a lathe), or through standard fastening techniques for two sub-units known in the art (e.g., welding).

[0022] Furthermore, it is proposed to design and arrange a rotary fluid pressure device comprising at least a valve core segment, at least a distribution plate segment, and at least a Gerotor-type fluid displacement segment, and further comprising a valve drive shaft designed and arranged to convert the revolution and rotation of the Gerotor-type fluid displacement segment into the rotational motion of the valve core segment, such that the distribution plate segment is designed and arranged as a distribution plate segment according to the present disclosure. In this way, the distribution plate segment, and therefore the rotary fluid pressure device, can exhibit the inherent advantages and features of the device according to the present disclosure in a particularly profound manner. In particular, the rotary fluid pressure device can be a Gerotor-type fluid pressure device.

[0023] Furthermore, it is proposed that the rotary fluid pressure device be designed and arranged in such a way that it also includes a main shaft support housing located within a recess and a main drive shaft arranged within the main shaft support housing, wherein the main drive shaft is designed and arranged to convert the rotary input action into the rotational and revolutionary motion of the Gerotor-type fluid displacement segment. This allows for the realization of a particularly advantageous rotary fluid pressure device. As an example, the rotary fluid pressure device can then be actuated by a standard actuating machine, such as an electric motor, internal combustion engine, etc. In particular, the distribution plate segmentation and therefore the rotary fluid pressure device can particularly profoundly demonstrate the inherent advantages and features of the device according to this disclosure.

[0024] Furthermore, it is recommended that rotary fluid pressure devices be designed and arranged in a manner that allows for pivoting movement between the main drive shaft and the valve drive shaft while preventing torque connection between them. This approach can particularly effectively address the specific drive requirements of Gerotor-type fluid pressure devices. In particular, the torque-resistant connection can be achieved through a type of gear, wherein the gear rim can be a crown-shaped rim and / or can exhibit a convex and / or concave shape in the axial direction.

[0025] Another possibility is to design and arrange the rotary fluid pressure device in such a way that the valve drive shaft comprises two end portions connected by an intermediate portion, wherein at least the end portions facing the Gerotor-type fluid displacement section (preferably both end portions) have a diameter larger than that of the intermediate portion. While the end portions of the valve drive shaft can exhibit (substantially) the same diameter, it is preferable that the end portions exhibit different diameters. In particular, the end portions pointing towards the valve core section typically exhibit a larger diameter compared to the end portions pointing towards the Gerotor-type fluid displacement section. Thus, when the rotary fluid pressure device is operating in its assembled state, the valve drive shaft can be held in place when viewed axially. This advantageously avoids axial movement of the valve drive shaft, which could lead to gaps between the distribution plate section and the valve core section, again resulting in a significant reduction in efficiency and / or a deterioration in the operating characteristics of the rotary fluid pressure device.

[0026] In particular, it is recommended that the rotary fluid pressure device be designed and arranged such that the diameter of the smaller end portion of the valve drive shaft facing the Gerotor-type fluid displacement section is slightly smaller than the inner diameter of the smaller diameter portion of the recessed portion of the distribution plate segment. In this way, undesirable axial displacement of the valve drive shaft and its resulting disadvantages can be largely suppressed.

[0027] Furthermore, it is recommended that rotary fluid pressure devices be designed and arranged such that the concave portions of the distribution plate segments and the adjacent end faces of the (typically) smaller end portions of the valve drive shaft are designed and arranged in a manner that ensures essentially sliding contact during assembly of the rotary fluid pressure device. Similarly, this approach may result in particularly high operating characteristics and efficiency for the resulting rotary fluid pressure device. It should be noted that in sliding contact, the individual surfaces are in hard-material-hard-material contact (solid-solid contact). In principle, this would lead to a grinding contact with significant friction and material wear potential. However, when lubricants are used, friction and wear can be severely limited, resulting in sliding contact. It should be noted that in fluid motors / fluid pumps, lubricating fluid is not only not readily available, but is often present due to leakage problems (especially in internal voids). Furthermore, drainage channels are often required to distribute this leaked hydraulic fluid. Therefore, lubrication is generally not an issue in hydraulic machinery.

[0028] Furthermore, it is recommended that the rotary fluid pressure device be designed and arranged such that the larger diameter of at least two axially aligned segments with different diameters in the recessed portion of the distribution plate segment is selected to be substantially the same as, or smaller than, the receiving recess of the valve core segment for the corresponding end portion of the valve drive shaft. This allows for additional axial fixation of the valve drive shaft when the rotary fluid pressure device is operating in its assembled state.

[0029] Furthermore, it is recommended that rotary fluid pressure devices be designed and arranged such that the concave portions of the distribution plate segments and the adjacent end faces of the (typically) larger end portions of the valve drive shaft are in substantially sliding contact during assembly of the rotary fluid pressure device. This approach can result in particularly high operating characteristics and efficiency for the resulting rotary fluid pressure device. Attached Figure Description

[0030] Other advantages, features, and objects of the invention will become apparent from the following detailed description of the invention taken in conjunction with the accompanying drawings, in which:

[0031] Figure 1 : A perspective view of an example low-speed, high-torque Gerotor motor 100;

[0032] Figure 2 : Figure 1 Cross-sectional view of the Gerotor motor 100;

[0033] Figure 3 : Figure 1 An exploded rear view of the Gerotor motor 100;

[0034] Figure 4 : Figure 1 An exploded view of the Gerotor motor 100;

[0035] Figure 5 Cross-sectional view of the region adjacent to the valve drive shaft according to another embodiment of the Gerotor motor of this disclosure. Detailed Implementation

[0036] Reference Figure 1Based on the principles of this disclosure, an exemplary low-speed, high-torque Gerotor hydraulic motor 100 is provided. Hereinafter, the hydraulic motor 100 is also referred to as a rotary fluid pressure device. The hydraulic motor 100 may include a shaft support housing segment 102, a wear plate segment 104, a Gerotor-type displacement segment 106, a distribution plate segment 108, and / or a valve housing segment 110. The shaft support housing 102 includes a mounting flange 112 configured to mount the motor 100 to a predetermined position. The shaft support housing segment 102, the wear plate segment 104, the Gerotor-type displacement segment 106, the distribution plate segment 108, and the valve housing segment 110 can be secured together by a plurality of fasteners 114 configured to pass through fastening holes 115 (see [link to fastening hole]). Figure 3 ).

[0037] Reference Figure 2 The hydraulic motor 100 includes an output shaft 116 positioned within a shaft support housing segment 102 and rotatably supported therein by one or more bearing elements 118 and 120. A wear-resistant plate segment 104 is disposed near the rear end of the bearing element 118 and is configured to hold the output shaft 116 and the bearing elements 118 and 120 in proper position within the shaft support housing segment 102.

[0038] The wear plate segment 104 defines an axial end surface 122, which is configured to engage with an adjacent end surface (e.g., its annular member 126 and star member 128) of the Gerotor-type displacement segment 106. In some examples, an annular sealing member (e.g., an O-ring) 124 is disposed between the engaging end surfaces of the wear plate segment 104 and the shaft support housing segment 102.

[0039] The Gerotor-type displacement segment 106 can be a rotary positive displacement device and includes an internal toothed annular member 126 and an external toothed star member 128. In some examples, the annular member 126 includes a plurality of rollers 130 serving as internal teeth. The star member 128 is eccentrically disposed within the annular member 126 and may have one fewer tooth than the annular member 126. In some examples, the star member 128 revolves and rotates relative to the annular member 126, and this revolving and rotating motion defines a plurality of expanding and contracting fluid volume chambers 132. Although the annular member is described as fixed and the star member revolves and rotates, those skilled in the art will clearly understand that, according to the principles of this disclosure, the annular member or the star member may have either a revolving or rotating motion, or both. Furthermore, it is apparent that this disclosure is not necessarily limited to the Gerotor as a fluid displacement mechanism. An example of a Gerotor-type displacement segment 104 is further described in U.S. Patents US4,533,302 and US4,992,034, the entire contents of which are incorporated herein by reference.

[0040] Reference Figure 3 and Figure 4 The distribution plate 108 defines a plurality of fluid channels 136, each fluid channel 136 being configured to be in continuous fluid communication with an adjacent volume chamber 132. In the depicted example, the distribution plate 108 includes seven fluid channels 136 because the annular member 126 has seven internal teeth and thus defines seven fluid volume chambers 132.

[0041] like Figure 2 As shown, an annular sealing member (e.g., an O-ring) 133 is disposed between the opposing axial end surfaces of the wear-resistant plate segment 104 and the Gerotor-type displacement segment 106. Another annular sealing member (e.g., an O-ring) 135 is also disposed between the opposing axial end surfaces of the Gerotor-type displacement segment 106 and the distribution plate segment 108.

[0042] Turn to Figure 2 The valve housing segment 110 is configured to rotatably support the valve core 140. The valve housing segment 110 includes a fluid inlet port 142 communicating with an annular chamber 144 surrounding the valve core 140 (see also...). Figure 1 Valve housing section 110 also includes a fluid outlet port 146 (see also...) Figure 1 The fluid outlet port is in fluid communication with the central chamber 148 located between the valve body section 100 and the valve core 140. The valve body section 110 also includes a housing drain port 150 (see [link to relevant documentation]). Figure 3The housing drain port 150 is blocked to force the drain fluid to flow to either port 142 or 146 under backflow pressure. Valve spool 140 defines a plurality of first valve passages 152 and a plurality of second valve passages 154. The first valve passages 152 and second valve passages 154 are arranged alternately around valve spool 140. The first valve passages 152 are in continuous fluid communication with an annular chamber 144, and the second valve passages 154 are in continuous fluid communication with a central chamber 148. In the depicted example, there are six first valve passages 152 and six second valve passages 154, corresponding to the six external teeth of the star member 128. Valve spool 140 may also define one or more inclined discharge passages 156.

[0043] Valve spool 140 may be biased toward distribution plate segment 108 to maintain a sealing engagement with adjacent surface 164 of distribution plate segment 108, thereby preventing cross-port leakage between fluid chambers 144 and 148. In some examples, a valve seat mechanism 160 is used to bias valve spool 140 toward distribution plate segment 108. Valve seat mechanism 160 is seated within an annular groove 162 defined by valve housing segment 110. Valve seat mechanism 160 may be in fluid communication with discharge passage 156. Examples of valve seat mechanism 160 are disclosed in U.S. Patent Nos. 3,572,983 and 4,533,302, the entire contents of which are incorporated herein by reference.

[0044] Refer again Figure 2 The hydraulic motor 100 includes a main drive shaft 170 and a valve drive shaft 172. The output shaft 116 includes a set of internal straight splines 174 configured to engage with a set of front splines 176 on the main drive shaft 170. The front splines 176 of the main drive shaft 170 may be external crown splines formed on the front end 175 of the main drive shaft 170. A set of rear splines 178 of the main drive shaft 170 is formed at the rear end 177 of the main drive shaft 170. The rear splines 178 may be external crown splines configured to engage with a set of internal straight splines 180 formed on the inner circumferential surface of the star member 128. In the depicted example, the annular member 126 includes seven internal teeth, and the star member 128 includes six external teeth. Therefore, six revolutions of the star member 128 will achieve one complete rotation of its axis, and one complete rotation of the main drive shaft 170 and the output shaft 116.

[0045] Reference Figure 2 and Figure 3 Valve drive shaft 172 is at least partially received within main drive shaft 170 and engages with main drive shaft 70 such that the interface between main drive shaft 170 and valve drive shaft 172 is generally aligned with Gerotor type displacement segment 106.

[0046] In some examples, the main drive shaft 170 includes a hollow portion 184 at its rear end 177 and has a set of internal splines 186 formed on the inner circumferential surface of the hollow portion 184. The internal splines 186 of the main drive shaft 170 may be straight splines. The hollow portion 184 of the main drive shaft 170 is configured to receive at least a portion of the front end 192 of the valve drive shaft 172, and the internal splines 186 of the main drive shaft 170 at its rear end 177 engage with a set of front external splines 196 formed around the front end 192 of the valve drive shaft 172. In some examples, the front splines 196 of the valve drive shaft 172 may be crown splines. The valve drive shaft 172 has a set of rearward external splines 198 at its rear end 194, which are configured to engage a set of internal splines 200 formed around the inner circumference of the valve core 140 (the recess 201 of the valve core 140, including internal splines 200). In some examples, the rear spline 198 of the valve drive shaft 172 may be an external crown spline, and the internal spline 200 of the valve core 140 may be a straight spline.

[0047] As shown in the figure, the engagement between the internal spline 186 of the main drive shaft 170 and the external spline 196 of the valve drive shaft 172 is arranged between opposing planes P1 and P2, which are respectively formed by the axial end surfaces 206 and 208 of the Gerotor displacement mechanism 106 (see also...). Figure 3 and Figure 4 The first plane P1 is defined by the axial end surface 206 of the Gerotor displacement mechanism 106, and the second plane P2 is defined by the axial end surface 208 of the Gerotor-type displacement segment 106. In some examples, the interface between the internal spline 186 of the main drive shaft 170 and the external spline 196 of the valve drive shaft 172 is typically aligned with the interface between the external spline 178 of the main drive shaft 170 and the internal spline 180 of the star member 128.

[0048] Therefore, the construction of the external spline 196 of the valve drive shaft 172 nested in the hollow portion 184 of the main drive shaft 170 requires a shorter axial length of the internal spline 180 of the star member 128 of the Gerotor-type displacement segment 106, thus maximizing the utilization efficiency of the spline 180 of the star member 128. In some cases, due to the requirement for a shorter axial length of the internal spline 180 of the star member 128, the lengths of the spline 186 of the main drive shaft 170 and the spline 196 of the valve drive shaft 172 can be maximized. Due to the reduced required spline length, the design of this disclosure also provides a high eccentricity on small displacement motors to improve starting torque efficiency. Furthermore, this configuration allows the use of a Gerotor-type displacement segment 106 with a smaller width along the axis of rotation A. The design according to this disclosure also reduces the operating angle of both the main drive shaft 170 and the valve drive shaft 172, thereby extending the life of the hydraulic motor 100. This design can reduce the demand for housing flow (e.g., leakage channels), thereby improving volumetric efficiency.

[0049] Refer again Figures 2 to 4 The hydraulic motor 100 includes a recess 224 that serves as a drive retainer device 220 to prevent the spool valve 140 from lifting off the distribution plate 108. According to this disclosure, this is achieved by the recess 224 comprising two distinct portions 221 and 222 with different diameters: a first portion 222 with a larger diameter (which may be referred to as the nominal diameter of the recess 24) and a second portion 221 with a smaller diameter. The transition between the first portion 222 and the second portion 221 is currently implemented as a stepped transition. In this disclosure, a lift-off phenomenon can be defined as the axial separation of the spool valve 140 from the fixed distribution plate segment 108. The lift-off phenomenon can occur as the main drive shaft 170 and the valve drive shaft 172 rotate and revolve in cooperation with a Gerotor-type displacement segment 106 including a Gerotor displacement mechanism, and as the main drive rod 170 and / or the valve drive rod 172 slide axially toward the spool valve 140. Disconnection can cause severe cross-port leakage and shutdown of motor 100.

[0050] As currently proposed, the drive retainer component 220 comprises two distinct portions 221, 222 with different diameters, wherein these two distinct portions 221, 222 are designed and arranged as integrally disposed on the inner side (recess 224) of the distribution plate segment 108, which is not removable. Preferably, the drive retainer assembly 220 is designed as a single-piece unit integral with the adjacent housing portion of the distribution plate segment 108. When the star-shaped component 128 rotates and revolves about the annular component 126 of the Gerotor-type displacement segment 106, the second portion 221 of the drive retainer assembly 220 with a smaller diameter is arranged near the axial end surface of the star-shaped component 128. In some examples, the second portion 221 of the drive retainer assembly 220 with a smaller diameter is arranged and configured to contact the axial end surface of the star-shaped component 128 during the rotation and revolution of the star-shaped component 128.

[0051] According to one possible embodiment, the second portion 221 of the drive retainer 220, having a smaller diameter, can be configured as an initially separate subunit that will be connected to a standard distribution plate segment 108 (e.g., to utilize existing castings and / or blanks to manufacture the distribution plate segment 108, thereby limiting cost increases and accelerating the implementation of the currently proposed design), for example, using a brazing or welding-like solid (positive substance) locking connection. In other examples, the distribution plate segment 108 can be used, which is specifically designed and arranged to include the drive retainer assembly 220 as a single unit.

[0052] As shown in the figure, the drive retainer assembly 220 includes a recess 224 having a nominal diameter (currently equal to the inner diameter of the first larger dimension portion 222 of the drive retainer assembly), which is configured such that when the valve drive shaft 172 is installed in place, the rod 226 of the valve drive shaft 172 (see figure 224) is positioned within the valve drive shaft 172. Figure 3 The nominal opening of the drive retainer assembly 220 is configured to hold the front end 192 of the valve drive shaft 192 within the hollow portion 186 of the main drive shaft 160 when the star member 128, the main drive shaft 170, and the valve drive shaft 172 revolve together about the annular member 126 of the Gerotor displacement mechanism / Gerotor-type displacement segment 106. In some examples, the center of the nominal opening of the drive retainer assembly 220 is aligned with the axis of rotation A.

[0053] In some examples, with according to Figures 1 to 4As in the embodiment of the hydraulic motor 100, the nominal opening of the drive retainer arrangement 220 (i.e. the inner diameter of the first portion 222) is designed as a hole with a diameter configured to be greater than the maximum diameter of the valve drive shaft 172 at the front end 192, such that the valve drive shaft 72 passes through the nominal opening of the first portion 222 of the drive retainer arrangement 220 during installation.

[0054] The opening of the first portion 222 is also configured such that when the valve drive shaft 172 rotates and revolves around the annular member 128 of the Gerotor-type displacement segment 106, its maximum outermost trajectory is smaller than that defined by the valve drive shaft 172 (i.e., its external spline 196) at the front end 192. This also applies to the second portion 221 of the drive retainer device 220 with necessary modifications in detail, although the inner diameter of the second portion 211 is smaller than that of the first portion 222. Therefore, the process of introducing the valve drive shaft 172 through the second portion 221 is more refined compared to the first portion 222. This configuration is to prevent the valve drive shaft 172 from disengaging from or sliding out of the hollow portion 186 of the main drive shaft 170, thereby preventing it from disengaging from the Gerotor-type displacement segment 106. When the valve drive shaft 172 tilts and deviates from the axis of rotation A and revolves around the annular member 126 of the Gerotor-type displacement segment 106, the maximum outermost trajectory of the valve drive shaft 172 is defined by the external spline 196 at the front end 192 of the valve drive shaft 172.

[0055] According to Figures 1 to 4 In an embodiment of the hydraulic motor 100, the diameter of the recess 201 of the valve core 140 is selected to be approximately the same as the diameter of the first portion 222 of the drive retainer member 220. (The diameter of the recess 201 of the valve core 140 may be defined by the protruding tooth tip of the internal spline 200, by the tooth root groove of the internal spline 200, or by a more or less average value.)

[0056] exist Figure 5 One modification is made whereby the diameter of the first portion 222 of the drive retainer member 220 is chosen to be significantly smaller than the diameter of the recess 201 of the valve core 140. This allows for sliding contact between the adjacent surfaces (partially) of the rear end 194 of the valve drive shaft 172 and the adjacent surfaces 164 (around the bore of the first portion 222 of the drive retainer member 220) of the distributor plate segment 108. This allows for advantageous fixation of the valve drive shaft 172 in the axial direction. It should be understood that, within the internal clearance of the Gerotor hydraulic motor 100 (as is the case with substantially all types of mobile hydraulic machinery), the amount of hydraulic fluid generated due to fluid leakage is generally sufficient, even without special provisions. Therefore, the (current) metal-to-metal contact will be lubricated to a degree that results in a low-friction sliding contact (appropriately low mechanical wear on the contact surfaces).

[0057] In some examples, the opening diameters of both the first portion 222 and the second portion 221 of the recess 224 are smaller than the maximum diameter of the main drive shaft 170 at the rear end 177, thereby preventing the main drive shaft 170 from slipping off the Gerotor-type displacement segment 106 during rotation and revolution. In other examples, when the main drive shaft 170 revolves around the annular member 128 of the Gerotor-type displacement segment 106, the opening diameters of both the first portion 222 and the second portion 221 of the recess 224 are smaller than the maximum trajectory defined by the main drive shaft 170 (i.e., its external spline 178) at the rear end 177.

[0058] Therefore, the drive retainer device 220 is configured to prevent the slide valve 140 from disengaging from other valve components (e.g., the distribution plate segment 108). Otherwise, disengagement would reduce volumetric efficiency and cause idling.

[0059] In this document, the shaft support housing segment 102 and the wear-resistant plate segment 104 can be considered as a single unit and referred to as the output shaft housing. In some examples, the shaft support housing segment 102 and the wear-resistant plate segment 104 can be configured as a single integral component. The output shaft housing (including the shaft support housing segment 102 and the wear-resistant plate segment 104) and the valve housing segment 110 can be considered as a single unit and referred to as the housing assembly herein. Furthermore, the valve core 140 can be considered as a valve mechanism. In some examples, the valve mechanism may also include a distribution plate segment 108.

[0060] It should be noted that throughout this disclosure, the same reference numerals are used for components that are sufficiently similar in design and / or function to support the use of the same reference numerals, even though the individual components may differ. This is done for the sake of brevity and to improve the comprehensibility of the description.

[0061] It should also be noted that one or more features of one, several or all of the detailed embodiments of this disclosure may be used in conjunction with the general description of this disclosure (even in this application and other foregoing applications).

Claims

1. A distribution plate segment (108) for a rotary fluid pressure device (100), comprising a recess (220) for receiving a valve drive shaft (172) that revolves and rotates within the distribution plate segment (108), the distribution plate segment (108) further comprising a plurality of circumferentially arranged fluid passage ports (136) for selectively fluidly connecting a valve core segment (110) and a Gerotor-type fluid displacement segment (106) of the rotary fluid pressure device (100), characterized in that, The recess (224) includes at least two axially aligned segments (221, 222) with different diameters.

2. The distribution plate segment (108) according to claim 1, characterized in that, The recess (224) includes a stepped variation between the at least two axially aligned segments (221, 222) with different diameters.

3. The distribution plate segment (108) according to claim 1 or 2, particularly according to claim 2, is characterized in that, The housing of the distribution plate segment (108) is designed and arranged as a single unit, particularly the portion adjacent to the recess (224).

4. A rotary fluid pressure device (100), particularly a Gerotor-type fluid pressure device (100), comprising at least a valve core segment (110), at least a distribution plate segment (108), and at least a Gerotor-type fluid displacement segment (106), and further comprising a valve drive shaft (172) designed and arranged to convert the revolution and rotation of the Gerotor-type fluid displacement segment (106) into the rotational motion of the valve core segment (110), characterized in that, The distribution plate segment (108) is designed and arranged as the distribution plate segment (108) according to any one of claims 1 to 3.

5. The rotary fluid pressure device (100) according to claim 4 further includes a main shaft support housing (102, 104) located within the recess and a main drive shaft (170) disposed within the main shaft support housing (102, 104), wherein, The main drive shaft (170) is designed and arranged to convert the rotary input motion (116) into the rotational and revolution motion of the Gerotor-type fluid displacement segment (106).

6. The rotary fluid pressure device (100) according to claim 4 or 5, particularly according to claim 5, is characterized in that, The main drive shaft (170) and the valve drive shaft (172) are connected to each other in a torque-resistant manner, while allowing pivoting movement between the main drive shaft (170) and the valve drive shaft (172).

7. The rotary fluid pressure device (100) according to any one of claims 4 to 6, characterized in that, The valve drive shaft (172) includes two end portions (192, 194) connected by a middle portion (226), wherein at least the end portion (192) facing the Gerotor-type fluid displacement portion (106) has a diameter larger than the diameter of the middle portion (226), preferably both end portions (192, 194) have a diameter larger than the diameter of the middle portion (226).

8. The rotary fluid pressure device (100) according to any one of claims 4 to 7, particularly according to claim 7, is characterized in that, The diameter of the smaller end portion (192) of the valve drive shaft (172) facing the Gerotor-type fluid displacement portion (106) is slightly smaller than the inner diameter of the smaller diameter portion (221) of the recess (224) of the distribution plate segment (108).

9. The rotary fluid pressure device (100) according to any one of claims 4 to 8, characterized in that, The recessed portion (220) of the distribution plate segment (108) and the adjacent end face of the smaller end portion (192) of the valve drive shaft (172) are designed and arranged in a manner that they are in substantially sliding contact when assembling the rotary fluid pressure device (100).

10. The rotary fluid pressure device (100) according to any one of claims 4 to 9, characterized in that, The larger diameter of the at least two axially aligned segments (221, 222) of the recess (224) of the distribution plate segment (108) with different diameters is selected to be substantially the same as, or smaller than, the receiving recess (201) of the valve core segment (110) of the corresponding end portion (194) of the valve drive shaft (172).

11. The rotary fluid pressure device (100) according to any one of claims 4 to 10, characterized in that, The recessed portion (220) of the distribution plate segment (108) and the adjacent end face of the larger end portion (194) of the valve drive shaft (172) are designed and arranged in a manner that they are in substantially sliding contact when assembling the rotary fluid pressure device (100).

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